Codecalc- 2013 Manual
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CodeCalc User's Guide
Version 2013 (V15.0) November 2012 DICAS-PE-200109C
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Contents What's New in PV Elite and CodeCalc ....................................................................................................... 9 CodeCalc Overview ................................................................................................................................... 11 What Distinguishes CodeCalc From our Competitors? ........................................................................ 12 What Analysis Types are Available?..................................................................................................... 12 Technical Support ................................................................................................................................. 16 Installation ............................................................................................................................................. 16 CodeCalc Workflows ................................................................................................................................. 17 Starting CodeCalc ................................................................................................................................. 17 Performing an Analysis ......................................................................................................................... 17 Reviewing the Results - The Output Option ......................................................................................... 22 Printing or Saving Reports to a File ................................................................................................ 23 Tabs ............................................................................................................................................................ 25 File Tab ................................................................................................................................................. 25 Home Tab ............................................................................................................................................. 26 Tools Tab .............................................................................................................................................. 28 Configuration Dialog Box ................................................................................................................ 29 Create/Edit Units File...................................................................................................................... 32 Material Database Editor ................................................................................................................ 34 Diagnostics Tab .................................................................................................................................... 47 ESL Tab ................................................................................................................................................ 47 Shells and Heads ....................................................................................................................................... 49 Purpose, Scope and Technical Basis (Shells) ...................................................................................... 49 API 579 Introduction ............................................................................................................................. 52 Purpose, Scope, and Technical Basis............................................................................................ 52 Discussion of Results (Shells) ........................................................................................................ 55 Shells/Heads Tab .................................................................................................................................. 55 Geometry Tab (Shell/Head) .................................................................................................................. 58 Bar Options ..................................................................................................................................... 62 Section Options .............................................................................................................................. 64 Optional Data Tab ................................................................................................................................. 66 Supplemental Loads ....................................................................................................................... 67 Compute Remaining Life ................................................................................................................ 68 Jacket Tab............................................................................................................................................. 69 API 579 (FFS) Tab ................................................................................................................................ 78 Data Measurement Tab .................................................................................................................. 81 Point Measurement Data Dialog Box ............................................................................................. 83 Enter CTPs Dialog Box................................................................................................................... 83 Groove Options .............................................................................................................................. 83 Enter Pitting Information Dialog Box .............................................................................................. 84 Results .................................................................................................................................................. 85
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Contents Nozzles ....................................................................................................................................................... 87 Purpose, Scope, and Technical Basis (Nozzles) .................................................................................. 87 Nozzle Tab ............................................................................................................................................ 88 Geometry Tab ....................................................................................................................................... 91 Miscellaneous Tab ................................................................................................................................ 95 Shell/Head Tab ................................................................................................................................... 101 Results ................................................................................................................................................ 105 Actual Nozzle Diameter Thickness............................................................................................... 105 Required Thickness of Shell and Nozzle...................................................................................... 105 UG-45 Minimum Nozzle Neck Thickness ..................................................................................... 106 Required and Available Areas ...................................................................................................... 106 Selection of Reinforcing Pad ........................................................................................................ 106 Large Diameter Nozzle Calculations ............................................................................................ 106 Effective Material Diameter and Thickness Limits ....................................................................... 106 Minimum Design Metal Temperature ........................................................................................... 107 Weld Size Calculations ................................................................................................................. 107 Weld Strength Calculations .......................................................................................................... 107 Failure Path Calculations.............................................................................................................. 107 Iterative Results Per Pressure, Area, And UG-45 ........................................................................ 107 Conical Sections ...................................................................................................................................... 109 Cone Design Tab (Conical Sections) .................................................................................................. 110 Cone Geometry Tab ........................................................................................................................... 112 Small Cylinder and Larger Cylinder Tabs ........................................................................................... 113 Results ................................................................................................................................................ 115 Internal Pressure Results ............................................................................................................. 115 External Pressure Results ............................................................................................................ 115 Reinforcement Calculations Under Internal Pressure .................................................................. 116 Reinforcement Calculations Under External Pressure ................................................................. 116 Floating Heads ......................................................................................................................................... 117 Head Tab ............................................................................................................................................ 118 Flange/Bolts Tab ................................................................................................................................. 120 Gasket Tab.......................................................................................................................................... 122 Miscellaneous Tab .............................................................................................................................. 128 Results ................................................................................................................................................ 132 Internal Pressure Results for the Head: ....................................................................................... 133 External Pressure Results for Heads: .......................................................................................... 133 Intermediate Calculations for Flanged Portion of Head ............................................................... 133 Required Thickness Calculations ................................................................................................. 133 Soehren's Calculations: ................................................................................................................ 134 Flanges ..................................................................................................................................................... 135 Purpose, Scope, and Technical Basis (Flanges) ................................................................................ 135 Flange Data Tab ................................................................................................................................. 138 Hub/Bolts Tab ..................................................................................................................................... 142 Gasket Data Tab ................................................................................................................................. 144 Results (Flanges) ................................................................................................................................ 148
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CodeCalc User's Guide
Contents TEMA Tubesheets ................................................................................................................................... 151 Purpose, Scope, and Technical Basis (TubeSheets) ......................................................................... 151 Shell Tab (TEMA Tubesheets)............................................................................................................ 155 Channel Tab (TEMA Tubesheets) ...................................................................................................... 156 Tubes Tab (TEMA Tubesheets).......................................................................................................... 157 Tubesheet Tab (TEMA Tubesheets) .................................................................................................. 161 Expansion Joint Tab (TEMA Tubesheets) .......................................................................................... 166 Tubesheet Extended as Flange Dialog (TEMA Tubesheets) ............................................................. 169 Outer Cylinder Dialog Box .................................................................................................................. 171 Outer Cylinder on the Thick Expansion Joint ............................................................................... 171 Outer Cylindrical Element Corrosion Allowance .......................................................................... 171 Outer Cylindrical Element Length (Lo) ......................................................................................... 171 Shell Band Properties Dialog Box ....................................................................................................... 172 Shell Thickness Adjacent to Tubesheet ....................................................................................... 173 Shell Band Corrosion Allowance .................................................................................................. 173 Length of Shell Thickness Adjacent to Tubesheet, front end L1 .................................................. 173 Length of Shell Thickness Adjacent to Tubesheet, rear L1.......................................................... 173 Multiple Load Cases Dialog Box (TEMA Tubesheets) ....................................................................... 173 Tubesheet Gasket Dialog Box ............................................................................................................ 173 Fixed Tubesheet Exchanger Dialog Box ............................................................................................ 176 Kettle Tubesheet Dialog Box .............................................................................................................. 177 Results (Tubesheets) .......................................................................................................................... 177 ASME Tubesheets ................................................................................................................................... 183 Purpose, Scope, and Technical Basis ................................................................................................ 183 Shell Tab ............................................................................................................................................. 185 Channel Tab........................................................................................................................................ 186 Tubes Tab ........................................................................................................................................... 187 Tube to Tubesheet Joint Input Dialog Box ................................................................................... 190 Tubesheet Tab .................................................................................................................................... 192 Tubesheet Exchanger Dialog Box ................................................................................................ 197 Multiple Load Cases Dialog Box .................................................................................................. 198 Tubesheet Gasket/Bolting Input Dialog Box................................................................................. 199 Expansion Joint Tab ........................................................................................................................... 205 Tubesheet Extended As Flange Dialog Box ....................................................................................... 209 Additional Input U-tube Tubesheets Dialog Box ................................................................................. 209 Results (ASME Tubesheets)............................................................................................................... 211 Horizontal Vessels ................................................................................................................................... 213 Saddle Wear Plate Design .................................................................................................................. 213 Vessel Tab .......................................................................................................................................... 216 Shell/Head Tab ................................................................................................................................... 218 Saddle/Wear Tab ................................................................................................................................ 220 Saddle Webs and Base Plate Dialog Box ........................................................................................... 220 Stiffening Ring Tab (Horizontal Vessels) ............................................................................................ 221 Longitudinal Loads Tab (Horizontal Vessels) ..................................................................................... 222 Seismic Loads Tab (Horizontal Vessels) ............................................................................................ 223 Wind Loads Tab (Horizontal Vessels)................................................................................................. 224 Results ................................................................................................................................................ 226
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Contents Rectangular Vessels (App. 13) ............................................................................................................... 229 Vessel Tab .......................................................................................................................................... 239 Figure A1 Dialog Box.................................................................................................................... 247 Figure A2 Dialog Box.................................................................................................................... 247 Figure B3-B Dialog Box ................................................................................................................ 254 Short Side Tab .................................................................................................................................... 256 Long Side Tab ..................................................................................................................................... 258 Reinforcing Bar Options ...................................................................................................................... 260 Reinforcing Section Options ............................................................................................................... 261 Results ................................................................................................................................................ 261 Ligament Efficiency Calculations .................................................................................................. 261 Reinforcement Calculations ......................................................................................................... 262 Stress Calculations ....................................................................................................................... 262 Allowable Calculations.................................................................................................................. 263 Highest Percentage of Allowable Calculations ............................................................................. 263 MAWP Calculations ...................................................................................................................... 263 External Pressure Calculations .................................................................................................... 264 Legs and Lugs ......................................................................................................................................... 265 Legs and Lugs Tab ............................................................................................................................. 267 Baseplate ...................................................................................................................................... 269 Loads Tab ........................................................................................................................................... 272 Wind Loads ................................................................................................................................... 273 Seismic Loads .............................................................................................................................. 276 Lifting Lug Dialog Box ......................................................................................................................... 278 Support Lug Dialog Box ...................................................................................................................... 281 Vessel Leg Tab ................................................................................................................................... 284 AISC Database Dialog Box .......................................................................................................... 285 Trunnion Tab ....................................................................................................................................... 286 Output ................................................................................................................................................. 288 Leg Results ......................................................................................................................................... 289 Baseplate Results ............................................................................................................................... 289 Trunnion Results ................................................................................................................................. 289 Pipes and Pads ........................................................................................................................................ 291 Pipes and Pads Tab (Pipes and Pads) ............................................................................................... 291 Output ................................................................................................................................................. 300 WRC 107/537 FEA .................................................................................................................................... 301 Design Tab .......................................................................................................................................... 302 Vessel Tab .......................................................................................................................................... 304 Loads Tab ........................................................................................................................................... 306 WRC 107/537 Load Conventions ................................................................................................. 314 Global Load and Direction Conventions ....................................................................................... 315 WRC 107 Options ............................................................................................................................... 315 FEA Options ................................................................................................................................. 317 Results (WRC 107/537/FEA) .............................................................................................................. 318 WRC 107 Stress Summations ...................................................................................................... 318 WRC 107 Stress Calculations ...................................................................................................... 321 Finite Element Analysis (FEA) ...................................................................................................... 323 Examples ............................................................................................................................................ 324
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CodeCalc User's Guide
Contents Base Rings ............................................................................................................................................... 327 Base Ring (1) Tab (Base Rings) ......................................................................................................... 333 Base Ring (2) Tab (Base Rings) ......................................................................................................... 334 Miscellaneous Tab (Base Rings) ........................................................................................................ 336 Results (Base Rings) .......................................................................................................................... 339 Thin Joints................................................................................................................................................ 341 Expansion Joint Tab (Thin Joints)....................................................................................................... 341 Bellows Tab (Thin Joints) .................................................................................................................... 346 Thick Joints .............................................................................................................................................. 349 Expansion Joint Tab (Thick Joints) ..................................................................................................... 351 Shell Tab (Thick Joints) ...................................................................................................................... 352 Miscellaneous Tab (Thick Joints)........................................................................................................ 353 Results (Thick Joints) .......................................................................................................................... 356 Half Pipes ................................................................................................................................................. 357 Shell Tab (Half Pipes) ......................................................................................................................... 358 Jacket Tab (Half Pipes) ....................................................................................................................... 359 Discussion of Results .......................................................................................................................... 360 Large Openings ....................................................................................................................................... 363 Opening Tab (Large Openings) .......................................................................................................... 365 Shell/Nozzle Tab (Large Openings) .................................................................................................... 366 WRC 297/Annex G ................................................................................................................................... 367 WRC 297 Tab ..................................................................................................................................... 367 Vessel Tab .......................................................................................................................................... 369 Nozzle / Attachment Tab ..................................................................................................................... 370 Loads Tab ........................................................................................................................................... 372 Appendix Y Flanges ................................................................................................................................ 375 Flange Tab .......................................................................................................................................... 376 Hubs/Bolts Tab.................................................................................................................................... 378 Gasket Tab.......................................................................................................................................... 380 Material Dialog Boxes ............................................................................................................................. 385 Material Database Dialog Box ............................................................................................................ 385 Material Properties Dialog Box ........................................................................................................... 422 Appendices .............................................................................................................................................. 433 Example Problems .............................................................................................................................. 433 Complete Vessel Examples ......................................................................................................... 433 Bibliography of Pressure Vessel Texts and Standards ...................................................................... 469 CodeCalc Version 4.5 Features (7/90) ............................................................................................... 471 CodeCalc Version 5.0 Features (6/91) ............................................................................................... 471 CodeCalc Version 5.1 Features (7/92) ............................................................................................... 472 CodeCalc Version 5.2 Features (7/93) ............................................................................................... 472
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Contents CodeCalc Version 5.4 Features (6/95) ............................................................................................... 472 CodeCalc Version 5.3 Features (7/94) ............................................................................................... 473 CodeCalc Version 5.5 Features (6/96) ............................................................................................... 474 CodeCalc Version 5.6 Features (6/97) ............................................................................................... 475 CodeCalc Version 6.0 Features (6/98) ............................................................................................... 475 CodeCalc Version 6.1 Features (1/99) ............................................................................................... 476 CodeCalc Version 6.2 Features (1/2000) ........................................................................................... 476 CodeCalc Version 6.3 Features (1/2001) ........................................................................................... 476 CodeCalc Version 6.4 Features (1/2002) ........................................................................................... 477 CodeCalc Version 6.5 Features (1/2003) ........................................................................................... 477 CodeCalc Version 2004 Features (1/2004) ........................................................................................ 478 CodeCalc Version 2005 Features (1/2005) ........................................................................................ 478 CodeCalc Version 2006 Features (1/2006) ........................................................................................ 479 Index ......................................................................................................................................................... 481
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CodeCalc User's Guide
What's New in PV Elite and CodeCalc Below are the new features for Version 2013 (V15.0) of PV Elite and CodeCalc. New features and improvements come directly from your comments as well as updates to the previous version.
Code Updates and Analysis changes:
PD 5500 2012 added PD 5500 jackets and limpet coils added TEMA 9th edition added API 579 -1/ FFS-1 (2007 edition), Part 4: General Metal Loss added to PV Elite Upgrade ASME VIII, Div 1 Fatigue Analysis using Div 2 (2007, 2011a version) MDMT for UHA 51 stainless steels EN-13445: expansion joint calculations (bellows) added (2012 R1) ASME Tubesheet MDMT calculations available Differential pressures on tubes for differential pressure design A number of user requested EN-13445 enhancements have been added
Internationalization
Australian/ New Zealand 2011 Wind Code update Vertical acceleration component for Indian seismic calculation Update to European Wind Code to 2011 version European Nozzle load table is now available (2012 R1) Inclusion of European shapes in structural database (2012 R1) Rounded metric defaults in basering and nozzle dialogs and tools à configuration(2012 R1) Multiple languages (French, Portuguese, Spanish, and Italian)
Productivity Enhancements
Superseded ASME materials dating back to 1947 Sort capabilities for materials database dialog – sort by any column Zick saddle analysis now uses 95% Yield (Hydro) or 80% Yield (Pneumatic) Allowables Miscellaneous weight percentages for component details such as saddles and nozzles Template file, *.pvpt, that will change all the files in the same folder if modified
Print directly to PDF printing in all modules
Multicolored output for stainless steels in the MDMT report
Output Reports
Search (ctrl + F), copy (ctrl + C) and select all (ctrl + A) are available Reports that fail will be shown in red in the report menu Users can now drag and drop the order of the reports in the output menu Multicolored table for tubesheets indicating shellside and tubeside components
User Interface
New updated ribbon toolbar Office 2010 style themes
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CodeCalc Overview
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New icons Ability to change graphics driver from within PV Elite Codecalc interface updated Users can now change the elements’ colors based on material, wall thickness, temperature, and pressure 2D and 3D views are now tabbed
CodeCalc User's Guide
SECTION 1
CodeCalc Overview CodeCalc consists of nineteen modules for the design and analysis of pressure vessels and heat exchangers, and assessment of fitness for service. The software provides the mechanical engineer with easy-to-use, technically sound, well-documented reports. The reports contain detailed calculations and supporting comments, which speed and simplify the task of vessel design, re-rating, or fitness for service. The popularity of CodeCalc is a reflection of Intergraph's expertise in programming and engineering, and dedication to service and quality. Calculations in CodeCalc are based on the latest editions of national codes such as the ASME Boiler and Pressure Vessel Code, or industry standards such as the Zick method of analysis for horizontal drums. CodeCalc offers exceptional ease of use, which results in dramatic improvement in efficiency for both design and re-rating. CodeCalc features include: Extensive on-line help. Management of multiple analysis files so that you can define a whole pressure vessel in a single file. Defining your own unit system, including metric and SI units. Internally, however, calculations continue to be in the English system of units, assuring continuing compliance with ASME Code requirements. Access to a complete material library including over 3,000 allowable stress versus temperature tables and 67 external pressure charts. You can also add materials to the database. Access to a component library containing diameter and wall thickness for all standard pipe sizes, pressure vs. temperature charts for ANSI B16.5 flanges, and section properties for AISC beam sections. A summary capability allowing evaluation of all the components of a pressure vessel or heat exchanger. Design pressure, temperature, material, and maximum allowable working pressure (MAWP) are shown for each component. Thorough and complete printed analysis reports, with definable headings on each page. Comments and other additions may be inserted at any point in the output. Analysis is saved to a drive and can be exported to a text or Microsoft Word file format, making it easy to keep records and do revisions. High-quality documentation with complete operating instructions, a tutorial, and many example problems, making CodeCalc suitable for both beginners and experts. Scaled and dimensioned plots for each component in every module. The graphics can be sent directly to the printer. Interactive calculations, allowing quick design optimization without leaving the input screen. Extensive examples covering most of the ASME Section VIII Div.1 code examples, along with some published examples. Merge and import features, allowing faster and error-free ways to share data between different CodeCalc modules or from PV Elite. An auto-save feature, allowing files to be saved at specified time intervals.
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CodeCalc Overview In This Section
What Distinguishes CodeCalc From our Competitors? ..................12 What Analysis Types are Available? ..............................................12 Technical Support ...........................................................................16 Installation.......................................................................................16
What Distinguishes CodeCalc From our Competitors? Our staff of experienced pressure vessel engineers are involved in day-to-day software development, software support, and training. This approach has produced software which closely fits today's requirements of the pressure vessel industry. Data entry is simple and straightforward through annotated input fields. Most of these fields are accompanied by an informative help file. CodeCalc provides the widest range of modeling and analysis capabilities without becoming too complicated for simple system analysis. You can tailor CodeCalc through default settings and customized databases. Comprehensive input graphics confirm model construction before analysis is made. The software's interactive output processor presents results on the monitor for quick review or sends complete reports to a file, printer or Microsoft Word document. CodeCalc is an up-to-date package that not only uses standard analysis guidelines, but also provides the latest recognized opinions for these analyses. CodeCalc is a field-proven engineering analysis program. It is a widely recognized product with a large customer base and has an excellent support and development record.
What Analysis Types are Available? The following analysis modules are available in CodeCalc:
Shells & Heads Performs internal and external pressure design of vessels and exchangers using the ASME Code, Section VIII, Division 1 rules. Components include cylinders, conical sections, elliptical heads, torispherical heads, flat heads, spherical shells, and spherical heads. This module calculates required thickness and maximum allowable internal pressure for the given component. It also calculates the minimum design metal temperature according to UCS-66, and evaluates stiffening rings for external pressure design. Jackets covering the shell can also be analyzed. These jackets are addressed in Appendix 9 of the ASME Sec. VIII Div. 1. The module implements API-579 Fitness For Service evaluations (FFS) Sec. 4, Local Thinning, Sec. 5, General Metal Loss and Sec. 6 Pitting Corrosion. For more information, see Shells and Heads (on page 49).
Nozzles Calculates required wall thickness and reinforcement under internal pressure for nozzles in shells and heads, using the ASME Code, Section VIII, Division 1 rules, including tables of outside diameter and wall thickness for all nominal pipe diameters and schedules. The module checks weld sizes, calculates the strength of reinforcement, and evaluates failure paths for the nozzle. Hillside, tangential and Y-angle nozzles can also be evaluated. For more information, see Nozzles (on page 87).
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CodeCalc User's Guide
CodeCalc Overview Conical Sections Performs internal and external pressure analysis of conical sections and stiffening rings using the ASME Code, Section VIII, Division 1 rules. Complete area of reinforcement and moment of inertia calculations for the cone under both internal and external pressure are included. For more information, see Conical Sections (on page 109).
Floating Heads Performs internal and external pressure analysis of bolted dished heads (floating heads) using the ASME Code, Section VIII, Division 1, Appendix 1 rules. The module also provides the additional Soehren's calculation technique allowed by the code. MAWP and MAPnc are also calculated. For more information, see Floating Heads (on page 117).
Flanges Performs stress analysis and geometry selection for all types of flanges using the ASME Code, Section VIII, Division 1 rules. This module designs and analyzes the following types of flanges: All integral flange types Slip-on flanges and all loose flange types with hubs Ring-type flanges and all loose flange types without hubs Blind flanges, both circular and non-circular TEMA channel covers Reverse geometry weld neck flanges Flat faced flanges with full face gaskets You can input the external forces and moments acting on the flange and alternate mating flange loads. For more information, see Flanges (on page 135).
TEMA Tubesheets (TEMA and PD 5500) Performs an analysis of all types of tubesheets using the 8th Edition of the Standards of the Tubular Exchanger Manufacturers Association and PD 5500. The module takes full account of the effects of tubesheets extended as flanges. For fixed tubesheets, the module includes the effects of differential thermal expansion and the presence of an expansion joint. Expansion joints can also be designed. For a fixed tubesheet exchanger the module analyzes multiple load cases for both the corroded and uncorroded conditions. If an expansion joint is added, then run the corresponding expansion joint load cases. For more information, see TEMA Tubesheets (on page 151).
ASME Tubesheets Determines the required thickness of tubesheets for fixed, floating, or U-tube exchangers according to the ASME Code Section VIII division 1 section UHX. Analyzes multiple loads cases for corroded and uncorroded conditions. MAWP and MAPnc for the shellside and tubeside are determined. For more information, see ASME Tubesheets (on page 183).
Horizontal Vessels Performs stress analysis of horizontal drums on saddle supports using the L.P. Zick method. Results include stresses at the saddles, the midpoint of the vessel, and in the heads. Stiffening
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CodeCalc Overview rings used in the design of the vessel are evaluated. Additionally, the saddle, webs, and baseplate are checked for external seismic and wind loads. You can also specify friction and additional longitudinal forces on the vessel. For more information, see Horizontal Vessels (on page 213).
Rectangular Vessels Analyzes non-circular pressure vessels using the rules of the ASME Code, Section VIII, Division 1 and Appendix 13. Most of the vessel types in Appendix 13 are analyzed for internal pressure, including reinforced or stayed rectangular vessels with a diametral staying plate. All membrane and bending stresses are calculated and compared to the appropriate allowables. For more information, see Rectangular Vessels (App. 13) (on page 229).
Legs & Lugs Performs analysis of vessel support legs, support lugs, trunnions, and lifting lugs based on industry standard calculation techniques. The resulting stresses are compared to the AISC Handbook of Steel Construction or the ASME Code. A full table of 929 AISC beams, channels, and angles is included in the software. WRC 107 analysis to check local vessel stresses around the trunnion and the support lug is also available. Various wind and seismic codes are available for leg and lug supported vessels. For more information, see Legs and Lugs (on page 265).
Pipes & Pads Calculates the required wall thickness and maximum allowable working pressure for two pipes, and branch reinforcement requirements for the same two pipes considered as a branch and a header. Based on ANSI B31.3 rules, this module includes tables of outside diameter and wall thickness for all nominal pipe diameters and schedules. For more information, see Pipes and Pads (on page 291).
WRC 107/FEA Calculates stresses in cylindrical or spherical shells due to loading on an attachment, using the method of P.P. Bijlaard as defined in Welding Research Council Bulletin 107, including a stress comparison to VIII Div. 2 allowables for three different loading conditions. This module also contains an interface to the finite element analysis software Nozzle Pro from The Paulin Research Group. For more information, see WRC 107/537 FEA (on page 301).
Baserings Performs stress and thickness evaluation for skirts and baserings. Results from both the neutral axis shift and simplified method for basering required thickness are reported. Required skirt thickness due to weight loads and bending moments are also displayed. Tailing lugs attached to the basering are analyzed. For more information, see Base Rings (on page 327).
Thin Joints (Bellows) Performs stress and life cycle evaluations for thin walled expansion joints (bellows kind) according to ASME VIII Div. 1 appendix 26. MAWP and MAPnc are also calculated. For more information, see Thin Joints (on page 341).
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CodeCalc User's Guide
CodeCalc Overview Thick Joints Performs stress, life cycle, and spring-rate calculations for flanged and fluid expansion joints according to with ASME VIII Div. 1 appendix 5. The spring rate computation is according to TEMA eighth edition. For more information, see Thick Joints (on page 349).
Half Pipes Determines the required thickness and MAWP for half-pipe jacketed vessels according to the ASME Code Section VIII division 1 appendix EE. For more information, see Half Pipes (on page 357).
Large Openings Analyzes large openings in integral flat heads according to the ASME Code Section VIII division 1 appendix 2 and appendix 14. Required thickness, MAWP, and weights are calculated for vessels with or without an attached nozzle. For more information, see Large Openings (on page 363).
WRC 297 / PD5500 Annex G Performs the stress analysis of loads and attachments according to Welding Research Council bulletin 297 and British Standard Annex G PD:5500. The WRC 297 bulletin, published in 1984, attempts to extend the existing analysis of WRC 107 for cylinder-to-cylinder intersections. PD:5500 Annex G provides an analysis of stress in cylindrical or spherical shells due to attachment loads. Complete material databases for ASME Sec VIII and Div-1, 2; and PD 5500 are available. For more information, see WRC 297/Annex G (on page 367).
Appendix Y Flanges Performs a stress evaluation of Class1 category 1, 2, or 3 flanges that form identical flange pairs, according to the latest version of the ASME Code Section VIII Division 1 Appendix Y. For more information, see Appendix Y Flanges (on page 375).
Summary Displays a description and evaluation of all the components of a pressure vessel or heat exchanger. Design pressure, temperature, material, actual thickness, and maximum allowable working pressure (MAWP) are shown for each component.
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CodeCalc Overview
Technical Support Intergraph understands your need to produce efficient, economical, and expeditious designs. To that end, Intergraph has a staff of helpful professionals ready to address all CodeCalc issues through their eCustomer service. This system logs and tracks all queries so that every issue and every problem found is addressed with the highest quality assurance in a timely manner. Intergraph provides this service for all users with valid licenses of the program. eCustomer also provides you with a readily available knowledge base of articles on many different aspects of the program, tutorials, frequently asked questions, webinars, testimonies and more. Formal training in CodeCalc and pressure vessel analysis is also available. Intergraph conducts regular training classes in Houston and provides in-house and open attendance courses around the world. These courses focus on the modeling, analysis, and design expertise available at Intergraph. Intergraph also provides free webinars through the WebEx service.
Contact Support eCustomer https://support.intergraph.com
Phone: 1-800-766-7701
Discussion Forums Training http://65.57.255.42/ubbthreads/ubbthr http://coade.com/PVEliteCourses.aspx eads.php?ubb=cfrm Webinars http://coade.com/products/pv-elite
Events Calendar http://coade.com/Events.shtml
Updates Intergraph distributes software updates every December or January. The purchase price of PV Elite includes unlimited access to PV Elite and CodeCalc and one year of updates, maintenance, and support. Updates, maintenance, and support are available on an annual basis after the first year. Intergraph strongly encourages every user to register their copy of PV Elite to be informed of the latest build/updates for the program. Your information will not be used for third parties.
Installation CodeCalc is now automatically installed when PV Elite is installed. Please refer to the PV Elite User's Guide Installation section for more information.
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CodeCalc User's Guide
SECTION 2
CodeCalc Workflows This section describes the basic workflows of CodeCalc.
In This Section
Starting CodeCalc .......................................................................... 17 Performing an Analysis .................................................................. 17 Reviewing the Results - The Output Option .................................. 22
Starting CodeCalc 1. Start CodeCalc by selecting Component Analysis The main CodeCalc window appears.
on the PV-Elite Home tab.
Performing an Analysis 1. Click CodeCalc or if you are running the software through PV Elite, click Component Analysis on the Home tab. 2. Click New . This allows you to specify the current analysis type. on the Home tab. 3. Click Shells and Heads A blank input screen displays. Shell analysis can be defined on the Shell/Head tab of this screen. You can use the Tab key to move down the column of data. Many of the boxes display default values. 4. Type 1 in the Item Number box. You must type a value in this field or the software cannot perform the analysis. It is a good practice to number the different calculations sequentially. 5. Press Tab twice. 6. Type Spherical Head in the Description box. The information in this box can be the part number or a short description of the part. This is an optional input. 7. Select ASME Sec VIII Div 1 for the Analysis Type. The next four boxes govern the pressure and temperature.
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17
CodeCalc Workflows 8. Type 100 (assuming that you are using English units) in the Design Internal Pressure box. 9. Type 700 in the Design Temperature for Internal Pressure box. When you press Tab, the software pauses momentarily to check whether the material specified has an allowable stress greater than zero at the temperature entered. 10. Click the button to view the allowable stress. The allowable stress for SA516-70 material is 18,100 psi at this temperature. This is precisely the value that CodeCalc extracted from the material database. 11. Type 15 in the Design External Pressure box. 12. Type 650 in the Design Temperature for External Pressure box. 13. Type SA-516-70 in the Material box. The software checks the database and updates the allowable stresses. 14. Another way to select a material is from the list of materials in the database. To see this list, click
to display the materials list.
Each major material classification is divided into columns.
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CodeCalc User's Guide
CodeCalc Workflows 15. View the parameters for a specific material by clicking the material name.
16. 17. 18. 19. 20.
21. 22. 23. 24. 25. 26. 27.
These parameters can be viewed and modified using Edit/Add Materials on the Tools tab. Scan the yield stresses for an exact material match at the operating temperature. In the Joint Efficiency Longitudinal Seams box, type the value of E. This is the longitudinal joint efficiency to use in the calculator. For full radiography, type 1. Select the box for Include Hydrostatic Head Components. Type 38 in the Operating Liquid Density box. Type 54 in the Height of Liquid Column (Operating) box. Type 72 in the Height of Liquid Column (Hydrotest) box. This particular vessel is a horizontal drum that operates in a partially filled position. When the shop hydrotests the vessel, it is filled and in the horizontal position. Select the Geometry tab. Select Spherical for Type of Shell. Specify the diameter basis (OD) for an outside diameter measurement (and calculation). Type 72 in the Diameter of Shell/Head box. Type 0.5 inches in the Minimum Thickness of Pipe or Plate box. Type 0.5 inches in the Nominal Thickness of Pipe or Plate box. Type 0.0625 inches in the Corrosion Allowance box.
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CodeCalc Workflows 28. For this example there is no reinforcing ring required for internal pressure, so select None for the ring type. You have now completed the spherical head input. Your screen should look like the following figure:
You can view the drawing of the current item at any time by selecting the Drawing tab. This horizontal tank has two additional sections, the shell and the elliptical head on the other end. on the Home tab. 29. Click Shells and Heads This adds a new element. The new element has identical inputs to the element before it except for a new Item Number on the Design tab. 30. Type 2 in the Item Number box. 31. Type Cylinder in the Description box. When entering new components, be sure to type appropriate descriptions in the Description field. This will make your finished reports clearer and easier to follow. 32. Select the Geometry tab to enter the shell type. 33. Because this is a cylinder type, select Cylindrical from the Type of Shell. 34. Type 180 inches for both the Design Length of Section and the Design Length for Cylinder Volume Calculations. on the Home tab. 35. Click Shells and Heads 36. Type 3 in the Item Number box, and type Elliptical Head in the Description box. The data from the previous element is carried forward, so you will only have to modify the shell/head type. 37. Select the Geometry tab. 38. Select Elliptical for Type of Shell. 39. Type 2 for a 2:1 elliptical head. You are now ready to analyze these three components for internal pressure and hydrostatic head considerations. 40. Save the file, and click Analyze File 41. Select the Analysis tab.
20
on the Home tab.
CodeCalc User's Guide
CodeCalc Workflows Your screen will resemble the following figure:
CodeCalc User's Guide
21
CodeCalc Workflows
Reviewing the Results - The Output Option You can quickly review the results of this analysis using the Output option. On the Home tab, click Review Result. If you have analyzed the components from the input, CodeCalc automatically displays the output for you. You see the following dialog box:
There are three analyses in the output file. If you perform additional analysis runs, or analyze other components, such as nozzles, flanges, and tubesheets, the additional analyses also display. This allows you to review (and print) all of the calculations that you have done for a given vessel or job at one time. The individual report can be viewed by selecting one of the items in the report area. You can scroll up and down in the text to see all input data and results. The Summary of Internal Pressure Results shows that the required thickness is less than the actual thickness for this job, while the maximum allowable working pressure (MAWP) is greater than the design pressure. Therefore, the shell thickness you selected is acceptable. You can select more than one analysis at a time by holding down the CTRL key while selecting the items to view. You can select all reports by clicking Edit > Select All. When viewing the reports, click Next Report to move to the next component.
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CodeCalc User's Guide
CodeCalc Workflows
Printing or Saving Reports to a File Printing the Graphics To print the graphics created by your input, click Print Drawing from the Print menu.
drop down
Printing the Reports To print the output results, click Print Analysis from the Print drop down menu.
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CodeCalc Workflows
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CodeCalc User's Guide
SECTION 3
Tabs
The CodeCalc interface is divided into tabs.
In This Section
File Tab .......................................................................................... 25 Home Tab ...................................................................................... 26 Tools Tab ....................................................................................... 28 Diagnostics Tab ............................................................................. 47 ESL Tab ......................................................................................... 47
File Tab The File tab contains the following commands for managing files and printing. Some commands also appear on the quick launch toolbar. New - Creates a new file. If you have a file open with unsaved changes when you click this command, you receive a message asking if you would like to save the changes. Open - Opens an existing file. Files of type *.cci are displayed in the Open dialog box. If you have a file open with unsaved changes when you click this command, you receive a message asking if you would like to save the changes. Save - Saves a .cci file with its currently defined data. If you are saving the file for the first time, the Save As dialog box appears, so you can specify the location, which could be a local or network drive or a UNC path, and the name of the file. Save As - Saves the data in the current file as a new file with a different name or in a different location. A dialog box prompts you to specify the location, which can be a local or network drive or a UNC path, and the name of the file. The software saves all files with a .cci extension added to the name. Print Setup - Opens the Print Setup dialog box. Options are available for default printer, paper size and source, orientation, and other printer characteristics. Recent - Displays a recently used file list provides quick access to the files you use most. The last file you opened is at the top of the list. You can have up to four files in the list. Exit - Closes the open file and exits the software. If you have changed data since the file was last saved, or if you have not saved a new file, the software prompts you to save your changes.
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Tabs
Home Tab The Home tab contains the following commands for editing elements in the file. New - Creates a new file. If you have a file open with unsaved changes when you click this command, you receive a message asking if you would like to save the changes. Open - Opens an existing file. Files of type *.cci are displayed in the Open dialog box. If you have a file open with unsaved changes when you click this command, you receive a message asking if you would like to save the changes. Save - Saves a .cci file with its currently defined data. If you are saving the file for the first time, the Save As dialog box appears, so you can specify the location, which could be a local or network drive or a UNC path, and the name of the file. Print - Prints the contents of the active window. Save Analysis as Text - Save the analysis results out to a .txt file that you specify. Delete Selected Item - Deletes the current element. Shells and Heads - Inserts a shell or head element. For more information, see Shells and Heads (on page 49). Nozzles - Inserts a nozzle element. For more information, see Nozzles (on page 87). Conical Sections - Inserts a cone element. For more information, see Conical Sections (on page 109). Floating Heads - Inserts a floating head element. For more information, see Floating Heads (on page 117). Flanges - Inserts a flange element. For more information, see Flanges (on page 135). TEMA Tubesheet - Inserts a TEMA tubsheet element. For more information, see TEMA Tubesheets (on page 151). ASME Tubesheet - Inserts a ASME tubesheet element. For more information, see ASME Tubesheets (on page 183). Horizontal Vessels - Inserts a horizontal vessel element. For more information, see Horizontal Vessels (on page 213). Rectangular Vessels - Inserts a rectangular vessel element. For more information, see Rectangular Vessels (App. 13) (on page 229). Legs and Lugs - Inserts a leg or lug element. For more information, see Legs and Lugs (on page 265). Pipes and Pads - Inserts a pipe or pad element. For more information, see Pipes and Pads (on page 291). WRC 107/537 - Inserts a WRC 107/537 nozzle. For more information, see WRC 107/537 FEA (on page 301). Base Rings - Inserts a base ring element. For more information, see Base Rings (on page 327).
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CodeCalc User's Guide
Tabs Thin Joints - Inserts a thin joint element. For more information, see Thin Joints (on page 341). Thick Joints - Inserts a thick joint element. For more information, see Thick Joints (on page 349). Half Pipes - Inserts a half pipe element. For more information, see Half Pipes (on page 357). Large Openings - Inserts a large opening element. For more information, see Large Openings (on page 363). WRC 297 - Inserts a WRC 297 nozzle element. For more information, see WRC 297/Annex G (on page 367). Appendix Y Flanges - Inserts an Appendix Y flange element. For more information, see Appendix Y Flanges (on page 375). Title Page - Opens a blank report title page. You can type report titles for this group of reports. Click Insert Default Title Page to use the title page template text that you define in the TITLE.HED file in the defined System folder. Project Data - Opens the Project Data dialog box. You can type title lines for Company, Vessel, and Engineer. These lines appear at the top of each page of the printed reports. Cascade Windows - Arranges all open windows from the top-left to bottom-right. Horizontal Tile - Arranges all open windows stacking them on top of each other. Vertical Tile - Arranges all open windows side-by-side. Analyze File - Performs the analysis on all components in the file. Analyze Selected Items - Performs calculations for selected analysis types. Review Result - Opens the Output Processor to view the analysis results. Append Result - Adds the analysis results to the end of the previous analysis results.
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Tabs
Tools Tab The Tools tab contains the following utility commands: Configuration - Specifies software parameters. For more information, see Configuration Dialog Box (on page 29). Select Units - Specifies a .fil units file. Select the needed file in the Open dialog box. The software internally uses conventional American units. Choose another .fil file, such as SI, to display values in other units. Create/Review Units - Creates a new .fil units file or edits an existing .fil file. For more information, see Make Unit (see "Create/Edit Units File" on page 32). Units Conversion Viewer - Converts a value in one set of units to a value in another set of units. Each tab of the Units Conversion Utility dialog box contains a category of conversions, such as length, area, pressure, or force. Edit/Add Materials - Creates and edits user-defined materials in the CodeCalc material database. For more information, see Material Database Editor (on page 34). Calculator - Opens the Windows calculator. You can calculate a value, select the value, and use Edit > Copy and Edit > Paste to transfer the value into a CodeCalc field.
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CodeCalc User's Guide
Tabs
Configuration Dialog Box Sets options for software parameters. Computation Control Tab (Configuration Dialog Box) (on page 29) Miscellaneous Tab (Configuration Dialog Box) (on page 30)
Computation Control Tab (Configuration Dialog Box) Sets options for computation methods used in the software. Compute Increased Nozzle Thickness? - Specifies that the minimum nozzle thickness (trn) will be the maximum of: trn = (.134, trn for internal pressure) less than or equal NPS 18 trn = (OD/150, trn for internal pressure) greater than NPS 18 This option is useful when nozzle loadings are unknown, such as when a pressure vessel is designed and built long before the attached piping system. By using this option in addition to UG-45, you have some additional metal available to satisfy thermal bending stresses. This option is not selected by default.
These formulae are not in the ASME Code, but are commonly used in industry.
You can also specify the minimum wall thickness of the nozzle, Trn, using Nozzles . The minimum wall thickness value then overrides the value calculated by this option. Calculate F in Flohead if the Pressure is Zero? - Specifies that the factor F is calculated in the design of a floating head. F is a direct function of the internal pressure. If the internal pressure is 0, then F is equal to 0, such as in the flange bolt up case where there is no internal pressure when bolting up the unit. The code can be interpreted to mean that F should always be calculated. This option is conservative and is not selected by default. Use P instead of MAWP for UG-99B? - Specifies that P is used instead of maximum allowable working pressure (MAWP) when calculating hydrostatic test pressure on vessels according to code paragraph UG-99(b). The equation would normally be: Test Pressure = 1.5 * MAWP * Stest/Sdesign (for A-98 Addenda) or Test Pressure = 1.3 * MAWP * Stest/Sdesign (for post 2001 edition of ASME VIII Division 1) The code, in note 32, states that the MAWP can be assumed to be the same as the design pressure when calculations are not made to determine the MAWP. This allows for lower test pressures. This option is not selected by default and should be used with caution. Print Water Volume in Gallons/Liters? - For US units, specifies volume in US gallons instead of cubic diameter units (such as cubic feet). For other units, specifies volume in liters instead of cubic diameter units (such as cubic mm). This option is not selected by default.
A US gallon (3.7854 liters) is smaller than an Imperial gallon (4.5461 liters) as defined in Europe. The software considers only the US gallon. Use Calculated Value of M for Torispherical Heads in UG-45 b1? - Specifies calculation of the required head thickness at the location of the nozzle by the rules of paragraph UG-32 or by the rules in Appendix 1, according to code interpretation VIII-1-95-13. This option is selected by default and should always be selected. The code in paragraph UG-45 requires a calculation of the required head thickness at the location of the nozzle. This sometimes leads to the incorrect assumption that the thickness may
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Tabs be calculated according to paragraph UG-37. However the code interpretation, VIII-1-95-133, issued December 1996, states: Question: Does the definition of the required thickness tr for a formed head given in the nomenclature of UG-37(a) in section VIII, Division 1 apply when determining the minimum nozzle neck thickness in UG-45(b)(1)? Reply: No, see UG-32. Use Pre-99 Addenda? - Specifies the use of the material database preceding the 1999 Addendum. This is only relevant to Division 1 of ASME VIII. This option is selected by default. In the 1999 addendum to ASME Section VIII, Division 1, the allowable design stresses (S) were increased. It is recognized that it may be necessary to re-rate vessels constructed before this addendum came into effect. Use Code Case 2260? (for elliptical and torispherical heads) - Specifies the use of modified equations in the Code Case 2260, May 20, 1998, to calculate the required thickness of elliptical and torispherical heads. A thinner head is typically designed. Code Case 2260, Alternate Design Rules for Ellipsoidal and Torispherical Formed Heads, applies to Section VIII Division 1. This option is not selected by default. Do not apply Bolt Spacing factor for flanges, tubesheets, and floating heads? - For the design of heat exchanger flanges and tubesheets, ASME and TEMA (like Taylor-Forge) provide a correction factor when the actual bolt spacing (circumferentially) exceeds the allowable bolt spacing. The correction factor is then multiplied by the moment to design a thicker flange. The use of this term is very standard in industry and is used in other pressure vessel design Codes such as PD-5500 and EN-13445. ASME Secion VIII introduced the bolt space correction factor in the 2010 edition. This factor will be used in the design. The ASME code also states that for computing the rigidity index, flange moments without this correction factor should be used. If you do not want to use the factor, then check this box. This factor tries to accounts for any possible opening of the flange faces in the area between any two bolts. The default is to use the bolt space correction factor. Material Database Year - Specifies the year of the material database. Each material year contains a complete database listing of materials, allowable design stresses, and other relevant properties. Select Current or an earlier year. If a different material database is selected after creating a set of components, update the component materials by re-selecting them from the material database before performing calculations.
Miscellaneous Tab (Configuration Dialog Box) Sets miscellaneous options used in the software. Report Content - Specifies the amount of detail and the length of printed reports. Select Summary to print a short report. Select Detailed to print a normal report that includes formulas and substitutions. External Pressure Printout in Rows? - Specifies the style for printing external pressure results rows and columns in reports. Select to print the values in rows to reduce report length. Clear to print the values in columns. This option is selected by default. Reload last file at startup? - Specifies loading the last file opened the next time the software is started. Syntax Highlighting In Output Reports - Specifies color-coding of results in reports. Select this option to print warnings in red or blue type, and errors or fatal problems in red type. This option is selected by default.
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CodeCalc User's Guide
Tabs When syntax highlighting is used, output generation on-screen and to a Microsoft Word file is slightly slower. Do not Print Extended ASCII Characters in Output Reports - Specifies printing of extended ASCII characters in reports. Extended ASCII characters such as superscript 2 are not displayed properly on some localized versions of Windows, such as Chinese, Korean, and Japanese. If you are having difficulty with extended ASCII characters, select this option. When selected, the software uses ASCII characters. Default Units File - Specifies the .fil units file to use when creating a new CodeCalc file. Select a units file to use for both data input and calculated results. This option is not used to change the units of the currently opened CodeCalc file. In this case, use Set Units. For more information, see Tools Tab (on page 28). Graphics Display Driver - Specifies the driver used for generating component and model graphic images on the screen. Open GL is the default value. If your computer does not display images correctly, select MSW, the Microsoft Windows driver. Nozzle Pro Installation Folder - Specifies the location of Nozzle Pro software, used to perform finite element analysis (FEA) of nozzles. FEA is more accurate and detailed than local load procedures such as WRC107, WRC297, and PD 5500 Annex G. Nozzle Pro is separately-purchased software from Paulin Research Group http://www.paulin.com. Default File Save Folder - Specifies the default location for saving input files. Enable Auto Save - Specifies automatically saving the input file. Select this option and enter the time interval between saves. Perform Background Saves (Silent)? - Specifies silently saving the input file. This option is available when Enable Auto Save is selected. Select to auto save without software prompts. Clear to get software prompts after the time interval specified for Enable Auto Save.
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Tabs
Create/Edit Units File The Create/Review Units File utility allows you to create a new custom units file or edit an existing units file for use with PV Elite or CodeCalc. The utility is available on the Tools tab > Create/Review Units . You can also double-click MakeUnit.exe in the product delivery folder. Delivered units files have the .fil extension and are in the C:\Users\Public\Public Documents\Intergraph CAS\PVELITE\2013\System folder. Many unit systems are delivered, such as English, MM, SI, Inches, and Newtons. Unicode systems are delivered for use in China, Japan, Taiwan, and Korea, where multibyte character sets are used. You can save new units files to the system folder or to another folder.
Use Tools tab > Configuration
Use Tools tab > Select Units to select a new units file. The data in your job file is immediately converted to the new units.
to specify the units file to use at startup.
Units File Dialog Box (on page 33) What do you want to do?
Create a new units file (on page 32) Edit an existing units file (on page 32)
Create a new units file 1. On the Tools tab, click Create/Review Units . The units file dialog box displays. Constant has a default value of 1 for each type of unit. 2. Do one of the following for each type of unit: Select defined values for Constant or User Unit. Type values for or Constant and User Unit. . 3. Click Save and Exit The Save As dialog box displays. 4. Select a folder path and type a file name. 5. Click Save. The Save As dialog box and the Units File dialog box close.
Edit an existing units file 1. On the Tools tab > click Create/Review Units The units file dialog box displays.
.
. 2. Click Open The Open dialog box displays. 3. Select an existing .fil units file and click Open.
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Tabs 4. Change unit types as needed by doing one of the following: Select defined values for Constant or User Unit. Type values for or Constant and User Unit. . 5. Click Save and Exit The Save As dialog box displays. 6. Select a folder path and type a file name. You can also use the same file name to replace the open file with the new unit values. 7. Click Save. The Save As and Units File dialog boxes close.
Units File Dialog Box Specifies units and constants for a units file. Name - Displays the type of unit, such as Length, Area, or Pressure. System Unit - Displays the default system unit used as a multiplier for conversions, such as feet, sq-inches, and psig. Constant - Select a defined conversion constant used as a multiplier for conversions, or type your own value. User Unit - Select a defined unit for the conversion, or type your own unit.
If you select a defined Constant, the software changes User Unit to the correct unit. If you select a defined User Unit, the software changes Constant to the correct value. If you type your own value for Constant and User Unit, you must manually ensure that the combination provides the needed conversion. Open - Open an existing units file for editing. Save - Saves the units file.
Save and Exit - Saves the units file and closes the dialog box. Help - Opens the help.
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Tabs
Material Database Editor The Material Database Editor utility allows you to add custom materials to a delivered ASME, PD:5500, or EN-13445 material database for use with PV Elite or CodeCalc. For a YouTube demonstration, visit: http://www.youtube.com/watch?v=GEtIRO4PwCw. While the video is centered around PV Elite, it works much the same way in CodeCalc. The utility is available from: Tools > Edit/Add Materials MatEdit.exe, found in the [Product Folder]\COADE\PVElite\ folder When you use this utility, material database files with the .bin extension are created in the [Product Folder]\COADE\PVElite\System Backup folder. These files contain only the custom materials you have added. The custom materials can then be merged into the main material databases.
The delivered databases contain allowed material for the current codes. You typically only add custom material if you are required to use an outdated material, or need to add material from a different code. Have the appropriate code available when adding new material. You will enter code-based material properties such as Chart Data, Material Band, and S Factor. The properties needed vary with the database that you are editing.
Material Properties (on page 35) What do you want to do?
Create a new custom material (on page 34) Create a custom material based on an existing material (on page 35)
Create a new custom material 1. Click Tools > Edit/Add Materials and select the ASME, PD:5500, or EN-13445 material database. . 2. Click Add A new row named New Material appears in the grid of the Material Database view in the right pane. 3. In the Material Properties view in the left pane, type values for the new material. As you type values, check the Stress vs. Temperature graph in the right pane. Stress must not increase as temperature decreases. 4. Repeat these steps for each new material that you want to add. 5. Click Save 6. Click Merge
to save the new material to a user database file. to add the user database to the material database of the software.
After merging, the custom material now appears at the bottom of the material database list for any command using the material database in PV Elite or CodeCalc.
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CodeCalc User's Guide
Tabs
Create a custom material based on an existing material 1. Click Tools > Edit/Add Materials and select the ASME, PD:5500, or EN-13445 material database. . 2. Click Edit The contents of the software database appear in the grid of the Material Database view in the right pane. 3. Select a material for the Material Database grid. and click Yes on the confirmation dialog box. 4. Click Select The copied material appears in a new row in the grid of the Material Database view. 5. In the Material Properties view in the left pane, type new values as needed.
You must change Material Name so that the name is unique in the user database and in the material database after merging. As you type values, check the Stress vs. Temperature graph in the right pane. Stress must not increase as temperature decreases.
6. Click Save
to save the new material to a user database file.
7. Click Merge
to add the user database to the material database of the software.
After merging, the custom material now appears at the bottom of the material database list for any command using the material database in PV Elite or CodeCalc.
Material Properties The following code-based values are typically used as material properties. Material Name - Type an allowed external pressure chart name. The software uses the chart name to calculate the B value for all external pressure and buckling calculations. If you type a valid value for Material Name, the software will look into its database and determine the external pressure chart name for this material and enter it into this cell. The program will also determine this chart name when you select a material name from the material selection window. The following are the allowed external pressure chart names: Carbon Steel CS-1
Carbon and Low Alloy Sy30000
CS-3
Carbon and Low Alloy Sy3/4)
NFN-20
Work Hardened Nickel
NFT-1
Unalloyed Titanium, Grade 1
NFT-2
Unalloyed Titanium, Grade 2
NFT-3
Titanium, Grade 1
NFZ-1
Zirconium, Alloy 702
NFZ-2
Zirconium, Alloy 705
Elastic Modulus Reference # The elastic modulus reference number is a value that points to or corresponds to a set of data set forth in ASME Section II Part D, tables TM-1, 2 and so on. Unfortunately, many materials have a composition or UNS number that does not match the criteria of what is supplied in the ASME Code. In these cases, the reference number will be brought in as zero. If this happens, you will need to enter in an appropriate value. Reference Number
Table
Description/UNS Number
1
TM-1
Carbon Steels with C 0.3%
3
TM-1
Material Group A
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Tabs
38
Reference Number
Table
Description/UNS Number
4
TM-1
Material Group B
5
TM-1
Material Group C
6
TM-1
Material Group D
7
TM-1
Material Group E
8
TM-1
Material Group F
9
TM-1
Material Group G
10
TM-1
S13800
11
TM-1
S15500
12
TM-1
S45000
13
TM-1
S17400
14
TM-1
S17700
15
TM-1
S66286
16
TM-2
A03560
17
TM-2
A95083
18
TM-2
A95086
19
TM-2
A95456
20
TM-2
A24430
21
TM-2
A91060
22
TM-2
A91100
23
TM-2
A93003
24
TM-2
A93004
25
TM-2
A96061
26
TM-2
A96063
27
TM-2
A92014
28
TM-2
A92024
29
TM-2
A95052
30
TM-2
A95154
31
TM-2
A95254
32
TM-2
A95454
33
TM-2
A95652
34
TM-3
C93700
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Tabs Reference Number
Table
Description/UNS Number
35
TM-3
C83600
36
TM-3
C92200
37
TM-3
C92200
38
TM-3
C28000
39
TM-3
C28000
40
TM-3
C65500
41
TM-3
C66100
42
TM-3
C95200
43
TM-3
C95400
44
TM-3
C44300
45
TM-3
C44400
46
TM-3
C44500
47
TM-3
C64200
48
TM-3
C68700
49
TM-3
C10200
50
TM-3
C10400
51
TM-3
C10500
52
TM-3
C10700
53
TM-3
C11000
54
TM-3
C12000
55
TM-3
C12200
56
TM-3
C12300
57
TM-3
C12500
58
TM-3
C14200
59
TM-3
C23000
60
TM-3
C61000
61
TM-3
C61400
62
TM-3
C65100
63
TM-3
C70400
64
TM-3
C19400
65
TM-3
C60800
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Tabs
40
Reference Number
Table
Description/UNS Number
66
TM-3
C63000
67
TM-3
C70600
68
TM-3
C97600
69
TM-3
C71000
70
TM-3
C71500
71
TM-4
N02200
72
TM-4
N02201
73
TM-4
N04400
74
TM-4
N04405
75
TM-4
N06002
76
TM-4
N06007
77
TM-4
N06022
78
TM-4
N06030
79
TM-4
N06045
80
TM-4
N06059
81
TM-4
N06230
82
TM-4
N06455
83
TM-4
N06600
84
TM-4
N06617
85
TM-4
N06625
86
TM-4
N06690
87
TM-4
N07718
88
TM-4
N07750
89
TM-4
N08020
90
TM-4
N08031
91
TM-4
N08330
92
TM-4
N08800
93
TM-4
N08801
94
TM-4
N08810
95
TM-4
N08825
96
TM-4
N10001
CodeCalc User's Guide
Tabs Reference Number
Table
Description/UNS Number
97
TM-4
N10003
98
TM-4
N10242
99
TM-4
N10276
100
TM-4
N10629
101
TM-4
N10665
102
TM-4
N10675
103
TM-4
N12160
104
TM-4
R20033
105
TM-5
R50250
106
TM-5
R50400
107
TM-5
R50550
108
TM-5
R52400
109
TM-5
R56320
110
TM-5
R52250
111
TM-5
R53400
112
TM-5
R52402
113
TM-5
R52252
114
TM-5
R52404
115
TM-5
R52254
116
TM-5
R60702
117
TM-5
R60705
118
TM-1
12Cr-13Cr Group F
119
TM-1
20+Cr Material Group G
220
TEMA
Ni-Mo Alloy B
221
TEMA
Tantalum
222
TEMA
Tantalum with 2.5% Tungsten
223
TEMA
7 MO (S32900)
224
TEMA
7 MO PLUS (S32950)
225
TEMA
17-19 CR Stn Steel
226
TEMA
AL-6XN Stn Steel (NO8367)
227
TEMA
AL-29-4-2
CodeCalc User's Guide
41
Tabs Reference Number
Table
Description/UNS Number
228
TEMA
SEA-CURE
229
TEMA
2205 (S31803)
230
TEMA
3RE60 (S31500)
Thermal Expansion Coefficient Reference #
42
Reference Number
Table
Description/UNS Number
1
TE-1
Carbon & Low Alloy Steels, Group 1
2
TE-1
Low Alloy Steels, Group 2
3
TE-1
5Cr-1Mo and 29Cr-7Ni-2Mo-N Steels
4
TE-1
9Cr-1Mo
5
TE-1
5Ni-¼4Mo
6
TE-1
8Ni and 9Ni
7
TE-1
12Cr,13Cr and 13Cr-4Ni Steels
8
TE-1
15Cr and 17Cr Steels
9
TE-1
27Cr Steels
10
TE-1
Austenitic Group 3 Steels
11
TE-1
Austenitic Group 4 Steels
12
TE-1
Ductile Cast Iron
13
TE-1
17Cr-4Ni-4Cu, Condition 1075
14
TE-1
17Cr-4Ni-4Cu, Condition 1150
15
TE-2
Aluminum Alloys
16
TE-3
Copper Alloys C1XXXX Series
17
TE-3
Bronze Alloys
18
TE-3
Brass Alloys
19
TE-3
70Cu-30Ni
20
TE-3
90Cu-10Ni
21
TE-4
N02200 and N02201
22
TE-4
N04400 and N04405
23
TE-4
N06002
CodeCalc User's Guide
Tabs Reference Number
Table
Description/UNS Number
24
TE-4
N06007
25
TE-4
N06022
26
TE-4
N06030
27
TE-4
N06045
28
TE-4
N06059
29
TE-4
N06230
30
TE-4
N06455
31
TE-4
N06600
32
TE-4
N06625
33
TE-4
N06690
34
TE-4
N07718
35
TE-4
N07750
36
TE-4
N08031
37
TE-4
N08330
38
TE-4
N08800,N08801,N08810,N08811
39
TE-4
N08825
40
TE-4
N10001
41
TE-4
N10003
42
TE-4
N10242
43
TE-4
N10276
44
TE-4
N10629
45
TE-4
N10665
46
TE-4
N10675
47
TE-4
N12160
48
TE-4
R20033
49
TE-5
Titanium Gr 1,2,3,7,11,12,16 and 17
50
TE-5
Titanium Grade 9
51
TEMA
5Cr-1/2Mo
52
TEMA
7Cr-1/2Mo & 9Cr-1Mo
53
TEMA
Ni-Mo (Alloy B)
54
TEMA
Nickel (Alloy 200)
CodeCalc User's Guide
43
Tabs Reference Number
Table
Description/UNS Number
55
TEMA
Copper-Silicon
56
TEMA
Admiralty
57
TEMA
Zirconium
58
TEMA
Cr-Ni-Fe-Mo-Cu-Cb (Alloy 20Cb)
59
TEMA
Tantalum
60
TEMA
Tantalum with 2.5% Tungsten
61
TEMA
17-19 CR (TP 439)
62
TEMA
AL-6XN
63
TEMA
2205 (S31803)
64
TEMA
3RE60 (S31500)
65
TEMA
7 MO (S32900)
66
TEMA
7 MO PLUS (S32950)
67
TEMA
AL 29-4-2
68
TEMA
SEA-CURE
69
TEMA
80-20 Cu-Ni (C71000)
Minimum Thickness (in.) - Type the minimum allowable thickness for the material. If the material has no minimum thickness, type -1. Maximum Thickness (in.) - Type the maximum allowable thickness for the material. If the material has no maximum thickness, type -1. Creep Temperature (F) - Type the temperature at which the material is governed by time dependent properties. MDMT Exemption Temperature (F) - When the material uses an impact tested product specification, type the impact temperature. Otherwise, type 1.
Product Form Type an integer that designates the product form of the material.
44
Form Value
Product Form
1
Plate
2
Forgings
3
Seamless pipe
4
Welded pipe
5
Welded tube
6
Seamless tube
CodeCalc User's Guide
Tabs 7
Bolting
8
Castings
9
Fittings
10
Seamless/welded pipe
11
Seamless/welded tube
12
reserved
13
Seamless pipe and tube
14
Pipe
15
Bar
16
Sheet
17
Tube
18
Forged pipe
19
Seamless/welded fitting
20
Drawn seamless tube
21
Condenser & heat exchanger tubes
22
Seamless extruded tube
23
Rod
24
Seamless and welded fittings
25
Welded fittings
26
Seamless fittings
27
Finned tube
28
Seamless U-bend tube
29
Welded condenser tube
Impact Reduction Temperature (F) - When the material is eligible for a -5ºF temperature reduction according to UCS-66(g), type -5. Otherwise, type 0.
Material Band The material band is used to determine the modulus of elasticity and coefficient of thermal expansion for that type of material. Material Band
Basic Material Type/composition
M0
Carbon steel
M1
Carbon manganese steel
M2
Carbon molybdenum steel
CodeCalc User's Guide
45
Tabs
46
M4
Low alloy MG Cr Mo V steel
M5
3.5Ni
M6
9Ni
M7
1-1.5Cr .5Mo
M8
.5Cr .5Mo .25V
M9
2.25Cr 1Mo
M10
5Cr .5Mo
M11
9Cr1Mo
M12
12Cr1Mo1V
CodeCalc User's Guide
Tabs
Diagnostics Tab The Diagnostics tab contains commands for troubleshooting installation problems: CRC Check - Performs a cyclic redundancy check on each of the delivered software dynamic link library (dll) files and checks that the files are correctly copied to the hard drive of your computer. Use this command if your software is behaving erratically. Build Version Check - Checks the software build version of each executable file. See the Intergraph web site www.coade.com/fpvelite.htm for the latest build information. Error Review - Reviews errors that may have been generated at startup or during program execution. DLL Version Check - Checks that the delivered software dll files are current. Dlls of the incorrect version can cause the software to run incorrectly.
ESL Tab The following commands are available on the Esl (External Software Lock) tab. Show Data - Displays the encrypted data on your external software lock (ESL) key that allows you to check the status of the device. The data can also be saved to a log file. This information is useful for updating the software and for remaining current with your Intergraph license. Phone Update or Generate Access Codes -Creates access codes needed to update the ESL when a new version of the software has been released. Enter Re-Authorization Codes - Allows ESL update codes to be entered. Check HASP Driver Status - - See Admin Control Center Install the HASP Device Driver - See Admin Control Center. Admin Control Center - Displays all information related to the HASP Driver. The HASP Keys tab shows all available keys, whether local or on the network. The Access Log tab displays all instances of a license being used on the network keyin on the host computer.
CodeCalc User's Guide
47
Tabs
48
CodeCalc User's Guide
SECTION 4
Shells and Heads Home tab: Components > Add New Shell/Head Performs internal and external pressure design of vessel and exchanger components using the rules in the ASME Code, Section VIII, Division 1, 2010 Edition. This program considers static liquid head in the pressure design, performs stiffening ring calculations, sizes stiffening rings, and computes weld shear flows on stiffening ring welds. Jackets can be attached to the vessel and are analyzed per Appendix 9 of ASME Sec. VIII Div. 1 code. This module also contains information for performing fitness for service evaluation per API-579.
Purpose, Scope and Technical Basis (Shells) This module calculates the required thickness and maximum allowable working pressure (MAWP) for cylindrical shells and heads under internal or external pressure. The program is based on the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2010 Edition 2004 A-06. Under internal pressure, the program analyzes six types of heads or shells, using applicable code formulae as follows: Shell or Head Type
ID Basis
OD Basis
Cylinder
UG-27 (c) (1)
App 1-1 (a) (1)
Elliptical
App 1-4 (c) (1), App 1-4 (f) App 1-4 (c) (2), App 1-4 (f)
Torispherical
App 1-4 (d) (3), App 1-4 (f) App 1-4 (d) (4), App 1-4 (f)
Spherical Head or Shell
UG-27 (d) (3)
App 1-1 (a) (2)
Conical Head or Shell
UG-32 (g)
App 1-4 (e) (1)
Flat Head
UG-34 (1)and (3)
Elliptical heads with aspect ratios between 1.0 and 3.0 (typically 2.0) may be analyzed. Torispherical heads with knuckle radii between 6% and 100% of the crown radius may be analyzed. The thin, large diameter elliptical or torispherical head is also checked using App. 1-4 (f). Conical heads and sections with half apex angles up to 30 degrees may be analyzed. Reinforcement at the large and small ends of the cone should be analyzed in the CONICAL program. Welded flat heads, circular or non-circular, are analyzed in this program. Bolted flat heads are analyzed in the FLANGE program. Bolted dished heads under internal or external pressure are analyzed in the FLOHEAD program. Under external pressure program analyzes five types of heads or shells, using applicable code formula as follows: Shell or Head Type
Code Paragraph
Cylinder
UG-28 (c)
CodeCalc User's Guide
49
Shells and Heads Elliptical
UG-33 (d)
Torispherical
UG-33 (e)
Spherical Head or Shell
UG-33 (c) and UG-28 (d)
Conical Shell or Head
UG-33 (f)
All of these shell or head types are analyzed for diameter to thickness ratios greater than 10. Elliptical heads with aspect ratios between 1.0 and 3.0 may be analyzed. Torispherical heads with any crown radius may be analyzed. Reinforcement at the large and small end of conical heads or sections is analyzed in the CONICAL program.
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CodeCalc User's Guide
Shells and Heads The SHELL program takes full account of corrosion allowance. You enter actual thickness and corrosion allowance, and the program adjusts thicknesses and diameters when making calculations for the corroded condition. Geometry is shown below. In addition, this module also accounts for static liquid head for shell components. For carbon steel vessels, normalized material can be used for UCS-66 calculations.
Figure 1: Shell Geometry
Figure 2: Head Geometry
CodeCalc User's Guide
51
Shells and Heads
API 579 Introduction Fitness For Service (FFS) assessments using API Recommended Practice 579 (API RP 579) are performed to assess the operation safety and reliability of process plant equipment, such as pressure vessels, piping, and/or tanks - for some desired future period. The assessment procedure provides an estimate of the remaining strength of the equipment in its current state, which may become degraded while in-use from its original condition. Typical FFS assessments entail: Identifying the flaw type and damage mechanism. Considering the applicability and limitations of the specific flaw type procedure. Reviewing data requirement and gathering the data. Applying the assessment techniques and comparing the result to the acceptance criteria. Estimating the remaining life for the inspection interval. Applying remediation as appropriate. Applying in-service monitoring as appropriate. Documenting the results. Common degradation mechanisms include general corrosion, localized corrosion, pitting corrosion, blister, mechanical distortion, and so on. The procedures on how to assess these common degradations or flaws are discussed in the sections described in the Table of Contents for API RP 579 and listed below: Section 1 – Introduction Section 2 – Fitness-For-Service Engineering Assessment Procedure Section 3 – Assessment of Equipment for Brittle Fracture Section 4 – Assessment of General Metal Loss Section 5 – Assessment of Local Metal Loss Section 6 – Assessment of Pitting Corrosion Section 7 – Assessment of Blisters and Laminations Section 8 – Assessment of Weld Misalignment and Shell Distortions Section 9 – Assessment of Crack-Like Flaws Section 10 – Assessment of Component Operating in the Creep Regimes Section 11 – Assessment of Fire Damage
Purpose, Scope, and Technical Basis CodeCalc supports the following flaw assessments for cylindrical shells, simple cones, and formed heads: Section 4, General Metal Loss. Section 5, Local Metal Loss. Section 6, Pitting Corrosion. There are three levels of assessments available for each flaw type. Level 1 - Typically involves a simplified method using charts, simple formulae, and conservative assumptions. Level 2 - Generally requires a more detailed evaluation and produce more accurate results Level 3 - Allows flaw assessments using a more sophisticated method such as FEA. CodeCalc provides only Level 1 and Level 2 assessments. In each assessment level, the respective remaining life or the de-rate value of MAWP is calculated depending on passing or failing acceptance criteria.
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CodeCalc User's Guide
Shells and Heads Section 4 covers flaw assessment procedures for components subject to general metal loss resulting from corrosion and/or erosion. Meanwhile Section 5 covers the analysis of local metal loss or Local Thin Areas (LTAs), which include groove-like flaws or gouges. In general, flaw assessments using Section 4 criteria produce more conservative results. The differences between Section 4 and 5 when applied to LTAs are as follows: Section 4 - Rules for all Level 1 and 2 assessments are based on the Average Thickness Averaging approach, which is combined with the ASME Code rules to determine the acceptability for continued operation. Section 5 - Rules for all Level 1 and Level 2 assessments are based on establishing a Remaining Strength Factor (RSF), which is used to determine the acceptability for continued operation. The Assessment of General Metal Loss described in Section 4 can be performed using either point thickness (random type readings) or profile thickness (grid type readings) measurement data. API RP 579 requires a minimum of 15 data measurement points be used for the analysis. The localized metal loss assessment (described in Section 5), can only be performed using profile thickness data according to a grid setup as shown in Figure 10.3. Two data entry types are provided in the Profile Type selection list; Grid and Critical Thickness Profile (CTP). The number of rows and columns are set by entering the number of points in both the circumferential and longitudinal directions. The total number of data inputs provided are 256 for both point and profile thickness data measurements.
Figure 3: Profile Thickness Inspection Planes
For most evaluations, it is recommended to first perform the assessment using Section 4, then perform Section 5 if necessary. The rules in Section 4 have been structured to provide consistent results with Section 5. However, it is the responsibility of the user to review the Assessment Applicability and Limitation whenever the assessment changes. API 579 Section 4 limitations for Level 1 and Level 2 assessments are as follows: The original design is in accordance with a recognized code or standard.
CodeCalc User's Guide
53
Shells and Heads
The component is not operating in the creep range. The region of metal loss has relatively smooth contours without notches. The component is not in cyclic service (less than 150 total cycles). The component under evaluation does not contain crack-like flaws. The component under evaluation has a design equation, which specifically relates pressure and/or other loads, as applicable, to a required wall thickness. With some exception, the following specific components do not have equations relating pressure and/or other loads to a required wall thickness may be evaluated using Level 2 assessments: Pressure vessel nozzles and piping branch connections. Cylinder to flat head junctions. Integral tubesheet connections Flanges Piping systems.
Currently, CodeCalc does not support API 579 analysis on nozzle, flange, tubesheet, flathead, and piping system components. The following limitations on applied loads are satisfied Level 1 assessment - Components are subject to internal and/or external pressure (negligible supplemental loads). Level 2 assessment - Components are subject to internal and/or external pressure and/or supplemental loads such as weight, wind and earthquake. Limitations for API 579 Section 5 Level 1 and Level 2 assessments are similar to the limitations for Section 4 with the following additions: The components cannot be subjected to external pressure, or if the flaw is located in the knuckle region of elliptical head (outside of the 0.8D region), torispherical/toriconical head, or conical transition. The material component is considered to have sufficient material toughness. Special provisions are provided for groove-like flaws such as: Groove (no mechanical cold work). Gouge (mechanical cold work). For more details, refer to Section 4 and Section 5 in the API Recommended Practice 579. Section 6 covers flaw assessment procedures for components that are subjected to pitting damages as described below: Widespread Pitting. Localized Pitting. Region of Local Metal Loss Located in an Area of Widespread Pitting. Pitting Confined within a Region of Localized Metal Loss. Pitting damage can occur on the inside, outside, or both sides of the component surfaces. For components with pittings on both surfaces, be sure to indicate the location of each pit-couple in the data entry table. Pitting damage is described using pit-couples, each is composed of two pits that are separated by a solid ligament. The procedure for determining pit-couples is described in the API 579 paragraph 6.3.3.3. A representative number of pit couples measurements in the damage area should be used. If the pit flaw is uniform then a minimum of 10 pit-couple measurements should be used. For non-uniform pit flaw, additional pit-couple measurements are required. CodeCalc can analyze up to 36 pit-couples measurements.
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CodeCalc User's Guide
Shells and Heads The limitations for API 579 Section 6 Level 1 and Level 2 assessments are similar to the limitations for Section 5 Level 1 and Level 2 assessments. For more details, refer to API RP 579 Section 6.
Discussion of Results (Shells) An effort has been made to use the same variable names and reporting formats as are used in the API Recommended Practice 579 book. A summary at the end of the analysis of each level is written. Depending on the pass or fail criteria, either the remaining life using the thickness (or MAWP) approach is computed or a de-rating MAWP is printed. As suggested in the API Recommended Practice 579 book, the following, or combinations thereof can be considered when the component does not meet the Level 2 Assessment requirements: Re-rate, repair, and retire the component. Adjust the FCA by applying remediation techniques. Adjust the weld joint efficiency factor, E, by conducting additional examinations and repeat the assessment. Conduct a Level 3 assessment.
Shells/Heads Tab Specifies parameters for shell and head design. Item Number - Enter an ID number for the item. This can be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Analysis Type - Specifies the analysis type: ASME Sec VIII Div. 1 API 579 - Fitness for Service Design Internal Pressure - Enter the internal design pressure. You must define either the design pressure or the minimum metal thickness, preferably both. Design pressure is used to determine the required thickness and minimum metal thickness is used to determine the Maximum Allowable Working Pressure. Design Temperature for Internal Pressure - Enter the temperature associated with the internal design pressure. The software automatically updates materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Design External Pressure - Enter the design pressure for external pressure analysis. This should be a positive value, such as 14.7 psig. If you enter a zero in this field the program does not perform external pressure calculations. 0.00 - No external calculation. 14.7 - Full vacuum calculation. Design Temperature for External Pressure -Enter the temperature associated with the external design pressure. The design external pressure at this temperature is a completely different design case than the internal pressure case. Therefore this temperature may be different than the temperature for internal pressure. Many external pressure charts have both lower and upper limits on temperature. If your design temperature is below the lower limit, use
CodeCalc User's Guide
55
Shells and Heads the lower limit as your entry to the program. If your temperature is above the upper limit, the component may not be designed for vacuum conditions. Shell Section Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Joint Efficiency, Longitudinal Seams - Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. See Section VIII, Div. 1, Table UW-12 for help in determining this value. 1.00 - Full Radiography 0.85 - Spot X-ray 0.70 - No radiography The joint efficiency in this (and all other) ASME Code formulas is a measure of the inspection quality on the weld seam. In general, weld seams that receive full radiography have a joint efficiency of 1.0. Weld seams that receive spot radiography have a joint efficiency of 0.85. Weld seams that receive no radiography have a joint efficiency of 0.7. Seamless components have a joint efficiency of 1.0. In addition to the basic rules described above, the Code requires that no two seams in the same vessel differ in joint efficiency by more than one category of radiography. For example, if circumferential seams receive no radiography (E=0.7) then longitudinal seams have a maximum E of 0.85, even if they receive full radiography. The practical outworking of this is that circumferential seams, which are usually less highly stressed, may be spot radiographed (E=0.85) while longitudinal seams are fully radiographed. This provides the same metal thickness at some savings in inspection costs. Include Hydrostatic Head Components? - If your shell or head design needs to account for hydrostatic liquid head, select this box. CodeCalc adds the hydrostatic pressure head to the internal design pressure for the required thickness calculation. Operating Liquid Density - Enter the density of the operating fluid. This value is multiplied by the height of the liquid column in order to compute the static head pressure. You can enter a number of specific gravity units and CodeCalc converts the number to the current set of units. To do this, enter a number followed by the letters sg. Typical specific gravities and densities are shown below in lbs/ft^3.
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CodeCalc User's Guide
Shells and Heads Convert the densities to your units. Name
Specific Gravity
Density (lb/ft^3)
Ethane
0.3564
22.23
Propane
0.5077
31.66
N-butane
0.5844
36.44
Iso-butane
0.5631
35.11
N-Pentane
0.6310
39.35
Iso-Pentane
0.6247
38.96
N-hexane
0.6640
41.41
2-methypentane
0.6579
41.03
3-methylpentane
0.6689
41.71
2,2-dimethylbutane
0.6540
40.78
2,3-dimethylbutane
0.6664
41.56
N-heptane
0.6882
42.92
2-methylheptane
0.6830
42.59
3-methylheptane
0.6917
43.13
2,2-dimethylpentane
0.6782
42.29
2,4-dimethylpentane
0.6773
42.24
1,1-dimethylcyclopentane
0.7592
47.34
N-octane
0.7068
44.08
Cyclopentane
0.7504
46.79
Methylcyclopentane
0.7536
46.99
Cyclohexane
0.7834
48.85
Methylcyclohexane
0.7740
48.27
Benzene
0.8844
55.15
Toluene
0.8718
54.37
Alcohol
0.7900
49.26
Ammonia
0.8900
55.50
Benzine
0.6900
43.03
Gasoline
0.7000
43.65
Kerosene
0.8000
49.89
Mineral Oil
0.9200
57.37
Petroleum Oil
0.8200
51.14
CodeCalc User's Guide
57
Shells and Heads Water
1.0
62.4
Height of Liquid Column (Operating) - Enter the distance from the bottom of this shell or head element to the surface of the liquid. The head pressure is determined by multiplying the liquid density by the height of the fluid to the point of interest. Height of Liquid Column (Hydrotest) - Enter the distance from the bottom of this shell or head element to the surface of the liquid when the vessel is being hydrotested. If this is shop hydrotest, and the vessel is laying on its side, then the height of the liquid column should be equal to the inside diameter of the vessel. In the case of a vertical hydrotest, this liquid height can be greater than the vessel diameter.
Geometry Tab (Shell/Head) Specifies parameters for shell and head geometry. Type of Shell - Enter the type of shell for this shell section: Cylindrical Elliptical Torispherical Hemispherical Head or Spherical Shell Conical Flat Head Specific parameters for the selected shell type display. Design Length of Section - Enter the design length of the section, typically the length of the vessel plus one-third the depth of the heads or, alternately, the distance between stiffening rings. For a vessel with 2 elliptical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/6. For a vessel with 2 spherical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/3. For a vessel with 2 flanged and dished heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/9. When analyzing a head, enter zero for the length. Design Length for Cylinder Volume Calculations - Enter the distance that you want CodeCalc to use for the liquid volume computation. Half Apex Angle for Conical Sections - Enter the half-apex angle for cones or conical sections. The maximum value of the half apex angle for cones under internal pressure and without toriconical transitions or discontinuity stress check is 30 degrees. The largest angle for cones under internal pressure and with toriconical sections or discontinuity stress check is 60 degrees. Typically the largest angle for cones under external pressure is 60 degrees. If you exceed these values the program will run, but with a warning. In that case the user is encouraged to use the CONICAL module for a more detailed analysis. Aspect Ratio for Elliptical Heads - Enter the aspect ratio for the elliptical head. The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Inside Crown Radius for Torispherical Heads - Enter the crown radius for torispherical heads. The crown radius for a torispherical head is referred to as the dimension "L", in the ASME VIII Div. 1 Code. This dimension is usually referred to as "DR" in many head catalogs. Even though the head catalogs list these heads as being "OD" heads, the crown radius is given on the inside diameter basis. See the illustration in the catalog and where the arrows for "DR" and "IKR" point to (the inside of the head). For more information, see Appendix 1-4 in the Code.
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CodeCalc User's Guide
Shells and Heads Inside Knuckle Radius for Torispherical Heads - Enter the knuckle radius r for torispherical heads, according to ASME Section VIII Div. 1. This dimension is usually referred to as IKR in many head catalogs. Even though the head catalogs list these heads as being OD heads, the knuckle radius is given on the inside diameter basis. See the illustration in the catalog and where the arrows for DR and IKR point to (the inside of the head). For more information, see Appendix 1-4 in the Code. Length of Straight Flange - The straight flange is the cylindrical portion of a torispherical (dished) or elliptical head. This dimension is used to compute the overall volume of the head in the new, cold, and corroded condition, as well as the weight of the head. This dimension does not affect the required thickness calculation. Attachment Factor for Flat Head - Enter the flat head attachment factor, calculated or selected from ASME Code, Section VIII, Division 1, Paragraph UG-34, Figure UG-34. Some typical attachment factors display below, however consult Paragraph UG-34 before using these values: 0.17 (b-1)
Head welded to vessel with generous radius
0.20 (b-2)
Head welded to vessel with small radius
0.20 (c)
Lap welded or brazed construction
0.13 (d)
Integral flat circular heads
0.20 (e f g)
Plate welded inside vessel (check 0.33*m)
0.33 (h)
Plate welded to end of shell
0.20 (I)
Plate welded to end of shell (check 0.33*m)
0.30 (j k)
Bolted flat heads (include bending moment). To compute the required thickness of the bolted flat heads (type j and k), use the Flange module and model it as a blind flange.
0.30 (m n o) Plate held in place by screwed ring 0.25 (p)
Bolted flat head with full face gasket
0.75 (q)
Plate screwed into small diameter vessel
0.33 (r s)
Plate held in place by beveled edge
Large Diameter for Noncircular Flat Heads - If you have a noncircular welded flat head, enter the large dimension in this field, and enter the small dimension as the component diameter above. This value is used to compute the factor Z for noncircular heads. If the head is circular, enter the diameter here. Diameter Basis - Select the type of diameter from the list. ID - Inside diameter OD - Outside diameter Torispherical heads should always be specified on the inside diameter basis. Even though the head catalogs refer to these as OD heads, inspection of the catalog nomenclature reveals that the dimensions listed are inside dimensions. Because of this, the inside dimensions from the catalog can be entered directly when the ID basis is specified. Normally, for a torispherical head the inside crown radius is equal to the vessel outside diameter. For flat heads, this value is ignored. Always enter the outside diameter of the flat head. Diameter of Shell/Head - Enter the diameter of the shell or head. For cones, enter the largest diameter of the cone. For flat heads, use the appropriate diameter per the figure UG-34 in the
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Shells and Heads ASME Code. The diameter of the head is usually taken as the inside diameter of the cylindrical shell to which it is attached. The program allows you to use either an inside diameter (ID) or an outside diameter (OD). Click to select a pipe by nominal pipe diameter and pipe schedule. Pipe Selection Minimum Thickness of Pipe or Plate - Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness, which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Some commonly used thicknesses are: 0.0625 - 1/16 " 0.1250 - 1/8 " 0.2500 - 14 " 0.3750 - 3/8 " 0.4375 - 7/16 " 0.5000 - 1/2 " 0.6250 - 5/8 " 0.7500 - 3/4 " 0.8750 - 7/8 " 1.0000 - 1 " Nominal Thickness of Pipe or Plate - (Optional) Enter the NOMINAL or AVERAGE thickness of the actual plate or pipe used to construct the vessel. This thickness is used to calculate the volume and weight of the metal ONLY if it is between 1 and 1.5 times the minimum thickness. If this value is left blank or 0, the program will use the minimum thickness to compute the weight and volume of this shell element. Corrosion Allowance - Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance that you enter. Type of Reinforcing Ring - Enter the index for the type of reinforcing ring on the cylindrical or conical section. Three options are available: None - No additional input required. Bar - Displays the Reinforcing Ring - Bar dialog box. You must enter the width and thickness of the bar. For more information, see Bar Options (on page 62). Section - Displays the Reinforcing Ring - Section dialog box. You must enter the moment of inertia, cross sectional area, and the distance from the shell to the centroid of the beam. In all cases CodeCalc includes the shell in the calculation of the moment of inertia for the stiffening ring. You can only perform this calculation for external pressure calculations. Also, the detailed analysis for the required moment of inertia and cross section area for cones is contained in the separate CONICAL program. For more information, see Section Options (on page 64). Minimum Design Metal Temperature - If this component is a carbon or low alloy steel shell or head, the program will compute its Minimum Design Metal Temperature (MDMT). The value to be entered in this field is the user-defined MDMT. This value is for reference only and will not be used by the program. If this material is not a carbon steel then enter a zero (0) in this field. If a value of zero is entered, the program will not echo this value out during runtime. Skip UG-16(b) Minimum Thickness Calculation? - Select this option to skip the UG-16(b) calculation. Section UG-16(b) states the minimum thickness for pressure retaining components as 0.0625 in. (1.6 mm). There are certain exemptions from this requirement such as in the case of heat exchanger tubes. Refer to the ASME Section VIII, Division -1, UG-16(b) for more details.
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Shells and Heads Is a Jacket Present (App. 9)? - Check this box if a jacket is present and to activate the Jacket tab. The program will analyze jackets according to Appendix-9 of the ASME Sec. VIII Div. 1. For more information, see Jacket Tab (on page 69). The following jacket types are addressed:
Is the Ring attached to both inner shell and Outer Jacket? - Specifies whether the ring is attached to both the inner shell and the outer jacket.
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Bar Options Specifies the parameters for bar reinforcement rings. Width of Reinforcing Ring - Enter the width of the reinforcing ring. For a reinforcing ring that is a simple bar, this is the dimension that is perpendicular to the surface of the shell. Thickness of Reinforcing Ring - Enter the thickness of the reinforcing ring. For a reinforcing ring that is a simple bar, this is the dimension that is parallel to the surface of the shell.
Figure 4: Thickness of Reinforcing Ring
Stiffening Ring Material Name - Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, you can select the material from the Material Database by clicking Database while the cursor is in this field. If a material is not contained in the database, you can select its specification and properties by selecting Tools > Edit > Add Materials from the Main Menu. If you type in the name, CodeCalc retrieves the first material it finds with a matching name. EXAMPLES FOR MATERIAL SPECIFICATION: SA-516 70, SA-285 C Some typical material names (standard ASME material name): Plates & Bolting SA-516 55 SA-516 60 SA-516 65 SA-516 70 SA-193 B7 SA-182-F1 SA-182 F1 SA-182 F11 SA-182 F12 SA-182 F22 SA-105 SA-36 SA-106 B Stainless Steel SA-240 304 SA-240 304L SA-240 316 SA-240 316L SA-193 B8
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Shells and Heads Aluminum SB-209 SB-234 Titanium SB-265 1 Nickel SB-409 SB-424 If you used old CodeCalc material names with previous versions, you may refer to the CodeCalc User's Guide Appendix 22.6 for name comparisons with ASME Code Names. Size of Fillet Weld Leg Connecting Ring to Shell - Enter the dimension of the weld leg, which connects the stiffening ring to the shell section. This value is used in the weld shear flow calculations if a simple bar stiffener has been selected as the type of reinforcing ring. Ring Type to Satisfy Inertia and Area Requirements -Entering a structural ring type here causes CodeCalc to search the structural database for a suitable member that meest the inertia requirements for the ring. The valid types of structural shapes are: EQUAL ANGLE - Equal Leg Angles UNEQUAL ANGLE - Unequal Angle DBL LARGE ANGLE - Double Angles Large Legs back to back DBL SMALL ANGLE - Double Angles Small Legs back to back CHANNEL - Channel Sections I-BEAM - Wide Flange Sections WT SECTION - Wide Flange Sections (T type ) MT SECTION - Miscellaneous Tee ST SECTION - Structural Tee MC SECTION - Miscellaneous Channel Weld Ring Attachment Style - Enter the style of the weld that attaches the stiffening ring to the shell section. Per UG-29 of the Code, there are three styles: INTERMITTENT CONTINUOUS BOTH This input in conjunction with the shell thickness and corrosion allowance will allow for the computation of the maximum spacing between weld segments. Location of Ring - There are two possibilities for the location of the stiffening ring. INTERNAL - Attached to the inside of the shell. EXTERNAL - On the outer surface of the shell.
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Shells and Heads Is the ring rolled the hard way? - If you have selected an angle type ring to satisfy the inertia requirements above, this box is meaningful; otherwise it is ignored. When this option is used, CodeCalc computes the distance from the shell surface to the ring centroid based on information in the AISC Steel handbook.
Figure 5: Hard Way or Easy Way
Section Options Specifies the parameters for reinforcing rings for sections. Stiffening Ring Material Name - Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, you can select the material from the Material Database by clicking Database while the cursor is in this field. If a material is not contained in the database, you can select its specification and properties by selecting Tools > Edit > Add Materials from the Main Menu. If you type in the name, CodeCalc retrieves the first material it finds with a matching name. EXAMPLES FOR MATERIAL SPECIFICATION: SA-516 70, SA-285 C Some typical material names (standard ASME material name): Plates & Bolting SA-516 55 SA-516 60 SA-516 65 SA-516 70 SA-193 B7 SA-182-F1 SA-182 F1 SA-182 F11 SA-182 F12 SA-182 F22 SA-105 SA-36 SA-106 B Stainless Steel SA-240 304
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Shells and Heads SA-240 304L SA-240 316 SA-240 316L SA-193 B8 Aluminum SB-209 SB-234 Titanium SB-265 1 Nickel SB-409 SB-424 If you used old CodeCalc material names with previous versions, you may refer to the CodeCalc User's Guide Appendix 22.6 for name comparisons with ASME Code Names. Size of Fillet Weld Connecting Ring to Shell - Enter the dimension of the weld leg, which connects the stiffening ring to the shell section. This value is used in the weld shear flow calculations if a simple bar stiffener has been selected as the type of reinforcing ring. Moment of Inertia of Reinforcing Ring - Enter the moment of inertia for the beam section, which is being used as a reinforcing ring, in the direction parallel to the surface of the shell. Cross Sectional Area of Reinforcing Ring - Enter the cross sectional area for the beam section which is being used as a reinforcing ring. Distance from Ring Centroid to shell Surface - Enter the distance from the surface of the shell to the centroid of the reinforcing ring. This distance should be measured normal to the shell surface. Ring Type to Satisfy Inertial and Area Requirements - Entering a structural ring type here causes CodeCalc to search the structural database for a suitable member that meest the inertia requirements for the ring. The valid types of structural shapes are: EQUAL ANGLE - Equal Leg Angles UNEQUAL ANGLE - Unequal Angle DBL LARGE ANGLE - Double Angles Large Legs back to back DBL SMALL ANGLE - Double Angles Small Legs back to back CHANNEL - Channel Sections I-BEAM - Wide Flange Sections WT SECTION - Wide Flange Sections (T type ) MT SECTION - Miscellaneous Tee ST SECTION - Structural Tee MC SECTION - Miscellaneous Channel Weld Ring Attachment Style - Enter the style of the weld that attaches the stiffening ring to the shell section. Per UG-29 of the Code, there are three styles: INTERMITTENT CONTINUOUS BOTH This input in conjunction with the shell thickness and corrosion allowance will allow for the computation of the maximum spacing between weld segments. Location of Ring - There are two possibilities for the location of the stiffening ring. INTERNAL - Attached to the inside of the shell.
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Shells and Heads EXTERNAL - On the outer surface of the shell. Is the ring angle rolled the hard way? - If you have selected an angle type ring to satisfy the inertia requirements above, this box is meaningful; otherwise it is ignored. When this option is used, CodeCalc computes the distance from the shell surface to the ring centroid based on information in the AISC Steel handbook.
Figure 6: Hard Way or Easy Way
Optional Data Tab Specifies parameters for overriding the values generated by the software. User MAWP - (Maximum Allowable Working Pressure) Enter the design MAWP. If this value is provided, the calculated MAWP based on the input nominal thickness will be overridden and used to compute the de-rated MAWP in Section 5 and Section 6 analysis. The de-rating of the vessel element will be shown automatically when the results indicate failure for continuing operation. However, when the results meet the passing criteria, a remaining life of the equipment using thickness approach methodology will be presented. Longitudinal Minimum Required Thickness, TMINL - Enter the TMINL thickness. If either the TMINL or the TMINC value is greater than 0.0, then the calculated TMIN value based on the ASME Section VIII will be overridden. Circumerential Minimum Required Thickness, TMINC - Enter the TMINC thickness. If either the TMINL or the TMINC value is greater than 0.0, then the calculated TMIN value based on the ASME Section VIII will be overridden. Longitudinal Membrane Stress, SigmaML - Enter the SigmaML stress value. If either the TMINL or the TMINC value is greater than 0.0, then the calculated SigmaML value based on the ASME Section VIII will be overridden. Circumferential Membrane Stress, SigmaMC - Enter the SigmaMC stress value. If either the TMINL or the TMINC value is greater than 0.0, then the calculated SigmaML value based on the ASME Section VIII will be overridden. RSFA (Remaining Strength Factor Allowable) - This value is defined as RSF = LDC / LUC Where: LDC = Limit or plastic collapse load of the damaged component LUC = Limit of plastic collapse load of the undamaged component. The default value as currently set in the API Recommended Practice 579 is 0.9
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Supplemental Loads Specifies the parameters for supplemental loads.
Figure 7: Direction of Supplemental Loads
Axial Force, F - Enter the net-section axial force from supplemental loads excluding the pressure trust for the Sustained Case and Expansion Case, if any. Shear Force, V - Enter the net-section shear force from supplemental loads for the Sustained Case and Expansion Case, if any. Bending Moment, Mx - Enter the component of the net-section bending moment from supplemental loads in the X direction for the Sustained Case and Expansion Case, if any. Bending Moment, My - Enter the component of the net-section bending moment from supplemental loads in the Y direction for the Sustained Case and Expansion Case, if any. Torsional Moment, Mt - Enter the net-section torsion moment from supplemental loads in the Z direction for the Sustained Case and Expansion Case, if any. Joint Efficiency, Circumferential Seams - Enter the joint efficiency in the circumferential direction.
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Shells and Heads Shell Orientation - Select the orientation of installed vessel. This input will be used to get horizontal input data for the thickness calculation due to supplemental load. If you select Horizontal, more options display.
Figure 8: Shell Orientation Directions
Depth of Head - Enter the head depth of the horizontal vessel. Saddle Contact Angle - Enter the contact angle of the saddle with the shell. Distance from Saddle to Vessel Tangent - Enter the length from the tangent line of the horizontal vessel to the centerline of a saddle support. Maximum Saddle Reaction Force - Enter the saddle reaction force resulting from the weight of the vessel and vessel content. Flaw Location Along Vessel - Select from the option the nearest point where the flaw located.
Compute Remaining Life Specifies that the software performs the remaining life calculation when the assessments have met the passing criteria.
Section 4 and 5 Corrosion Rate per year - Enter the corrosion rate per year in both directions, circumferential and longitudinal directions. These corrosion rates are also required for the localized pitting analyzed using Section 5.
Section 6 PPR Mode Settings Pit Size - Activates the pit grow in Increasing In Pit Size mode. This mode will simulate the increase of the pit size, diameter and depth. This check box will enable the Diameter and Depth Pit Propagation Rate (PPR) boxes. Region Size - Activates the pit grow in Increasing In Pit Region Size mode. This mode will simulate the increase of the LTA size. This check box will enable the C dim and S dim fields.
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Shells and Heads Density - Activate the pit grow in Increasing In Pit Density mode. This mode will simulate the increase the pit density by decreasing the pit spacing. This check box will enable the Couple Spacing field.
Pit Propagation Rate per year Diameter - Enter the diameter pit propagation rate. Depth - Enter the depth pit propagation rate. S dim - Enter the S dimension (longitudinal direction) pit propagation rate. C dim - Enter the C dimension (circumferential) pit propagation rate. Couple Spacing - Enter the pit couple spacing pit propagation rate.
RLife Computation Approach - Specifies how you want to compute the remaining life. You can select Thickness or MAWP. Print Intermediate RLife Results - Prints the table of the intermediate results of the RLife iterations. These intermediate results are printed in every 100 iterations.
Jacket Tab Specifies parameters for jacket and closure bars. Select Jacket (fig. 9-2) - Select the jacket type that you are analyzing from the list. If you cannot decide the type that best suits your model, then select Type 2. If this is not appropriate, then the software gives you a warning message. The software calculates the required thickness of the jacket, closure bar, and the internal chamber (cylindrical / conical shell, or head covered by the jacket). The code gives weld sizes, which must be adhered to because they ensure full integrity of the jacket attachment to the vessel. ASME VIII Div 1 Appendix 9 sets out 5 basic jacket configurations. For more information, see Figure 9-2 in the Code.
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In a type 3 jacket arrangement, there is no closure bar, however the welding is critical, and the notes set out in the Code must be adhered to. Typically, the jacket is attached by means of a closure bar as shown here:
Figure 9: Inner Vessel with Jacket and Closure Bar
The closure bar can be a simple rectangular section ring as displayed above, or it can be more elaborate as displayed in Appendix 9 of the Code.
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Shells and Heads Verify the inner shell/head for external pressure using (any) vacuum plus the Jacket Pressure and consider the Design Length of the Jacket section L. Select Closure (fig. 9-5) - Select the closure bar type most resembling your design:
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Figure - Closure Bar Jacket Types
Jacket long. Jt. Eff. - Enter the jacket and jacket head welded joint efficiencies. This is obtained from table UW-12 in ASME Section VIII Division 1. In the case of a type 1 weld (Welded from both sides, or with removable backing strip), the joint efficiencies are as follows: 1.00 - Full radiography 0.85 - Spot radiography 0.70 - No radiography Select Jacket Head - Select the jacket head type: Elliptical Torispherical Hemispherical Corrosion Allowances - Enter the following corrosion allowances. The program will perform all the calculations in the corroded condition. 1
Inner shell corrosion allowance outside
cso
2
Jacket corrosion allowance inside
cji
3
Jacket head corrosion allowance inside
ci
The input for the inner shell corrosion allowance inside is available on the Geometry tab of the main input screen. For more information, see Shells and Heads Geometry Tab (see "Geometry Tab (Shell/Head)" on page 58). Design Temperature - Enter the design temperature of the jacket. Jacket Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Shells and Heads Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Pressure Pj - Enter the pressure in the jacket space. This is the pressure shown in the figure L. Inside Diameter Dj - Enter the inside diameter of the jacket as shown in figure L. Thickness tj - Enter the thickness of the jacket as shown in figure L. Half Apex Angle - Enter the half apex angle for the (c), (b-2), (k) and (l) closure bar types as shown in the following figure.
Figure 10: Half Apex Angles
Length for Volume Calculation - Enter the total length (Ltot) of the jacket, which can be used for computing the volume and weight of the jacket. Design Length (dist. bet. rings) - Enter the design length of the jacket used to check the inner shell. The internal pressure in the jacket acts as an external pressure on the inner shell. The inner shell is checked for external pressure using this design length plus the jacket pressure and any shell vacuum pressure specified. The design length is typically the length of the jacket, but if there is a stiffening ring located in between the jacket and the shell, then this length is smaller. The length is between two support points. Jacket Head Thickness - Enter the new thickness of the jacket head. Aspect Ratio - The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head, the aspect ratio is 2.0. Inside Crown - Enter the crown radius in the case of a torispherical jacket head.
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Shells and Heads Knuckle Radius - Enter the knuckle radius in the case of a torispherical jacket head.
Closure Bar Dimensions Closure Bar Material Name - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Thickness - Enter the thickness of the closure bar. Total Corr. Allow - Enter the corrosion allowance of the closure bar. if the closure is subject to corrosion both outside and inside, then enter the combined corrosion allowance.
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API 579 (FFS) Tab Specifies damage and flaw description options for shells and heads.
Figure 11: Zones for Thickness Averaging
Damage Description Flaw Type - Select the flaw type from the list. General Metal Loss – Assess the flaw using API 579 Section 4 analysis Local Metal Loss – Assess the flaw using API 579 Section 5 analysis. Pitting Corrosion – Assess the flaw using API 579 Section 6 analysis. You must review the assessment applicability and limitation whenever the assessment changes.
Flaw Description Flaw Location - Select the location of the flaw: Inside – Located on the inner diameter surface. Outside – Located on the outer diameter surface. Inside and Outside – Located on both inner and outer diameter surfaces in Section 6 (Multiple Layer Analysis).
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Shells and Heads Section 4 and 5 Near Axisymmetric Discontinuity - Select the available option if the flaw is near the axisymmetric structural discontinuity such as seam weld, stiffening ring, or knuckle area of the head. Cylinder - Near stiffening ring or skirt weld seam or cone weld seam or circumferential weld seam. Cylinder provides the following options: None User specified Near a stiffening ring Skirt weld seam Cone weld seam Formed Head - Beyond the spherical portion or circumferential weld seam. Formed head provides the following options: None User specified Beyond the spherical portion Cone - Near the large end or the small end junction. Cone provides the following options: None User specified Near the large end or the small end junction
Figure 12: Zones for Thickness Averaging - Axisymmetric Discontinuity
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Shells and Heads Distance of 1st Data Point from Discontinuity - Enter the nearest distance of the first data point along the longitudinal or meridional direction to the axisymmetric structural discontinuity. This value will be used to determine the location of each thickness profile data in reference to the axisymmetric structural discontinuity location. Refer to a dimension in the above sketch. Distance of Head Tangent from Skirt Weld Seam - Enter the distance of head tangent from skirt weld seam. Refer to b dimension in Figure E. For more information, see Near Axisymmetric Structural Discontinuity on the API 579 (FFS) Tab (on page 78). User Specified, Lv - Enter the user specified Zone Thickness Averaging length, Lv. The value that you enter will override the calculated value described in the API579. If you leave this box blank, the software interprets that as a zero value. Proximity to Cone End - Select the cone end nearest the discontinuity. Cone Diameter At That End - Specifies the cone diameter at the selected end.
Section 6 Widespread Pitting - Specifies that pitting occurs over a significant region of the component. Localized Pitting - Specifies that pitting occurs over a localized region of the component LTA in Region of Widespread Pitting - Specifies that a region of LTA is located in an area of widespread pitting. Pitting Confined in LTA - Specifies that pitting is confined within the LTA.
LTA Dimensions Enter the s and c dimensions. These dimensions are required for the following pitting damage types: Localized pitting Region of LTA located in an area of widespread pitting Pitting confined within a region of localized metal loss
Figure 13: LTA Dimensions in Pitting Damage
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Shells and Heads Long/Merid. Dir. (s) - Enter the total number of measurement points along the Longitudinal/Meridional Direction for Profile Thickness measurement method.
Figure 14: Longitudinal and Meridional Directions
Circ. Dir. (c) - Enter the total number of measurement points along the Circumferential Direction for Profile Thickness measurement method.
Data Measurement Tab Uniform Metal Loss - Enter the metal loss prior to the assessment. LMSD - Enter the shortest distance from the edge of the local metal loss region under investigation to the nearest major structural discontinuity such as weld seam and stiffening ring. This parameter is used to check the limiting flaw size in Section 5 analysis. Measurement Type - Select the measurement type to use. You can select: Point - Specifies that the point thickness measurement method is used. Profile - Specifies that the profile thickness measurement method is used. Groove - Specifies that the groove measurement method is used. For more information, see Groove Options (on page 83). Pitting - Specifies that the software is analyzing pitting flaws. Profile Type - Select the profile thickness measurement data type, CTP (Critical Thickness Profile) or Grid type (raw data). This value sets the data entry table accordingly.
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Shells and Heads Data Size Circumfer. Dir. - Enter the total number of measurement points along the Circumferential Direction for Profile Thickness measurement method. Long./Merid. Dir. - Enter the total number of measurement points along the Longitudinal/Meridional Direction for Profile Thickness measurement method.
Figure 15: Longitudinal and Meridional Directions
Grid Size Circumfer. Dir - Enter the grid size of the thickness profile in the circumferential direction. Long./Merid. Dir - Enter the grid size in the thickness profile in the longitudinal or meridional direction. Measurement Data - Displays a dialog box that specifies the parameters for measurement data. For more information, see the following: Point Measurement Data Dialog Box (on page 83) Enter CTPs Dialog Box (on page 83) Groove Options (on page 83) Enter Pitting Information Dialog Box (on page 84)
Optional Data Overriding Values (MAWP, TMINL, TMINC, RFSA, etc.) - Select this check box to specify that the software uses the MAWP, TMINL, TMINC, SigmaML, SigmaMC, and RSFA override values. Supplemental Loads - Specifies that the software uses the supplemental loads values.
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Shells and Heads Compute Remaining Life - Specifies that the software performs the remaining life calculation when the assessments have met the passing criteria. Specifies parameters for profile measurements. Circumferential Planes - Type the distance between the planes. Longitudinal Planes - Type the distance between the planes.
Point Measurement Data Dialog Box Specifies parameters for point measurements. Thk - Enter the measured thickness for each point.
Enter CTPs Dialog Box Specifies parameters for critical thickness profiles. Longitudinal Plane CTP - Enter the critical thickness profile in the longitudinal direction. Circumferential Plane CTP - Enter the critical thickness profile in the circumferential direction.
Groove Options Specifies the parameters for measuring grooves.
Figure 16: Groove Measurement Dimensions
Radius, gr - Enter the groove radius. Length, gl - Enter the groove length.
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Shells and Heads Depth, gd - Enter the groove depth. Width, gw - Enter the groove width. Orientation, Beta - Enter the groove orientation (Beta) in degrees. Critical Exposure Temperature - Enter the lowest metal temperature derived from either the operating or atmospheric conditions.
Enter Pitting Information Dialog Box Specifies parameters for pitting.
Figure 17: Pitting Dimensions
P_k - Enter the pit-couple spacing in pit-couple k. Theta_k - Enter the pit-couple orientation in degree. d_ik - Enter the diameter of the pit i in pit-couple k. w_ik - Enter the depth of the pit i in pit-couple k. d_jk - Enter the diameter of the pit j in pit-couple k. w_jk - Enter the depth of the pit j in pit-couple k.
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Results Thickness Due to Internal Pressure The appropriate formula from ASME Section VIII is referenced, and the formula and substitutions are shown. The diameter or crown radius is adjusted to take into account the corrosion allowance. If your shell design includes hydrostatic head components, the additional pressure due to the height of the liquid column and the operating liquid density will be included with the basic design pressure. The hydrostatic head will be subtracted in order to properly determine the MAWP for the vessel part that is being analyzed. Remember, when pressures are being read from the pressure gauge, the gauge is usually at the high point of the vessel. The pressure registered by the gauge would be different if were at the bottom of the liquid filled vessel. For elliptical heads, the K factor is (2 + Ar * Ar) / 6, per App. 1-4 (c). For torispherical heads, the factor M is (1/4) * (3 + SQRT (L / R)), where "L" (the crown radius) and "R" (the knuckle radius) were entered by the user. CodeCalc does not replace the given thickness with this calculated minimum. If you are choosing the thickness for a component, compare the values shown under "Summary of Internal Pressure Results" (required vs. actual) and adjust the actual thickness up or down accordingly.
Maximum Allowable Working Pressure at Given Thickness This value is calculated as described above, using the given thickness minus corrosion allowance and the operating allowable stress. The hydrostatic head component is subtracted from this value. The pressure gauge is assumed to be at the top of the vessel.
Maximum Allowable Working Pressure, New & Cold This value is calculated as described above, using the uncorroded thickness and the ambient allowable stress.
Actual Stress at Given Pressure and Thickness Note that the joint efficiency is included in this value, so this can be considered as the stress at the welded joint rather than in the base metal.
Summary of Internal Pressure Results Either of two conditions can indicate a problem in your design. First, if the required thickness plus corrosion allowance is greater than the given thickness, then you must increase the given thickness. Second, if the MAWP is less than the design pressure, then you must either decrease the design pressure or increase the given thickness to achieve an acceptable design. The hydrotest pressure is calculated as the maximum allowable working pressure times 1.5 or 1.3 (depending on the material database selection) times the ratio of the allowable stress at ambient temperature to the allowable stress at design temperature. The hydrotest pressure may not be appropriate for the entire vessel for three reasons. First, some other component may have a lower maximum allowable working pressure, which may govern the hydrotest pressure. Second, you may choose to base hydrotest pressure on design pressure rather than maximum allowable working pressure. Third, if the vessel is tested in the vertical position you may have to adjust the hydrotest pressure for the head of water in the vessel. For the UG99-C hydrotest, the liquid head is subtracted from the basic result.
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Shells and Heads Minimum Metal Temperatures For carbon steels, these temperatures represent the minimum design metal temperature for the given thickness and, in the second case, the given pressure. The first temperature is interpolated directly from chart UCS-66. The second temperature is reduced if the actual stress is lower than the allowable stress, using figure UCS-66.1. The program also checks for materials, which qualify for the -20 minimum design temperature per UG-20 and prints it in the output. See the input notes above to enter normalized or non-normalized materials.
Weight & Volume Results, No Corrosion Allowance CodeCalc computes the volume and weight of the shell component. Additionally, the inside volume for a 2.00 inch straight flange is computed and used in the computation of the total volume for the head and the flange. The dimensions used in the volume and weight calculations are non-corroded dimensions.
Results for Max. Allowable External Pressure For the given diameter, thickness, and length, the maximum allowable external pressure is computed per UG--28.
Results for Required Thickness for External Pressure Required thickness results are calculated iteratively using the rules of UG-28. Items such as the length and outside diameter are held constant, and the software calculates the required thickness based on the entered value for external pressure.
Summary of External Pressure Results Summary listing displaying external pressure results for the user-entered thickness and the calculated required thickness.
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SECTION 5
Nozzles
Home tab: Components > Add New Nozzle Calculates the required reinforcement under internal pressure and performs failure path calculations for nozzles in shells and heads, using the ASME Code, Section VIII, Division 1 rules. You can also orientate the nozzle in directions such as hillside, lateral, and radial.
In This Section
Purpose, Scope, and Technical Basis (Nozzles)........................... 87 Nozzle Tab ..................................................................................... 88 Geometry Tab ................................................................................ 91 Miscellaneous Tab ......................................................................... 95 Shell/Head Tab .............................................................................. 101 Results ........................................................................................... 105
Purpose, Scope, and Technical Basis (Nozzles) Nozzles calculates the required wall thickness and area of reinforcement for a nozzle in a pressure vessel shell or head, and compares this area to the area available in the shell, nozzle and optional reinforcing pad. The software also calculates the strength of failure paths for a nozzle. Nozzles is based on the ASME Code, Section VIII, Division 1, Paragraph UG-37 through UG-45, 2007 Edition. The calculation procedure is based on Figure UG-37.1. The software calculates the required thickness (for reinforcement conditions) based on inside or outside diameter for the following vessel components: Component
Paragraph
Limitations Per UW-37
Cylinder
UG-27 (c) (1)
None
Elliptical Head
UG-32 (d) (1)
Nozzle concentric within 0.8D
Torispherical Head
UG-32 (e) (1)
Nozzle in spherical portion
Spherical Head or Shell UG-27 (d) (3)
None
Conical
None
UG-27 (g)
The software evaluates nozzles at any reasonable angle from the perpendicular, allowing evaluation of off angle, hillside, or tangential nozzles.
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87
Nozzles Nozzles account for the internal corrosion allowance. You enter actual thickness and corrosion allowance, and the software adjusts thicknesses and diameters when making calculations for the corroded condition. Nozzles also performs UCS-66 MDMT calculations for nozzles.
Figure 18: Nozzle Dimensions
Nozzle Tab Specifies design parameters for nozzles. Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. Design Internal Pressure - Enter the internal design pressure. This is a non-zero positive value and is usually obtained from the design drawings or vessel design specification. Required information such as the required thickness tr and trn are determined from the design internal pressure. Design Temperature for Internal Pressure - The software automatically updates material properties for built-in materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Design External Pressure - Enter the external design pressure. CodeCalc will compute the required thickness of the given geometry for the external pressure entered. If you are designing for a full vacuum, you would enter a value of 14.7 psig (or rounded off to 15 psig) or 1.0133 bars. CodeCalc will compute the required thickness for both external and internal pressure. It will the choose the greatest required thickness, tr, and proceed with the calculations. If external pressure governs, the program will automatically reduce the required area of reinforcement by 50 percent. Shell Design Length for External Pressure - Enter the design length of the section, typically the length of the vessel plus one third the depth of the heads or, alternately, the distance between stiffening rings. For a vessel with 2 elliptical heads and no intermediate stiffeners, the design length is the tangent to tangent length plus the shell diameter / 6. For a vessel with 2 spherical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/3. For a vessel with 2 flanged and dished heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/9.
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CodeCalc User's Guide
Nozzles When analyzing a conical head enter the length along the axis of the cone, from the small end to the point where the nozzle center line penetrates the cone. If any other head types are being analyzed, enter a 0 here and you must enter the required thickness of the component in the required field. Print Intermediate Calculations For External Pressure - Indicates that CodeCalc will print out the parameters used for external pressure design. Design Temperature for External Pressure - The CodeCalc software will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Maximum Allowable Pressure for New Cold - Some design specifications require that nozzle reinforcement calculations are performed for the maximum allowable pressure, new and cold condition, MAPnc. MAPnc for the nozzles is the minimum of the MAPs determined from analyzing the vessel elements using the Shell/Head part of the software. The software will then check to see if the nozzle is reinforced adequately using the user entered MAPnc. When the area of replacement calculations are made for this case, cold allowable stresses are used and the corrosion allowance is set to 0. Designing nozzles for this case helps the vessel to comply with UG99 or appropriate (hydrotest) requirements. Check your design requirements to see if this case is required by your client. Nozzle Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Include Hydrostatic Head Components - If your nozzle design needs to account for hydrostatic liquid head, select this box. CodeCalc adds the hydrostatic pressure head to the internal design pressure for the required thickness calculation. Operating Liquid Density - Enter the density of the operating fluid. This value is multiplied by the height of the liquid column in order to compute the static head pressure. You can enter a number of specific gravity units and CodeCalc converts the number to the current set of units. To do this, enter a number followed by the letters sg. Typical specific gravities and densities are shown below in lbs/ft^3.
Convert the densities to your units. Name
Specific Gravity
Density (lb/ft^3)
Ethane
0.3564
22.23
Propane
0.5077
31.66
N-butane
0.5844
36.44
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89
Nozzles Iso-butane
0.5631
35.11
N-Pentane
0.6310
39.35
Iso-Pentane
0.6247
38.96
N-hexane
0.6640
41.41
2-methypentane
0.6579
41.03
3-methylpentane
0.6689
41.71
2,2-dimethylbutane
0.6540
40.78
2,3-dimethylbutane
0.6664
41.56
N-heptane
0.6882
42.92
2-methylheptane
0.6830
42.59
3-methylheptane
0.6917
43.13
2,2-dimethylpentane
0.6782
42.29
2,4-dimethylpentane
0.6773
42.24
1,1-dimethylcyclopentane
0.7592
47.34
N-octane
0.7068
44.08
Cyclopentane
0.7504
46.79
Methylcyclopentane
0.7536
46.99
Cyclohexane
0.7834
48.85
Methylcyclohexane
0.7740
48.27
Benzene
0.8844
55.15
Toluene
0.8718
54.37
Alcohol
0.7900
49.26
Ammonia
0.8900
55.50
Benzine
0.6900
43.03
Gasoline
0.7000
43.65
Kerosene
0.8000
49.89
Mineral Oil
0.9200
57.37
Petroleum Oil
0.8200
51.14
Water
1.0
62.4
Height of Liquid Column - Enter the distance from the bottom of this shell or head element to the surface of the liquid. The head pressure is determined by multiplying the liquid density by the height of the fluid to the point of interest.
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Nozzles
Geometry Tab Specifies nozzle geometry parameters. Nozzle Diameter Basis - Specifies the diameter basis. ID - Inside diameter OD - Outside diameter Nozzle Size Thickness Basis - Select the value from the list. Actual - Actual diameter and thickness. The software uses the actual diameter entered in the Nominal Diameter of Nozzle box and the actual thickness entered in the Actual Thickness of Nozzle (0 if Nominal) box. Nominal - Nominal diameter and thickness. The software looks up the actual diameter based on the nominal diameter entered in the Nominal Diameter of Nozzle box, and looks up the nominal thickness based on the schedule entered in the Nominal Schedule of Nozzle field. Minimum - Minimum diameter and thickness. The software looks up the actual diameter based on the nominal diameter entered in the Nominal Diameter of Nozzle box, and looks up the nominal thickness based on the schedule entered in the Nominal Schedule of Nozzle field. It will then multiply the nominal thickness by a factor of 0.875. Nominal Diameter of Nozzle - Enter the diameter of the nozzle. If you specify nominal or minimum for the nozzle size and thickness basis, then you must enter the nominal diameter of the nozzle in this field. Valid nominal diameters are:
0.1250 - 1/8 " 0.2500 - 1/4 " 0.3750 - 3/8 " 0.5000 - 1/2 " 0.7500 - 3/4 " 1.0000 - 1 " 1.2500 - 1.25 " 1.5000 - 1.5 " 2.0000 - 2 " 2.5000 - 2.5 " 3.0000 - 3 " 3.5000 - 3.5 " 0.1250 - 1/8 " 0.2500 - 1/4 " 0.3750 - 3/8 " 0.5000 - 1/2 " 0.7500 - 3/4 " 1.0000 - 1 "
1.2500 - 1.25 " 1.5000 - 1.5 " 2.0000 - 2 " 2.5000 - 2.5 " 3.0000 - 3 " 3.5000 - 3.5 " 4.0000 - 4 " 5.0000 - 5 " 6.0000 - 6 " 8.0000 - 8 " 10.000 - 10 " 12.000 - 12 " 14.000 - 14 " 16.000 - 16 " 18.000 - 18 " 20.000 - 20 " 24.000 - 24 " 30.000 - 30 "
to select a pipe by nominal pip diameter and pipe schedule. Click Pipe Selection Actual Thickness of Nozzle (0 if Nominal) - Enter the minimum actual thickness of the nozzle wall. Enter a value in this field only if you selected Actual in the Nozzle Size Thickness Basis field. Otherwise enter a schedule in the Nominal Schedule of Nozzle field.
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91
Nozzles Nominal Schedule of Nozzle - Select the schedule for the nozzle wall. Select a value for this field only if you selected Nominal or Minimum In the Nozzle Size Thickness Basis field. Required Thickness of Nozzle (Computed if 0.0) - The software normally calculates the required thickness of the nozzle but under the following circumstances you must enter the required thickness (Trn): When your job specification requires that no area be included from the shell. Enter the actual thickness minus the corrosion allowance. When the nozzle is non-circular. Nozzle Corrosion Allowance - The software adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Some Common Corrosion Allowances are : 0.0625 - 1/16 " 0.1250 - 1/8 " 0.2500 - 1/4 " Joint Efficiency of Shell Seam Through Which Nozzle Passes - The seam efficiency is used in the area available calculations to reduce the area available in the shell. For shell and nozzle wall thickness calculations, the seam efficiency is always 1.0. Joint Efficiency of Nozzle Neck - This value is used to compute the required thickness for a seamless nozzle. A seamless nozzle will have a value of 1.0. The nozzle required thickness values are used in the CODE equations for A2 "area available in the nozzle". CodeCalc will use this value in determining the MDMT of the Nozzle. Insert or Abutting Nozzle - The nozzle type and depth of groove welds are used to determine the required weld thicknesses and failure paths for the nozzle. If the nozzle is welded to the outside of the vessel wall, it is abutting the vessel wall. If the hole in the vessel is bigger than the nozzle OD and the nozzle is welded into the hole, it is inserted. Figure UW-16.1 in the code shows typical insert and abutting nozzles. Nozzle Outside Projection - Enter the projection of the nozzle from the vessel wall to the nozzle flange. If there is no flange, enter the distance to the first elbow, valve, or anything that can be considered a stiffener. This value is used in two ways: This length is used to compute the nozzle weight. If the pressure entered is negative (vacuum) condition, the software uses this value for the length in the external pressure required thickness calculations.
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CodeCalc User's Guide
Nozzles Weld Leg Size for Fillet between Nozzle Shell or Pad - Enter the size of one leg of the fillet weld between the nozzle and the pad or shell. The following figure shows different welds.
Figure 19: Nozzle Weld Locations
Depth of Groove Weld between Nozzle and Vessel - Enter the total depth of the groove weld. Most groove welds between the nozzle and the vessel are full penetration welds. The depth of the weld is the same as the depth of the component (that is, the thickness of the nozzle). If the nozzle is attached with a partial penetration weld, or just a fillet weld, enter the depth of the partial penetration or a zero, respectively, in this field. Nozzle Inside Projection - Enter the projection of the nozzle into the vessel. The software uses the least of the inside projection and the thickness limit with no pad to calculate the area available in the inward nozzle. Therefore, you may safely enter a large number such as six or twelve inches if the nozzle continues into the vessel a long distance. Weld Leg for Fillet Between Nozzle Inside of Shell - Enter the size of one leg of the fillet weld between the inward nozzle and the inside shell. Is there a reinforcing pad? - If there is a reinforcing pad on the nozzle, or if you want to specify the geometry for a reinforcing pad, select this option. CodeCalc designs and recommends a reinforcing pad if one is needed, but the analysis of areas is based only on what you have entered. If CodeCalc recommends a pad or a larger pad than the one you enter, you must go back into input and enter a pad of the correct size in order for the final configuration to be reflected in the final analysis. Pad Outside Diameter Along Vessel Surface - Enter the outside diameter of the pad. The diameter of the pad is entered as the length along the vessel shell (not the projected diameter around the nozzle), although these two values will be equal when the nozzle is at 90 degrees. A hillside or Y- angle nozzle makes a non-circular hole in the vessel. As a result, a reinforcing pad with same width around the nozzle will have different diameter in the longitudinal and the circumferential planes. For this type of nozzle, enter the smaller diameter, which is Pad OD = 2 * pad width + Nozzle OD Pad Thickness - Enter the thickness of the pad. If any external corrosion is to be considered, subtract the corrosion allowance from the new pad thickness. Some commonly used thicknesses are: 0.0625 - 1/16 " 0.1250 - 1/8 " 0.2500 - 1/4 "
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93
Nozzles
0.3750 - 3/8 " 0.4375 - 7/16 " 0.5000 - 1/2 " 0.6250 - 5/8 " 0.7500 - 3/4 " 0.8750 - 7/8 " 1.0000 - 1 "
Pad Weld Leg Size at Outside Diameter - Enter the size of one leg of the fillet weld between the pad OD and the shell. Note that if any part of this weld falls outside the diameter limit, the weld will not be included in the available area. The following figure shows different welds. Depth of Groove Weld Between Pad and Nozzle Neck - Enter the total depth of the groove weld between the pad and the nozzle neck. If the nozzle is attached with a partial penetration weld, or just a fillet weld, enter the depth of the partial penetration or a zero, respectively, in this field. Pad Material Name - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
For split pads, reduce area A5 by 75% per UG-37(h) - Indicates that the area will be reduced by 75%.
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CodeCalc User's Guide
Nozzles
Miscellaneous Tab Specifies miscellaneous nozzle parameters. Is the Nozzle Outside the 80% Diameter Limit? - If the nozzle is outside of the spherical portion of the elliptical or torispherical head, select this option. The software uses the standard internal pressure equation from UG-27 instead of the equation from UG-37. When a nozzle is within the 80% diameter limit, the required thickness of the head is equal to that of a seamless sphere of radius K1*D (D is the shell diameter and K1 is given by Table UG-37). Do you want to modify the reinforcement limit? - You can enter any physical limitation that exists on the thickness or the diameter available for reinforcement. An example of a thickness limitation is a studding pad or nozzle stub that does not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. An example of a diameter limitation is two nozzles close together, or a vessel seam for which you did not want to take an available area reduction. Physical Maximum for Nozzle Diameter Limit - Enter the maximum diameter for material contributing to nozzle reinforcement. An example of a diameter limitation would be two nozzles close together, or a vessel seam for which you did not want to take an available area reduction. A hillside or Y- angle nozzle makes a non-circular hole in the vessel. So, the diameter limit in the longitudinal and the circumferential planes is different. For this type of nozzle, enter the smaller diameter limit. Physical Maximum for Nozzle Thickness Limit - Enter the maximum thickness for material contributing to nozzle reinforcement. An example of a thickness limitation would be a studding pad or nozzle stub which would not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. Neglect Areas - Frequently in the analysis of openings in heads or shells, you do not want to account for the area in the shell and sometimes in the nozzle. If this is what your design specification calls out for then enter one of the following in this field. A1 - No area available in the shell or head A2 - No area available in the nozzle wall A1 A2 - No area available in the shell or nozzle wall If the input has A2 there will be no area contributed by the nozzle wall for either the pad case (A2WP) or the case when there is no pad (A2NP). ASME Large Nozzle Calc. Option - Select the large nozzle calculation option from the list. Do you want to rate the attached flange? - Specifies that the software asks you the class and grade of the attached flange. The software will used these two items along with the temperature to rate the flange using the tables in ANSI B16.5. Class for Attached B16.5 Flange - The attached flange often limits the MAWP of a pressure vessel. If your geometry has an attached flange, select the class from the list. The following flange classes are available: CL 150 - Class 150 CL 300 - Class 300 CL 400 - Class 400 CL 600 - Class 600 CL 900 - Class 900 CL 1500 - Class 1500
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Nozzles
CL 2500 - Class 2500
Grade of Attached B16.5 Flange - Select the nozzle flange material grade (group). Please note that there are certain advisories on the use of certain material grades. Please review those cautionary notes in the ANSI B16.5 code. The following flange grades are available:
Table 1A List of Material Specifications (ASME B16.5-2003) Material Nominal Designation Group 1.1
1.2
1.3
C-Si C-Mn-Si C-Mn-Si-V 3½ Ni C-Mn-Si C-Mn-Si-V 2½Ni 3½Ni
Forgings A 105 A 350 Gr. LF2 A 350 Gr. LF 6 Cl.1 A 350 Gr. LF3
A 350 Gr. LF 6 Cl.2
C-Si C-Mn-Si C-½Mo 2 ½Ni 3 ½Ni C-Si C-Mn-Si
A 350 Gr. LF1 Cl. 1
1.5
C-1/2Mo
A 182 Gr. F1
½C-½Mo Ni-½Cr-½Mo ¾Ni-¾Cr-1Mo
A 216 Gr. WCB
A 216 Gr. WCC A 352 Gr. LCC A 352 Gr. LC2 A 352 Gr. LC3
A 352 Gr. LCB A 217 Gr. WC1 A 352 Gr. LC1
1.4
1.7
Castings
A 182 Gr. F2
Plates A 515 Gr. 70 A 516 Gr. 70 A 537 Cl. 1
A 203 Gr. B A 203 Gr. E A 515 Gr. 65 A 516 Gr. 65 A 203 Gr. A A 203 Gr. D A 515 Gr. 60 A 516 Gr. 60 A 204 Gr. A A 204 Gr. B
A 217 Gr. WC4 A 217 Gr. WC5
1.9
1¼Cr-½Mo 1¼Cr-½Mo-Si
A 182 Gr. F11 Cl.2
1.10
2¼Cr-1Mo
A 182 Gr. F22 Cl.3
1.11
Cr-½Mo
1.13
5Cr-½Mo
1.14
9Cr-1Mo
A 182 Gr. F9
A 217 Gr. C12
1.15
9Cr-1Mo-V
A 182 Gr. F91
A 217 Gr. C12A
A 387 Gr. 91 Cl.2
1.17
1Cr-½Mo 5Cr-½Mo
A 182 Gr. F12 Cl.2 A 182 Gr. F5
2.1
18Cr-8Ni
A 182 Gr. F304
A 351 Gr. CF3
A 240 Gr. 304
96
A 217 Gr. WC6 A 217 Gr. WC9
A 387 Gr. 11 Cl.2 A 387 Gr. 22 Cl.2 A 204 Gr. C
A 182 Gr. F5a
A 217 Gr. C5
CodeCalc User's Guide
Nozzles Material Nominal Designation Group
2.2
16Cr-12Ni-2Mo 18Cr-13Ni-3Mo 19Cr-10Ni-3Mo
Forgings
Castings
Plates
A 182 Gr. F304H
A 351 Gr. CF8
A 240 Gr. 304H
A 351 Gr. CF3M A 351 Gr. CF8M A 351 Gr. CG8M
A 240 Gr. 316 A 240 Gr. 316H A 240 Gr. 317
A 182 Gr. F316 A 182 Gr. F316H A 182 Gr. F317
2.3
18Cr-8Ni 16Cr-12Ni-2Mo
A 182 Gr. F304L A 182 Gr. F316L
A 240 Gr. 304L A 240 Gr. 316L
2.4
18Cr-10Ni-Ti
A 182 Gr. F321 A 182 Gr. F321H
A 240 Gr. 321 A 240 Gr. 321H
2.5
18Cr-10Ni-Cb
A 182 Gr. F347 A 182 Gr. F347H A 182 Gr. F348 A 182 Gr. F348H
A 240 Gr. 347 A 240 Gr. 347H A 240 Gr. 348 A 240 Gr. 348H
2.6
23Cr-12Ni
2.7
25Cr-20Ni
2.8
A 240 Gr. 309H A 182 Gr. F310
20Cr-18Ni-6Mo A 182 Gr. F44 22Cr-5Ni-3Mo-N A 182 Gr. F51 25Cr-7Ni-4Mo-N A 182 Gr. F53 24Cr-10Ni-4Mo-V 25Cr-5Ni-2Mo-3Cu 25Cr-7Ni-3.5Mo-W-Cb 25Cr-7Ni-3.5Mo-N-Cu-W
A 240 Gr. 310H A 351 Gr. CK3McuN A 351 Gr. CE8MN A 351 Gr. CD4Mcu A 351 Gr. CD3MWCuN
A 240 Gr. S31254 A 240 Gr. S31803 A 240 Gr. S32750 A 240 Gr. S32760
2.9
23Cr-12Ni 25Cr-20Ni
2.10
25Cr-12Ni
A 351 Gr. CH8 A 351 Gr. CH20
2.11
18Cr-10Ni-Cb
A 351 Gr. CF8C
2.12
25Cr-20Ni
A 351 Gr. CK20
3.1
35Ni-35Fe-10Cr-Cb
B 462 Gr. N08020
B 463 Gr. N08020
3.2
99.0Ni
B 160 Gr. N02200
B 162 Gr. N02200
3.3
99.0Ni-Low C
B 160 Gr. N02201
B 162 Gr. N02201
3.4
67Ni-30Cu 67Ni-30Cu-S
B 564 Gr. N04400 B 164 Gr. N04405
B 127 Gr. N04400
3.5
72Ni-15Cr-8Fe
B 564 Gr. N06600
B 168 Gr. N06600
3.6
33Ni-42Fe-21Cr
B 564 Gr. N08800
B 409 Gr. N08800
3.7
65Ni-28Mo-2Fe B 462 Gr. N10665 64Ni-29.5Mo-2Cr-2Fe-M B 462 Gr. N10675 n-W
B 333 Gr. N10665 B 333 Gr. N10675
CodeCalc User's Guide
A 240 Gr. 309S A 240 Gr. 310S
97
Nozzles Material Nominal Designation Group
3.8
54Ni-16Mo-15Cr 60Ni-22Cr-9Mo-3.5Cb 62Ni-28Mo-5Fe 70Ni-16Mo-7Cr-5Fe 61Ni-16Mo-16Cr 42Ni-21.5Cr-3Mo-2.3Cu 55Ni-21Cr-13.5Mo 55Ni-23Cr-16Mo-1.6Cu
Forgings
Castings
B 564 Gr. N10276 B 564 Gr. N06625 B 335 Gr. N10001 B 573 Gr. N10003 B 574 Gr. N06455 B 564 Gr. N08825 B 462 Gr. N06022 B 462 Gr. N06200
Plates B 575 Gr. N10276 B 443 Gr. N06625 B 333 Gr. N10001 B 434 Gr. N10003 B 575 Gr. N06455 B 424 Gr. N08825 B 575 Gr. N06022 B 575 Gr. N06200
3.9
47Ni-22Cr-9Mo-I8Fe
B 572 Gr. N06002
B 435 Gr. N06002
3.10
25Ni-46Fe-21Cr-5Mo
B 672 Gr. N08700
B 599 Gr. N08700
3.11
44Fe-25Ni-21Cr-Mo
B 649 Gr. N08904
B 625 Gr. N08904
26Ni-43Fe-22Cr-5Mo B 621 Gr. N08320 47Ni-22Cr-20Fe-7Mo B 581 Gr. N06985 46Fe-24Ni-21Cr-6Mo-Cu B 462 Gr. N08367 -N
B 620 Gr. N08320 B 582 Gr. N06985 B 688 Gr. N08367
3.12
A 351 Gr. CN3MN
3.13
49Ni-25Cr-18Fe-6Mo Ni-Fe-Cr-Mo-Cu-Low C
B 581 Gr. N06975 B 462 Gr. N08031
B 582 Gr. N06975 B 625 Gr. N08031
3.14
47Ni-22Cr-19Fe-6Mo 40Ni-29Cr-15Fe-5Mo
B 581 Gr. N06007 B 462 Gr. N06030
B 582 Gr. N06007 B 582 Gr. N06030
3.15
33Ni-42Fe-21Cr
B 564 Gr. N08810
B 409 Gr. N08810
3.16
35Ni-19Cr-1¼Si
B 511 Gr. N08330
B 536 Gr. N08330
3.17
29Ni-20.5Cr-3.5Cu-2.5M o
A 351 Gr. CN7M
Table 1A List of Material Specifications (ASME B16.5-1996) Material Nominal Designation Group 1.1
1.2
1.3
98
C-Si C-Mn-Si C-Mn-Si-V C-Mn-Si C-Mn-Si-V 21/2Ni 31/2Ni C-Si C-Mn-Si 21/2Ni 31/2Ni
Forgings
Castings
Plates
A 105 A 350 Gr. LF2 A 350 Gr. LF 6 Cl.1
A 216 Gr. WCB A 216 Gr. WCC
A 515 Gr. 70 A 516 Gr. 70 A 537 Cl. 1
A 350 Gr. LF 6 Cl.2 A 350 Gr. LF3
A 352 Gr. LCC A 352 Gr. LC2 A 352 Gr. LC3 A 352 Gr. LCB
A 203 Gr. B A 203 Gr. E A 515 Gr. 65 A 516 Gr. 65 A 203 Gr. A A 203 Gr. D
CodeCalc User's Guide
Nozzles Material Nominal Designation Group
Forgings
1.4
C-Si C-Mn-Si
A 350 Gr. LF1 Cl. 1
1.5
C-1/2Mo
A 182 Gr. F1
1.7
C-1/2Mo 1/2Cr-1/2Mo Ni-1/2Cr-1/2Mo 3/4Ni-3/4Cr-1Mo
A 182 Gr. F2
Castings
Plates A 515 Gr. 60 A 516 Gr. 60
A 217 Gr. WC1 A 352 Gr. LC1
A 204 Gr. A A 204 Gr. B A 204 Gr. C
A 217 Gr. WC4 A 217 Gr. WC5
1Cr-1/2Mo 11/4Cr-1/2Mo 11/4Cr-1/2Mo-Si
A 182 Gr. F12 Cl.2 A 182 Gr. F11 Cl.2
A 217 Gr. WC6
A 387 Gr. 11 Cl.2
1.10
21/4Cr-1Mo
A 182 Gr. F22 Cl.3
A 217 Gr. WC9
A 387 Gr. 22 Cl.2
1.13
5Cr-1/2Mo
A 182 Gr. F5 A 182 Gr. F5a
A 217 Gr. C5
1.14
9Cr-1Mo
A 182 Gr. F9
A 217 Gr. C12
1.15
9Cr-1Mo-V
A 182 Gr. F91
A 217 Gr. C12A
A 387 Gr. 91 Cl.2
2.1
18Cr-8Ni
A 182 Gr. F304 A 182 Gr. F304H
A 351 Gr. CF3 A 351 Gr. CF8
A 240 Gr. 304 A 240 Gr. 304H
16Cr-12Ni-2Mo 18Cr-13Ni-3Mo 19Cr-10Ni-3Mo
A 182 Gr. F316 A 182 Gr. F316H
A 351 Gr. CF3M A 351 Gr. CF8M A 351 Gr. CG8M
A 240 Gr. 316 A 240 Gr. 316H A 240 Gr. 317
2.3
18Cr-8Ni 16Cr-12Ni-2Mo
A 182 Gr. F304L A 182 Gr. F316L
A 240 Gr. 304L A 240 Gr. 316L
2.4
18Cr-10Ni-Ti
A 182 Gr. F321 A 182 Gr. F321H
A 240 Gr. 321 A 240 Gr. 321H
2.5
18Cr-10Ni-Cb
2.6
25Cr-12Ni 23Cr-12Ni
2.7
25Cr-20Ni 20Cr-18Ni-6Mo 22Cr-5Ni-3Mo-N 25Cr-7Ni-4Mo-N 24Cr-10Ni-4Mo-V 25Cr-5Ni-2Mo-3Cu 25Cr-7Ni-3.5Mo-W-Cb
1.9
2.2
2.8
CodeCalc User's Guide
A 182 Gr. F347 A 182 Gr. F347H A 182 Gr. F348 A 182 Gr. F348H
A 351 Gr. CF8C
A 240 Gr. 347 A 240 Gr. 347H A 240 Gr. 348 A 240 Gr. 348H
A 351 Gr. CH8 A 351 Gr. CH20
A 240 Gr. 309S A 240 Gr. 309H
A 182 Gr. F310
A 351 Gr. CK20
A 240 Gr. 310S A 240 Gr. 310H
A 182 Gr. F44 A 182 Gr. F51 A 182 Gr. F53 A 182 Gr. F55
A 351 Gr. CK3McuN A 351 Gr. CE8MN A 351 Gr. CD4Mcu A 351 Gr. CD3MWCuN
A 240 Gr. S31254 A 240 Gr. S31803 A 240 Gr. S32750 A 240 Gr. S32760
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Nozzles Material Nominal Designation Group
Forgings
Castings
Plates
25Cr-7Ni-3.5Mo-N-CuW 3.1
35Ni-35Fe-20Cr-Cb
B 462 Gr. N08020
B 463 Gr. N08020
3.2
99.0Ni
B 160 Gr. N02200
B 162 Gr. N02200
3.3
99.0Ni-Low C
B 160 Gr. N02201
B 162 Gr. N02201
3.4
67Ni-30Cu 67Ni-30Cu-S
B 564 Gr. N04400 B 164 Gr. N04405
B 127 Gr. N04400
3.5
72Ni-15Cr-8Fe
B 564 Gr. N06600
B 168 Gr. N06600
3.6
33Ni-42Fe-21Cr
B 564 Gr. N08800
B 409 Gr. N08800
3.7
65Ni-28Mo-2Fe
B 335 Gr. N10665
B 333 Gr. N10665
54Ni-16Mo-15Cr 60Ni-22Cr-9Mo-3.5Cb 62Ni-28Mo-5Fe 70Ni-16Mo-7Cr-5Fe 61Ni-16Mo-16Cr 42Ni-21.5Cr-3Mo-2.3C u
B 564 Gr. N10276 B 564 Gr. N06625 B 335 Gr. N10001 B 573 Gr. N10003 B 574 Gr. N06455 B 564 Gr. N08825
B 575 Gr. N10276 B 443 Gr. N06625 B 333 Gr. N10001 B 434 Gr. N10003 B 575 Gr. N06455 B 424 Gr. N08825
3.8
ASME Code Weld Type - Select the type of weld connecting the nozzle to the shell or head. The type of weld can optionally be entered in this field. If it is a type A, B, C, D, E, F-1, F-2, F-3, F-4, G, X-1, Y-1, OR Z-1 weld, then CodeCalc will not perform the weld strength calculations. The code exempts these calculations per paragraph UW-15 when one of the above weld classifications such as A is used. If it is a type I, J, K, L, X-2, Y-2, Z-2 weld, then CodeCalc will perform the additional weld size calculations per UW-16(d)(1). Select None if you want the software to perform the weld strength calculations regardless of the type of welded geometry. Is this a manway or access/inspection opening? - UG 45 states that if the opening is a manway or access opening, the minimum thickness requirement per UG-45 is not required. Checking this box will cause the software to bypass the UG-45 minimum nozzle neck thickness requirement. Perform Area Calculations for Small Nozzles? - Code paragraph UG-36 discusses the requirement of performing area replacement calculations when small nozzles are involved. The code states: Openings in vessels not subject to rapid fluctuations in pressure do not require reinforcement other than that inherent in the construction under the following conditions : 3.5" finished opening in a shell or head with minimum required thk. of .375 inches or less 2.375" finished opening in a shell or head greater than minimum required thk. of .375 inches If your geometry meets this criteria and this checkbox is NOT checked, then no area of reinforcement calculations will be performed on this nozzle item.
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Nozzles Is this compressed air, water, or steam service? - Select if the vessel s under compressed air, steam, or water service. This causes the software to use a value of 3/32 instead of the 1/16 inch default per UG 16(b). By default for UG45 the program uses the value of 1/16 of an inch for minimum thickness considerations. Is this welded pipe? - If the pipe is not seamless, then check this box. Note that this value is only used for documentation purposes and is not used for any computations. Do not skip iterative failure thickness calcs.? - If this box is checked then the software iteratively computes the maximum corrosion allowance and minimum wall thickness at which the failure occurs. ASME Large Nozzle Calculation Option - Select the large nozzle calculation option from the list.
Shell/Head Tab Specifies parameters for shells and heads. Shell/Head Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Type of Shell - Select the type of shell for this shell section. The thickness of an elliptical head is analyzed as an equivalent spherical head, as specified in the Code, paragraph UG-37 (a). Similarly, the thickness of the spherical portion of a torispherical head is analyzed using the same paragraph. You must enter the required thickness (below) under the following circumstances: Bolted Flat Heads - Calculate the required thickness using the FLANGE module and enter it in. Additionally, the software automatically reduces the required area of reinforcement if you specify a flat head per UG-39(b)(1). Any other geometry not covered by the program. Aspect Ratio for Elliptical Heads - Enter the aspect ratio for the elliptical head. The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Inside Crown Radius for Torispherical Heads - Enter the crown radius for torispherical heads. The crown radius for a torispherical head is referred to as the dimension "L", in the ASME VIII Div. 1 Code. This dimension is usually referred to as "DR" in many head catalogs. Even though the head catalogs list these heads as being "OD" heads, the crown radius is given on the inside diameter basis. See the illustration in the catalog and where the arrows for "DR" and "IKR" point to (the inside of the head). For more information, see Appendix 1-4 in the Code.
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Nozzles Inside Knuckle Radius for Torispherical Heads - Enter the knuckle radius r for torispherical heads, according to ASME Section VIII Div. 1. This dimension is usually referred to as IKR in many head catalogs. Even though the head catalogs list these heads as being OD heads, the knuckle radius is given on the inside diameter basis. See the illustration in the catalog and where the arrows for DR and IKR point to (the inside of the head). For more information, see Appendix 1-4 in the Code. Half Apex Angle for Conical Sections - Enter the half-apex angle for cones or conical sections. The maximum value of the half apex angle for cones under internal pressure and without toriconical transitions or discontinuity stress check is 30 degrees. The largest angle for cones under internal pressure and with toriconical sections or discontinuity stress check is 60 degrees. Typically the largest angle for cones under external pressure is 60 degrees. If you exceed these values the program will run, but with a warning. In that case the user is encouraged to use the CONICAL module for a more detailed analysis. Attachment Factor for Flat Head - Enter the flat head attachment factor, calculated or selected from ASME Code, Section VIII, Division 1, Paragraph UG-34, Figure UG-34. Some typical attachment factors display below, however consult Paragraph UG-34 before using these values: 0.17 (b-1)
Head welded to vessel with generous radius
0.20 (b-2)
Head welded to vessel with small radius
0.20 (c)
Lap welded or brazed construction
0.13 (d)
Integral flat circular heads
0.20 (e f g)
Plate welded inside vessel (check 0.33*m)
0.33 (h)
Plate welded to end of shell
0.20 (I)
Plate welded to end of shell (check 0.33*m)
0.30 (j k)
Bolted flat heads (include bending moment). To compute the required thickness of the bolted flat heads (type j and k), use the Flange module and model it as a blind flange.
0.30 (m n o) Plate held in place by screwed ring 0.25 (p)
Bolted flat head with full face gasket
0.75 (q)
Plate screwed into small diameter vessel
0.33 (r s)
Plate held in place by beveled edge
Large Diameter for Noncircular Flat Heads - If you have a noncircular welded flat head, enter the large dimension in this field, and enter the small dimension as the component diameter above. This value is used to compute the factor Z for noncircular heads. If the head is circular, enter the diameter here.
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Nozzles Is this a Lateral Nozzle (Y-angle)? - Y-angle or lateral nozzles can be specified in case of conical and cylindrical sections, by turning on this option. In this case, only the vessel-nozzle centerline angle needs to be specified. The following figure shows an example.
Figure 20: Vessel-Nozzle Angle
For users of versions prior to 6.40, the input specification for non radial and non hillside nozzles has changed. The current requirement is the angle between the centerline of the nozzle and the centerline of the vessel. Is this a Radial Nozzle? - Non-radial nozzles can be specified by entering the angle between the vessel and nozzle centerlines, and the offset from vessel centerline. This vessel-nozzle centerline angle can vary from 0 to a limiting value depending upon specific geometry. The following figure illustrates these dimensions. In this case the input for the offset dimension and vessel-nozzle centerline angle are optional, only required for the graphic and not for the analysis.
Figure 21: Radial Nozzle Angle
Hillside nozzles and some angular nozzles are subject to calculations to meet area requirements in both planes of reinforcement. In these cases CodeCalc automatically checks the area requirements in both the planes, using the corresponding lengths of the nozzle opening. For integral construction, the Code F correction factor of 0.5 will automatically be applied in the
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Nozzles hillside direction. If the connection is pad reinforced, a value of 1.0 will be used. The F factor is used to account for the fact that the longitudinal stress is one half of the hoop stress. The use of the F factor is limited to nozzles located on cylindrical and conical sections.
Figure 22: Hillside Nozzle Angle
Offset Distance from Cylinder/Head Centerline (L1) - Enter the offset between the nozzle and the center of the shell. Angle Between Nozzle and Shell Centerlines - Enter the angle between the nozzle and shell. Shell Diameter Basis - Select ID for shell sections based on the inside diameter. Select OD for shell sections based on the outside diameter. Normally, for a flanged & dished torispherical head, the inside crown or radius is equal to the vessel outside diameter. For flat heads, this value is ignored. Refer to Fig. UG-34 for equivalent diameter of the head. For example, in case of most welded heads this is the diameter over which the pressure acts. For bolted heads with narrow faced gasket this is the diameter of the gasket reaction. For cones, the program expects the diameter of the cone at the point where the nozzle intersects the shell. Diameter of Shell/Head (not crown radius) - Enter the diameter of the shell or head. Torispherical heads - Diameter of the shell to which the head is attached. Flat heads - Refer to Fig. UG-34 for equivalent diameter of the head. For example, in case of most welded heads this is the diameter over which the pressure acts. Bolted heads with narrow faced gasket - Diameter of the gasket reaction. Cones- Diameter of the cone at the point where the nozzle intersects the shell. Actual Thickness of Shell - Enter the minimum thickness of the actual plate or pipe used to build the shell, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Shell Corrosion Allowance - Enter the corrosion allowance. The software adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Enter Required Thicknesses? - The only time the required thickness must be entered is if the component being analyzed is a bolted flat head. Otherwise, the required thickness of the shell/head will be computed by the program. For hillside nozzles, as of Version 5.40, several changes have been made relating to the use of the required thickness. They are as follows: If you want to enter an offset and allow CodeCalc to compute the nozzle angle, the required thickness must be left blank. If an angle less than 90 has been entered, or computed via the entered offset values, and you would like to take credit for the Code 0.5 F-correction factor, the required thickness must be entered in and multiplied by the F factor.
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Nozzles If an angle less than 90 has been entered and you do not want to take credit for the Code 0.5 F-correction factor, the required thickness should be entered. Required Shell Thickness for Int. P - Specifies the required shell thickness for internal pressure. Required Shell Thickness for Ext. P - Specifies the required shell thickness for external pressure. Required Shell Thickness for Hydro - Specifies the required shell thickness for hydro.
Results Topics
Actual Nozzle Diameter Thickness ................................................ 105 Required Thickness of Shell and Nozzle ....................................... 105 UG-45 Minimum Nozzle Neck Thickness ...................................... 106 Required and Available Areas ....................................................... 106 Selection of Reinforcing Pad ......................................................... 106 Large Diameter Nozzle Calculations ............................................. 106 Effective Material Diameter and Thickness Limits ......................... 106 Minimum Design Metal Temperature ............................................ 107 Weld Size Calculations .................................................................. 107 Weld Strength Calculations ........................................................... 107 Failure Path Calculations ............................................................... 107 Iterative Results Per Pressure, Area, And UG-45 ......................... 107
Actual Nozzle Diameter Thickness If you specified an actual basis for nozzle diameter and thickness, the diameter and thickness shown will be the same as those which you entered. If you specified nominal, these values will be the nominal diameter and thickness found in the software pipe size tables. If you entered minimum, the software will have looked up the diameter and thickness in the pipe size tables and then multiplied the thickness by 0.875.
Required Thickness of Shell and Nozzle The software calculates the required thickness for the shell and nozzle as follows: Cylindrical (and the nozzle wall)
-
Calculated per UG-27 or as given by the user.
Hemisphere
-
Calculated per UG-27 or as given by the user.
Torispherical
-
Calculated per UG-37 or as given by the user.
Elliptical
-
Calculated per UG-37 or as given by the user.
Conical
-
Calculated per UG-37 or as given by the user.
Flat
-
Calculated per UG-37 or as given by the user.
The joint efficiency used in this calculation is always 1.0. In 1989 we submitted a request for interpretation to the ASME Code in order to show that the use of 1.0 under all circumstances
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Nozzles was justified. The reply was published in the A-90 Addenda as Interpretation VIII-1-89-171. The question and reply were as follows: Question: In reinforcement calculations, is the joint efficiency used in calculating the required thickness of the vessel wall tr and the required thickness of the wall trn 1.0 regardless of the joint efficiency determined for the vessel wall and nozzle wall from the rules in UW-12, provided the nozzle does not pass through a weld? Reply: Yes. Note also that the program takes into account the case where the nozzle passes through a weld by asking the joint efficiency of the weld, if any.
UG-45 Minimum Nozzle Neck Thickness The software uses the design rules from paragraph UG-45 for minimum nozzle neck thickness. If the thickness used by CodeCalc for your nozzle calculation is less than required by UG-45, your Code Vessel is in violation of this paragraph.
Required and Available Areas The area required is calculated per UG-37(c). For all vessel types under external pressure and for flat heads, this value is multiplied by 0.5. The required areas are calculated per Fig. UG-37.1. The software uses dl - d, (Diameter limit minus inside hole radius) in the calculations for the area available in the shell. This is because the code incorrectly assumes that dl-d is always equal to d, which is only true when the natural diameter limit is used. Because you can enter a reduced diameter limit, the software does not use the pure code equation.
Selection of Reinforcing Pad The program gives up to three possible reinforcing pad selections. Pad thickness based on the given pad diameter. Pad diameter based on the given pad thickness. Thickness based on the thinner of the shell and nozzle walls, calculating a required diameter. If this exceeds the diameter limit, the software selects a thickness based on a pad at the diameter limit. All thickness results are rounded up to the nearest sixteenth, while all diameter results are rounded up to the nearest eighth of an inch.
Large Diameter Nozzle Calculations For large diameter nozzles, the rules of Appendix 1-7 require that two-thirds of the reinforcement be within 0.75 of the natural diameter limit for the nozzle. If the calculated value of the percent within this limit is greater than 66%, the nozzle is adequately reinforced for the large diameter rules. For a large nozzle geometry to meet Code requirements both sets of area calculations must meet their respective area requirements.
Effective Material Diameter and Thickness Limits The MAWP for reinforcement is an estimate, typically accurate to within 1 or 2 psi. Enter the given MAWP as the design pressure to check its accuracy. The MAP for the flange is based on ANSI B16.5 tables for the given grade and class of flange.
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Nozzles
Minimum Design Metal Temperature The minimum design metal temperature is computed for the nozzle. The software considers UG-20(f), UCS-66 and UCS-66.1 when performing these calculations.
Weld Size Calculations Nozzle weld thicknesses are based on Figure UW-16.1. The outward nozzle weld is compared to the cover weld required by the Code. Note that the minimum dimension of a weld is 0.7 times its leg dimension. Note also that for cover welds the maximum weld the Code requires is 0.25 inches. The pad weld requirement is typically at least one half of the element thickness. In addition to the cover welds, the total groove weld plus cover weld for inserted nozzles must be at least 1.25 times the minimum element thickness.
Weld Strength Calculations The strength of connection elements is their cross sectional area times the allowable unit stress for the element. The last two terms in the equations shown give the stress factor and basic allowable stress for the element in the direction considered.
Failure Path Calculations The failure paths differ based on whether there is a reinforcing pad, whether the nozzle is inserted or abutting, and whether there is an inward projection. Note that the strength of each path must exceed either the W value or the W#-# associated with that path. Note also that UW-15(b) indicates that no strength calculations for nozzle attachment welds are required for figure UW-16.1, sketches (a), (b), (c), (d), (e), (f-1), (f-2), (f-3), (f-4), (g), (x-1), (y-1), and (z-1). But, for types I, J, K, L, X-2, Y-2, Z-2 weld, CodeCalc will perform the additional weld size calculations per UW-16(d)(1).
Iterative Results Per Pressure, Area, And UG-45 Assuming the same corrosion allowance for the shell and nozzle, the maximum (failure) corrosion allowance, the minimum (discard) nozzle thickness and the minimum (failure) shell thickness are computed. You can project the nozzle service lifetime based on the rate of corrosion and the above results.
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Nozzles
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SECTION 6
Conical Sections Home tab: Components > Add New Conical Section Performs internal and external pressure design of conical sections and stiffening rings using the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1 rules, 2010 Edition, paragraphs UG-32, UG-33, and Appendix 1, Sections 1-5, and 1-7 This module calculates required thickness and maximum allowable working pressure (MAWP) for the cone under both internal and external pressure. Also calculated are the required thickness of the attached cylinders under either internal or external pressure and the required thickness of a transition knuckle. The required area of reinforcement and actual reinforcement available are calculated for both internal and external pressures. Reinforcement is limited to the area available in the shell sections plus simple stiffening rings. Corrosion allowance is fully considered. Enter actual thickness and corrosion allowance, and the software adjusts thicknesses and diameters when making calculations for the corroded condition.
Figure 23: Conical Dimensions
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Conical Sections In This Section
Cone Design Tab (Conical Sections) ............................................ 110 Cone Geometry Tab ...................................................................... 112 Small Cylinder and Larger Cylinder Tabs ...................................... 113 Results ........................................................................................... 115
Cone Design Tab (Conical Sections) Item Number - Enter an ID number for the item. This can be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Design Internal Pressure - You can analyze both internal and external pressure at the same time because the two cases are analyzed and reported separately. Enter zero for internal pressure if you only want to analyze the external pressure case. Design Internal Temperature - Enter the temperature associated with the internal design pressure. The software automatically updates materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. This value is used by the input echo to help insure that the correct design data was entered. This value is not used by the analysis portion of the software. Design External Pressure - Enter the design pressure for external pressure analysis. This should be a positive value, such as 14.7 psig. If you enter a zero in this field, the software does not determine the required thickness due to external pressure but will determine the External MAWP. For a skirt, you should not enter a value other than zero because there cannot be an external pressure on a skirt. External Pressure definitions are the same for PD:5500, ASME and EN-13445. Examples of External Pressure: 0 - No External Pressure 15 psig (0.1034 MPa) - Full Vacuum 0.3 psig - Partial Vacuum Take Cone as Lines of Support for External Pressure? - Select to take the intersections of the cone and the two cylinders as lines of support for external pressure, provided that the moment of inertia and area of reinforcement requirements of ASME Appendix 1-8 are satisfied. Alternately, you can calculate external pressure using an equivalent design length which includes the cone and both the large and small cylinders. For details see Section VIII, Division 1, Paragraph UG-28 and Figure UG-28.1 (A-90 Addenda and following.) Normally it is preferable to take the cone as lines of support, because the equivalent length of the large cylinder/ cone/small cylinder combination may easily result in low allowable external pressures. However, the moment of inertia is very easy to be less than the required for knuckle-to-cylinder junction — because the shell/knuckle/cone is usually so close to the resulting neutral axis. The moment of inertia with the knuckle is calculated, following the procedure of code example L-3.3. Design External Temperature - Enter the temperature associated with the external design pressure. The software automatically updates materials properties for external pressure calculations when you change the design temperature. The design external pressure at this temperature is a completely different design case than the internal pressure case. Therefore, this temperature may be different than the temperature for internal pressure.
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Conical Sections Many external pressure charts have both lower and upper limits on temperature. If your design temperature is below the lower limit, use the lower limit. If your temperature is above the upper limit the component may not be designed for vacuum conditions. Cone Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Cone Long. Joint Efficiency - Enter the efficiency of the welded joint for shell sections with welded seams. This is the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. 1.00 - Full Radiography 0.85 - Spot Xray 0.70 - No Radiography Cone Circ. Joint Efficiency - Enter the efficiency of the welded joint for shell section with welded circumferential seams. This is the efficiency of the circumferential seam at the cone to cylinder junction. Cone Corrosion Allowance - Enter the corrosion allowance. The software adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4"
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Conical Sections
Cone Geometry Tab Cone Diameter Basis - Select ID for shell sections based on inside diameter. Select OD for shell sections based on outside diameter. This diameter basis is also used for the cylinder at the small end of the cone and the cylinder at the large end of the cone. Cone Diameter at Small End - Enter the diameter of the cone at the small end. This diameter is also used for the cylinder at the small end of the cone. This should not be the diameter at the point where a knuckle or flare intersects the conical section, but at the point where the knuckle or flare intersects the cylindrical section. The software calculates the other diameter. Cone Diameter at Large End - Enter the diameter of the cone at the large end. This diameter is also used for the cylinder at the large end of the cone. This should not be the diameter at the point where a knuckle or flare intersects the conical section, but at the point where the knuckle or flare intersects the cylindrical section. The software calculates the other diameter. Cone Half Apex Angle - For internal pressure calculations the half apex angle should not be greater than 30 degrees, though the program will give results for up to 60 degrees. For external pressure calculations it must not be greater than 60 degrees. If you enter a zero for the angle, the software calculates an angle based on the cone diameters and length. Cone Axial Length - Enter the length of the cone along the axis of the vessel. The software calculates the effective length of the cone for internal and external pressure calculations. Cone Actual Thickness - Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. Some commonly used thicknesses are: 0.0625 - 1/16 " 0.1250 - 1/8 " 0.2500 - 1/4 " 0.3750 - 3/8 " 0.4375 - 7/16 " 0.5000 - 1/2 " 0.6250 - 5/8 " 0.7500 - 3/4 " 0.8750 - 7/8 " 1.0000 - 1 " Are there axial forces on the cone? - If there are axial forces on the cone, check this field. Examples of axial forces include weight loads, from external attachments, and thermal loads. The axial force due to internal or external pressure is already taken into account by the software. In general, loads causing compression are significant for the external pressure case, while loads causing tension are significant for the internal pressure case. Total Axial Force on Large End for Internal Pressure - Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The software calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a positive (tensile) axial force adds to the tension due to internal pressure, while a negative (compressive) axial force subtracts from the tension due to internal pressure.
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Conical Sections Total Axial Force on Large End for External Pressure - Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The software calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a negative (compressive) axial force adds to the compression due to external pressure, while a positive (tensile) axial force subtracts from the compression due to external pressure. Total Axial Force on Small End for Internal Pressure - Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The software calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a positive (tensile) axial force adds to the tension due to internal pressure, while a negative (compressive) axial force subtracts from the tension due to internal pressure. Total Axial Force on Small End for External Pressure - Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The software calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a negative (compressive) axial force adds to the compression due to external pressure, while a positive (tensile) axial force subtracts from the compression due to external pressure.
Small Cylinder and Larger Cylinder Tabs Cylinder Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Cylinder Joint Efficiency - Enter the efficiency of the welded joint for shell sections with welded seams. This is the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. 1.00 - Full Radiography 0.85 - Spot Xray 0.70 - No Radiography Cylinder Actual Thickness - Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. Some commonly used thicknesses are: 0.0625 - 1/16 " 0.1250 - 1/8 " 0.2500 - 1/4 "
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Conical Sections 0.3750 - 3/8 " 0.4375 - 7/16 " 0.5000 - 1/2 " 0.6250 - 5/8 " 0.7500 - 3/4 " 0.8750 - 7/8 " 1.0000 - 1 " Cylinder Corrosion Allowance - Enter the corrosion allowance. The software adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Cylinder Axial Length - Enter the length of the cylinder along the axis of the vessel. This value is not used in internal pressure calculations, but is required for external pressure calculations. Reinforcement/Knuckle Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Reinforcing Ring - Select the type of reinforcing ring. None - No reinforcement on this end and no knuckle. Bar - Reinforcing bar on this end (width and thickness). Section - Reinforcing beam section on this end (moment of inertia, area, and depth of beam). Knuckle - Toroidal knuckle on this end (radius and thickness) . Knuckle and Bar Ring - Toroidal knuckle and a reinforcing bar on this end. Knuckle and Section Ring - Toroidal knuckle and a reinforcing beam section on this end. Location of Reinforcing Ring - Enter the location of the reinforcing bar: SHELL - welded to the shell (cylinder). CONE - welded to the cone Radial Width of Reinforcing Ring - Enter the width of the reinforcing bar. You can also think of this as the projection of the bar out from the vessel OD. For example, a donut shaped plate 10 inches by 1 inch has a radial width of 10. Axial Thickness of Reinforcing Ring - Enter the thickness of the reinforcing bar. For example, a donut shaped plate 10 inches by 1 inch has an axial thickness of 1.
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Conical Sections Moment of Inertia of Reinforcing Ring - Enter the moment of inertia of the beam section (I, T, and so on) used to reinforce the cone/cylinder junction. This can usually be found in the Manual of Steel Construction for common beam sections. Cross Sectional Area of Reinforcing Ring - Enter the cross sectional area of the beam section (I, T, and so on) used to reinforce the cone/cylinder junction. This can usually be found in the Manual of Steel Construction for common beam sections. Distance to Centroid of Reinforcing Ring - Enter the distance from the Shell or Cone Outside surface to the centroid of the beam section (I, T, and so on) used to reinforce the cone/cylinder junction. This can usually be found in the Manual of Steel Construction for common beam sections. Knuckle Bend Radius - Enter the bend radius of the toroidal knuckle at the large end. The Code requires this radius to be no less than 6% of the outside diameter of the head, or less than three times the knuckle thickness (UG-31, (h)). Knuckle Thickness - Enter the minimum thickness after forming of the toroidal knuckle at the selected end.
Results Topics
Internal Pressure Results .............................................................. 115 External Pressure Results ............................................................. 115 Reinforcement Calculations Under Internal Pressure ................... 116 Reinforcement Calculations Under External Pressure .................. 116
Internal Pressure Results The first section of results shows the required thicknesses and Maximum Allowable Working Pressures for the cone and for the upper and lower cylinders under internal pressure. Note that this section is shown even when the internal design pressure is zero: the required thicknesses will be zero, but the Maximum Allowable Working Pressures will be meaningful. The software summarizes these internal pressure results, adding the corrosion allowances as necessary.
External Pressure Results The External Pressure module calculates materials properties and required thicknesses under external pressure. Because the software uses Young's modulus values in both the internal and external reinforcement calculation, this module is called even when the external design pressure is zero. However, in this case the required thickness and Maximum Allowable Working Pressure calculations for external pressure are skipped. The required thickness under external pressure is calculated using the interactive method outlined in Paragraph UG-33 of the ASME Code. The effective length for toriconical sections is adjusted to include a fraction of the knuckle in the design length.
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Conical Sections
Reinforcement Calculations Under Internal Pressure The software calculates the required reinforcement for cone/cylinder junctions at both the large and the small ends. This calculation is performed whenever the internal pressure is greater than zero, and the reinforcing material is defined. If a knuckle is specified instead of a reinforcing ring, the knuckle calculation will be performed and the required area calculation will not. When a knuckle calculation is performed, the software calculates both the required thickness and the maximum allowable working pressure for the toroidal portion of the knuckle, using the rules in Appendix 1-4(d). When there is no knuckle, the software calculates the required area of reinforcement at the intersection of the cylinder and the two cones. Cones are required to have reinforcement at the large and small ends under internal pressure (Appendix 1-5) because of the tendency of the cone/cylinder junction to buckle under the radial load developed in the cone. The Code calculates the maximum angle below which buckling will not occur as a function of the design pressure and allowable stress. This ratio is used because it is a pretty good indication of the diameter thickness ratio for the cylinder, and takes into account the strength of the material. This approach has the odd effect that when you increase the allowable stress you decrease the allowable cone angle. However, you will normally find that for a given thickness this effect is offset by the increase of area available in the cone for reinforcement. Given that reinforcement is required, the area required is a function of the pressure and the square of the radius. Area available in the shell within one decay length may be included in the area available for stiffening. CodeCalc will set the area required in the reinforcing ring to zero if either the allowed apex angle is higher than the actual apex angle or the area available in the shell is greater than the area required.
Reinforcement Calculations Under External Pressure The software calculates the required reinforcement and moment of inertia for the cone/cylinder junctions at both the large and the small ends. This calculation is performed whenever the external pressure is greater than zero, the cone is taken as a line of support and the reinforcing material is defined. If a knuckle is specified instead of a reinforcing ring, the knuckle calculation will be performed and the area of reinforcement calculation will not. If the user specifies that the cone/cylinder junctions are not to be taken as a line of support, then the area of reinforcement and moment of inertia calculations will not be performed. Cones are required to have reinforcement at the large and small ends under external pressure (Appendix 1-7) because of the tendency to buckle under axial external loads. At both the large and small ends there are requirements for the area of reinforcement and moment of inertia of the reinforcement. The area of reinforcement is based on considerations similar to those described for internal pressure. The required moment of inertia of the reinforcement is a function of the strain in the ring at the cone/shell junction, which is in turn calculated using the Code materials chart from the stress in the ring. See the comments on stiffening rings in the external pressure section for further insight. The maximum apex angle is taken from Tables 1-8.1 in Appendix 1 of the ASME Code. The software calculates the ratio P/SE. Note that this angle applies only to the large end of the cone - the small end always requires at least a little reinforcement. The area required in the reinforcing ring will be set to zero if either the cone angle is less than the maximum angle (large end only), or the area of reinforcement available in the shell is greater than the area required.
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SECTION 7
Floating Heads Home tab: Components > Add New Floating Head Calculates the required thickness of spherically dished covers (bolted heads) according to the ASME Code, Section VIII, Division 1 analysis rules found in Appendix 1, Paragraph 1-6. A more detailed analysis of bolted dished heads is included, based on Soehren's analysis, The Design of Floating Heads for Heat-Exchangers, ASME 57-A-7-47. The more detailed analysis may be used for the design of floating heads, as specifically mentioned in the ASME Code, Paragraph 1-6 (h). The software calculates required thickness for the dished part of the head under both internal and external pressure. Also calculated are the required thickness of the flange and the backing ring. Three types of heads, as defined in the code and shown below, are included. Soehren's analysis applies only to the most common type of head, type d.
Figure 24: Floating Head Types
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Floating Heads In This Section
Head Tab ....................................................................................... 118 Flange/Bolts Tab ............................................................................ 120 Gasket Tab .................................................................................... 122 Miscellaneous Tab ......................................................................... 128 Results ........................................................................................... 132
Head Tab Item Number - Enter the floating head ID number. It is recommended that the floating head numbers start at 1 and increase sequentially, but you may also enter some other meaningful number. This field is required, since the software uses this field to determine if a floating head has been defined. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Type of Floating Head (ASME Appl. 1-6) - Enter the type of floating head or spherically dished cover, which you are analyzing. The following types are available and correspond to Figure 1-6 of ASME Section VIII, Division 1, Appendix 1. b - solid thick head, spherically dished. c - thin dashed head, continuous across flange face. d - spherical cap welded to flange ID. This is the most common type of head used for heat exchanger floating heads.
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Floating Heads Floating head types are shown in the following illustration:
Figure 25: Floating Head Types
Tube Side (Internal) Design Pressure - Enter the internal pressure, which is the pressure on the concave side of the head and the tube side pressure for heat exchanger floating heads. Normally you may enter both the shell side and the tube side pressures and evaluate the entire head in a single analysis. However, when analyzing a type d head, the interaction between shell side and tube side pressure may result in a lower thickness than if each pressure is entered separately. Consequently, it is recommended that you run the software twice, first with the internal and then with the external pressures set to zero (0). Shell Side (External) Design Pressure - Enter the external pressure, which is the pressure on the convex side of the head and the shell side pressure for heat exchanger floating heads. Normally, you may enter both the shell side and the tube side pressures and evaluate the entire head in a single analysis. However, when analyzing a type d head, the interaction between shell side and tube side pressure may result in a lower thickness than if each pressure is entered separately. Consequently, it is recommended that you run the software twice, first with the internal pressure and then the external pressure set to zero (0). Design Temperature - Enter the design temperature for the flange. This value will be used to look up the allowable stresses for the material at design temperature. Head Material - Specify the material name as it appears in the material specification of the appropriate code.
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Floating Heads 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Inside Crown Radius of Head - Enter the inside crown radius of the head. This value may be any dimension greater than the inside radius of the flange. However, values roughly equal to the flange ID are more typical. Actual Thickness of Head - Enter the minimum thickness of the actual plate used to build the floating head or spherical cap, or the minimum thickness measured for an existing floating head or spherical cap. Tube Side (Internal) Corrosion Allowance - Enter the corrosion allowance on the concave side of the head. The shell side and tube side corrosion allowances are fully implemented in this version of FLOHEAD. Thicknesses and diameters are adjusted by the software for the evaluation of allowable pressure. They are also added to the required thicknesses. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Shell Side (External) Corrosion Allowance - Enter the corrosion allowance on the convex side of the head. The shellside and tubeside corrosion allowances are fully implemented in this version of FLOHEAD. Thicknesses and diameters are adjusted by the software for the evaluation of allowable pressure. They are also added to the required thicknesses.
Flange/Bolts Tab Flange Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
CodeCalc User's Guide
Floating Heads Outside Diameter of Flange - Enter the outer diameter of the flange. This value is referred to as A in the ASME code. Inside Diameter of Flange - Enter the inner diameter of the flange. For integral type flanges, this value will also be the inner pipe diameter. This value is referred to as B in the ASME code. The corrosion allowance will be used to adjust this value (two times the corrosion allowance will be added to the un-corroded ID defined by the user). Actual Thickness of Flange - Enter the minimum thickness of the actual plate used to build the floating head or spherical cap, or the minimum thickness measured for an existing floating head or spherical cap. Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Diameter of Bolt Circle - Enter the diameter of the bolt circle of the flange. This is dimension C in the ASME Code.
Figure 26: Flange Diagram
Thread Series - The following bolt thread series tables are available: TEMA Bolt Table UNC Bolt Table User-specified root area of a single bolt TEMA Metric Bolt Table
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Floating Heads
British, BS 3643 Metric Bolt Table
Irrespective of the table used, the values are converted back to user selected units. TEMA threads are National Coarse series below 1-inch and 8 pitch thread series for 1-inch and above bolt nominal diameter. The UNC threads available are the standard threads. Nominal Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the software range from 0.5 to 4.0 inches. This value is used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field. Also, enter the root area of one bolt in the Root Area cell. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this field. This option is used only if bolt root area is greater than 0.0. Number of Bolts - Enter the number of bolts to be used in the flange analysis. The number of bolts is almost always a multiple of four. Select Bolt Size - This is used mainly for the metric thread series. Selecting a value from this field will populate the Nominal Bolt Diameter field with the corresponding value.
Gasket Tab Full Face Gasket Option - ASME Sec. VIII Div. 1 does not cover the design of flanges for which the gasket extends beyond the bolt circle diameter. A typically used method for the design of these types of flanges is from the Taylor Forge Flange Design Bulletin. This method is implemented in the program. Gaskets for full face flanges are usually of soft materials such as rubber or an elastomer, so that the bolt stresses do not go too high during gasket seating. The program adjusts the flange analysis and the design formula to account for the full face gasket. There are three options available:
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Floating Heads
Program Selects - Instructs the software to automatically make the determination if this is a full face gasket flange depending upon the input. If the gasket ID and OD matches the flange ID and OD dimensions, respectively (except for a blind flange) then it is determined to be a full face flange.
Full Face Gasket - Indicates to the software that this is a full face gasket flange. Use this option when the gasket ID or OD does not match the flange ID/OD dimensions, but the gasket extends beyond the bolt circle diameter.
Not a Full Face - Indicates to the software that this is not a full face gasket flange. Flange Face Outer Diameter - Enter the outer diameter of the flange face. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point but uses the maximum in design when selecting the bolt circle. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Flange Face Inner Diameter - Enter the inner diameter of the flange face. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket.
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Floating Heads
Self energizing types (O rings, elastomer, other gasket types considered as self-sealing)
Facing Column
Gasket Factor m
Gasket Material
Seating Stress y, psi (MPa)
Gasket Inner Diameter - Enter the inner diameter of the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. Gasket Outer Diameter - Enter the outer diameter of the gasket. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Factor m - The values of m and y shown in the following table are listed in ASME Section VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y, please contact your gasket manufacturer.
0.00
0
II
Below 75A Shore Durometer
0.50
0
II
75A Shore Durometer or higher
1.00
200 (1.4)
II
1/8 inch thick
2.00
1600 (11)
II
1/16 inch thick
2.75
3700 (26)
II
1/32 inch thick
3.50
6500 (45)
II
Elastomer with cotton fabric insertion
1.25
400 (2.8)
II
3 ply
2.25
2200 (15)
II
2 ply
2.50
2900 (20)
II
1 ply
2.75
3700 (26)
II
Vegetable Fiber
1.75
1100 (7.6)
II
Carbon Steel
2.50
10000 (69)
II
Stainless Steel, Monel, and nickel-base alloys
3.00
10000 (69)
II
Soft aluminum
2.50
2900 (20)
II
Soft copper or brass
2.75
3700 (26)
II
Iron or soft steel
3.00
4500 (31)
II
Monel or 4-6% Chrome
3.25
5500 (38)
II
Stainless - steels and nickel-base alloys
3.50
6500 (45)
II
2.75
3700 (26)
II
Elastomers without fabric or high percent of mineral fiber
Mineral fiber with suitable binder for operating conditions
Elastomer with mineral fiber fabric insertion (with or without wire reinforcment)
Spiral-wound metal, mineral fiber filled
Corrugated metal, mineral fiber inserted or Corrugated metal, jacketed, mineral fiber filled
Corrugated metal, not filled Soft aluminum
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Facing Column
Gasket Factor m
Gasket Material
Seating Stress y, psi (MPa)
Floating Heads
Soft copper or brass
3.00
4500 (31)
II
Iron or soft steel
3.25
5500 (38)
II
Monel or 4-6% Chrome
3.50
6500 (45)
II
Stainless steel
3.75
7600 (52)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel
3.50
8000 (55)
II
4-6% chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
3.75
9000 (62)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel or 4-6% Chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
4.25
10100 (70)
II
Soft aluminum
4.00
8800 (61)
I
Soft copper or brass
4.75
13000 (90)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steels and nickel-base alloys
6.50
26000 (180)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steel
6.50
26000 (180)
I
Flat metal, jacketed, mineral fiber filled
Grooved metal
Solid flat metal
Ring Joint
Gasket Design Seating Stress y - Enter the gasket design seating stress Y.
Flange Face Facing Sketch - Using Table 2-5.2 of the ASME Code, select the facing sketch number according to the following correlations: FACING SKETCH
DESCRIPTION
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
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Floating Heads 1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Facing Column
Gasket Factor m
Gasket Material
Seating Stress y, psi (MPa)
Column for Gasket Seating (I, II) - Enter the gasket column for gasket seating. Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. For sketch 9, however, this is not a nubbin width. Instead, it is the contact width of the metallic ring. Length - Enter the length of the partition gasket. Width - Enter the width of the partition gasket. Gasket Factor m - The values of m and y shown in the following table are listed in ASME Section VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y, please contact your gasket manufacturer.
0.00
0
II
Below 75A Shore Durometer
0.50
0
II
75A Shore Durometer or higher
1.00
200 (1.4)
II
1/8 inch thick
2.00
1600 (11)
II
1/16 inch thick
2.75
3700 (26)
II
1/32 inch thick
3.50
6500 (45)
II
Elastomer with cotton fabric insertion
1.25
400 (2.8)
II
3 ply
2.25
2200 (15)
II
2 ply
2.50
2900 (20)
II
1 ply
2.75
3700 (26)
II
Vegetable Fiber
1.75
1100 (7.6)
II
2.50
10000 (69)
II
Self energizing types (O rings, elastomer, other gasket types considered as self-sealing) Elastomers without fabric or high percent of mineral fiber
Mineral fiber with suitable binder for operating conditions
Elastomer with mineral fiber fabric insertion (with or without wire reinforcment)
Spiral-wound metal, mineral fiber filled Carbon Steel
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Stainless Steel, Monel, and nickel-base alloys
Facing Column
Seating Stress y, psi (MPa)
Gasket Material
Gasket Factor m
Floating Heads
3.00
10000 (69)
II
Soft aluminum
2.50
2900 (20)
II
Soft copper or brass
2.75
3700 (26)
II
Iron or soft steel
3.00
4500 (31)
II
Monel or 4-6% Chrome
3.25
5500 (38)
II
Stainless - steels and nickel-base alloys
3.50
6500 (45)
II
Soft aluminum
2.75
3700 (26)
II
Soft copper or brass
3.00
4500 (31)
II
Iron or soft steel
3.25
5500 (38)
II
Monel or 4-6% Chrome
3.50
6500 (45)
II
Stainless steel
3.75
7600 (52)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel
3.50
8000 (55)
II
4-6% chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
3.75
9000 (62)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel or 4-6% Chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
4.25
10100 (70)
II
Soft aluminum
4.00
8800 (61)
I
Soft copper or brass
4.75
13000 (90)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steels and nickel-base alloys
6.50
26000 (180)
I
Corrugated metal, mineral fiber inserted or Corrugated metal, jacketed, mineral fiber filled
Corrugated metal, not filled
Flat metal, jacketed, mineral fiber filled
Grooved metal
Solid flat metal
Ring Joint
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Facing Column
Seating Stress y, psi (MPa)
Gasket Material
Gasket Factor m
Floating Heads
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steel
6.50
26000 (180)
I
Flange Face Facing Sketch - Using Table 2-5.2 of the ASME Code, select the facing sketch number according to the following correlations: FACING SKETCH
DESCRIPTION
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Column for Partition Gasket Seating - Enter the gasket column for gasket seating.
Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. For sketch 9, however, this is not a nubbin width. Instead, it is the contact width of the metallic ring.
Miscellaneous Tab Distance from Flange Centroid to Head Centerline, hr - Enter the distance from the flange centroid to the intersection of the head centerline and the flange. This distance is known as the hr dimension and should be entered in the corroded condition. The hr dimension is positive if it is above the flange centroid and is negative if it is below the flange centroid.
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If the Distance from Flange Top to Flange/Head Intersection is known, you can enter it in the un-corroded condition and click Compute. The software will calculate the hr dimension in corroded condition and place its value in the input.
CodeCalc User's Guide
Floating Heads
The hr dimension is used in the Code calculation but not in the Soehren's calculation as shown in the following illustration:
Distance from Flange Top to Flange/Head Intersection - Enter the distance from the top of the floating head flange to the intersection of the dished head makes with the flange. This value is a positive dimension.
The software can use the value you enter to automatically calculate the hr dimension (Distance from Flange Centroid to Head Centerline). After you enter a value for Distance from Flange Top to Flange/Head Intersection, click Compute. The software will calculate the distance from the flange centroid to the mid-point of the flange/head intersection (hr). Enter the dimension in the un-corroded condition. During the calculation, the software automatically considers the corrosion allowance to compute hr, as shown in the following illustration:
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Floating Heads Is the Flange Slotted? - Check this box if the flange has slotted bolt holes for quick opening. A slotted flange has bolt holes that extend radially to the outer edge of the flange. The software automatically adjusts for this condition; you do not have to change the flange outside diameter. Perform Soehrens Calculations? - Check this box if you want to perform Soehren's Calculation. Soehren's calculation is a more detailed analysis of the interaction between the spherical cap and the flange. Frequently, the stresses calculated using this method will be acceptable for heads or flanges that are slightly less thick than required by the normal code rules. This analysis can only be done for type d heads. The Code (Par. 1-6(h)) allows this type of analysis. Inside Depth of Flange (Flange Face to Attached Head) - Enter the distance from the bolting face of the flange to the intersection of the head inside diameter and the flange (Q). This value (Q) is used in Soehren's calculation, while hr is used in the Code calculation.
Is there a Backing Flange? - Check this box if there is a backing ring. A backing ring is a second flange used to sandwich the tubesheet of a floating head heat exchanger. If the backing ring is a split ring, consider the following guidelines: If the ring has one split, then it has been split along a diameter into two pieces. For split rings, the bending moment on the ring is multiplied by 2.0. A ring with two splits has been sliced in half like a bagel, and then each half has been split along a diameter. The ring is assembled with the diametrical splits offset by 90-degrees. For this case, enter the thickness of one half of the original ring, since each half is required to support 75% of the original design moment. Backing Ring Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Floating Heads Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Backing Ring Inside Diameter - Enter the inside diameter of the backing ring. This value is usually a little larger than the inside diameter of the flange. Backing Ring Actual Thickness - Enter the actual thickness of the backing ring. For doubly-split rings, this is the thickness of each piece, as shown in the following illustration:
Figure 27: Flange Thickness
Number of Splits in Backing Ring - Enter the number of splits in the ring, if any, for loose type flanges. You can select 0, 1, or 2. Typically, split flanges are ring-type flanges. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. The following illustration shows a ring with a single split:
Figure 28: Single Split Ring
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Floating Heads If a flange consists of two separate split rings, each ring shall be designed as if it were a solid flange (without splits), using 0.75 times the design moment. The software automatically considers this. The flange thickness in the input, as well as the required value, is the thickness of the quarter piece. As a result, the thickness of the total ring is twice this value. The pair of rings shall be assembled so that the splits in one ring shall be 90-degrees from the splits of the other. The following illustration shows a flange with two splits:
Figure 29: Flange Thickness
TEMA RCB-5.141 shows different styles of backing devices, though the Styles A and D have a split ring, but the moment used to design them is not increased. When you have one of these styles, set the number of splits to 0 in CodeCalc to get the same effect. Mating Flange Loads - Check this box if loads from the mating flange are to be considered. This auxiliary bolt loading will only be used if it is greater than the standard bolt loads computed using the ASME formulas. Mating Flange Bolt Load, Operating - Specify the alternate operating bolt load such as from the mating flange. This value will be used if it is greater than the operating bolt load computed by the software. Mating Flange Bolt Load, Seating - Specify the alternate seating flange bolt load such as from the mating flange. This value will be used if it is greater than the seating bolt load computed by the software. Mating Design Bolt Load - Specify the alternate flange design bolt load such as from the mating flange. This value will be used if it is greater than the flange design bolt load computed by the software.
Results Topics
Internal Pressure Results for the Head: ........................................ 133 External Pressure Results for Heads: ........................................... 133 Intermediate Calculations for Flanged Portion of Head ................. 133 Required Thickness Calculations .................................................. 133 Soehren's Calculations: ................................................................. 134
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Floating Heads
Internal Pressure Results for the Head: The ASME Code provides a simple formula for calculating the required thickness of the head under internal pressure. This formula is the same for type b, c, and d heads: t=5PL/6S The software solves this formula for required thickness, maximum allowable working pressure, and actual stress, and displays the results. These results are also displayed in the thickness summary at the end of the printout.
External Pressure Results for Heads: The required thickness and maximum allowable working pressure for each head type is based on the external pressure requirements for an equivalent sphere.
Intermediate Calculations for Flanged Portion of Head Three separate bending moments are calculated for each head: The bolt up moment The moment due to external pressure The moment due to internal pressure In each case, the moment is calculated per the ASME Code, Section VIII, Division 1, Appendix 2. However, in the case of the type d head the moment is further modified to take into account the force imposed on the flange by the pressure on the head. This force is shown in the printout as MH. The sign of this force will be negative if the head is attached above the centroid of the flange, and positive if the head is attached below the centroid.
Required Thickness Calculations The required thickness formula for each flange type and loading condition are printed by the software. These formulas are taken from Appendix 1-6, paragraphs (e)(2) and (3), (f)(2) through (5) and (g)(2). The required thickness calculations for the backing ring are also shown. The backing ring is taken as a ring flange and calculated per Appendix 2. The analysis is corrected for the number of splits in the backing ring, and shows the required thickness for each piece of the split ring. The thickness calculations for the main flange and backing ring involve the factor F that is directly proportional to the design pressure. Thus when the pressure is 0 for the bolt-up condition, the factor F is theoretically equal to 0. Some however interpret the Code to mean that F should be computed using the design pressure even for the bolt-up cases. There is a setup file directive that allows you to toggle this to work one way or the other. To keep the software results consistent with older versions, this setup file parameter is set to compute F with 0 pressure for the bolt-up conditions. After the required thicknesses are calculated, a summary table is printed.
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Floating Heads
Soehren's Calculations: The ASME Code, Section VIII, Division 1, Appendix 1-6, paragraph (h) states: These formulas are approximate in that they do not take into account continuity between the flange ring and the dished head. A more exact method of analysis, which takes this into account may be used if it meets the requirements of U-2. The analysis referred to in this paragraph is Soehren's calculation, based on the paper The Design of Floating Heads for Heat-Exchangers, ASME 57-A-7-47. Intermediate results and calculated stresses are shown in the printout. Equation numbers are included from the original paper. Allowable stresses are not shown in the printout, but bending stresses should be limited to 1.5 times the basic Code allowable stress, while membrane stresses should be limited to 1.0 times the basic Code allowable.
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SECTION 8
Flanges
Home tab: Components > Add New Flange Calculates actual and allowable stresses for all types of flanges designed and fabricated to the ASME Code, Section VIII, Division 1. The software uses the Code rules found in Appendix 2 of the 2010 Edition.
In This Section
Purpose, Scope, and Technical Basis (Flanges)........................... 135 Flange Data Tab ............................................................................ 138 Hub/Bolts Tab ................................................................................ 142 Gasket Data Tab ............................................................................ 144 Results (Flanges) ........................................................................... 148
Purpose, Scope, and Technical Basis (Flanges) The flange design rules incorporated in the Code were based on a paper written in 1937 by Waters, Westrom, Rossheim, and Williams. These rules were subsequently published by Taylor Forge in 1937, and were incorporated into the Code in 1942. For all practical purposes they have been unchanged since that time. The Taylor Forge bulletin, frequently republished, is also still available, and is one of the most useful tools for flange analysis. The input and results for the FLANGE software are roughly modeled on the Taylor Forge flange design sheets. The flange analysis model assumes that the flange can be modeled as stiff elements (the flange and hub) and springs (the bolts and gaskets). The initial bolt loads compresses the gasket. This load needs to be high enough to seat (deform) the gasket, and needs to be high enough to seal even when pressure is applied. The pressure load adds to the bolt load and unloads the gasket. Analysis of a typical flange includes the following steps: 1. Identify operating conditions and materials. Determine the allowable stresses for the flange material and the bolting at both ambient and operating temperatures, from the Code tables of allowable stress. 2. Identify the gasket material and the flange facing type. Determine the effective width, the effective diameter of the gasket and the gasket factors from the Code charts (Tables 2-5.1 and 2-5.2). 3. Calculate the required area of the bolts, from the design pressure and the gasket information. Calculate the actual area of the bolts, and make sure it is greater than the required area. Based on the bolt areas and the allowable stresses, calculate the flange design bolt loads. 4. Calculate the bending moments on the flange. In each case the bending moment is the product of a load (pressure, gasket load, etc.) and the distance from the bolt circle to the point of application of the load. The final result is one bending moment for operating conditions and a second for gasket seating conditions. The stresses on a given flange are determined entirely by the bending moment on the flange. All the loads on the flange produce bending in the same direction (i.e., counterclockwise) and this bending is resisted by the ring behavior of the flange, and in integral flanges by the reaction of the pipe.
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Flanges 5. Calculate the hub factors and other geometry factors for the flange based on the flange type (Code Figure 2-4). The factors are found in Code figures 2-7.1, 2-7.2, 2-7.3, 2-7.4, 2-7.5, and 2-7.6. Formulae are also given in the Code so that computer software can consistently arrive at the answers that are normally selected from charts in the appendix. These formulae are implemented in the Flanges. 6. Calculate the stress formula factors based on the geometry factors and the flange thickness. 7. Calculate the flange stresses using the stress formula factors and the bending moments. Compare these stresses to the allowable stresses for the flange material. The form of the stress equations is: S = k(geometry) * M / t2 That is, a constant dependent on the flange geometry times the bending moment, divided by some thickness squared, either the thickness of the flange or the thickness of the hub. The calculation procedures and format of results are similar to those given in "Modern Flange Design", Bulletin 503, Edition VII, published by Taylor Forge. Flanges includes the capability to analyze a given flange under the bolting loads imposed by a mating flange. The software also takes full account of corrosion allowance. You enter uncorroded thicknesses and diameters, which the software adjusts before performing the calculations. Corrosion in treated in a special manner if indicated. The command can also be used for two levels of flange design. The Partial option forces the software to calculate the minimum flange thickness for a given geometry. The Design option forces the software to select all of the relevant flange geometry including bolt circle, number of bolts, outside diameter, thickness, and hub geometry.
Flange Design The defined geometry is the basis for the design performed by the software. The inside diameter, materials, pressure, gasket geometry and gasket properties remain fixed throughout the design. Beginning from this point, the software uses the following approach to design the rest of the flange: 1. For slip-on type flanges, calculate the small end of the hub equal to roughly the thickness required for the design pressure 2. For weld neck, slip-on, and reverse flanges, calculate the large end of the hub as the small end of the hub plus 1/16th (for small end thickness less than one inch) or 1/8th (for small end thickness greater than one inch). Then calculate a hub length equal to the small end thickness plus the minimum slope (3:1) for the hub. The effect of these choices is to design a small hub when compared with standardized flanges. This has the additional effect of keeping the moment arms and diameters (of the bolt circle and flange OD) small, and keeping the flange light. Finally, the selection of a small hub keeps the amount of machining required for the flange to a minimum. 3. Select a preliminary number of bolts. This is a multiple of four based on the diameter of the flange. The algorithm chosen tends to select more and smaller bolts than would be found on standard flanges. This also has the effect of minimizing the flange outside diameter and the weight of the flange. 4. Select a bolt size that will give the required bolt area for this number of bolts. 5. Using this bolt size, calculate a final number of bolts based on: The area required divided by the area available per bolt -ORThe maximum allowed spacing between bolts of this size. 6. Using this number of bolts, calculate the bolt circle based on: The OD of the hub plus the minimum ID spacing of the bolt -OR-
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Flanges The OD of the gasket face plus the actual size of the bolt -ORThe minimum spacing distance between the bolts -ORFor reverse flanges, the vessel OD plus the bolt ID spacing. 7. Calculate the outside diameter of the flange based on the bolt circle plus the minimum edge spacing for the bolt size chosen. 8. For flanges with full face gaskets, adjust the gasket and face outside diameter for the values chosen, and recalculate the moment arms for the flange. 9. Select a thickness for the flange and calculate the stresses. If the stress is not equal to the allowable, adjust the thickness based on the difference between the actual and allowable stresses, and then repeat the stress calculation. Repeat until the actual stress for one of the stress components is equal to the allowable stress. This step also applies to partial design of the flange.
Figure 30: Flange Dimensions
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Flange Data Tab Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. Type of Flange - Enter the flange type number for this flange. Flange types are:
Integral Weld Neck Integral Slip On Integral Ring Loose Slip On
Loose Ring Lap Joint Blind Reverse
There are essentially only two categories of flanges for the purposes of analysis. These are integral type flanges, where the flange and the vessel to which it is attached behave as a unit, and loose types, where the flange and the vessel do not behave as a unit. Within these categories, however, there are several additional subdivisions. Weld Neck Flanges - These have a hub that is butt welded to the vessel. Slip-on Flanges - These have hubs, and are normally analyzed as loose type flanges. To qualify as integral type flanges they require a penetration weld between the flange and the vessel. Ring Flanges - These do not have a hub, though they frequently have a weld at the back of the flange. They are normally analyzed as loose, but may be analyzed as integral if a penetration weld is used between the flange and the vessel. Lap Joint Flanges - These flanges may or may not have a hub, but they are completely disconnected from the vessel, bearing only on a vessel 'lap'. They are always analyzed as loose. Reverse Geometry Flange - Here the gasket seat is on the inside of the shell diameter. These use integral flange rules, which are suitably modified for the reversal of the bending moments. See Appendix 2-13. Loose Type Flanges - Especially lap joints, may be split. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange (without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90 deg. from the splits in the other. Flat Face Flanges with Full Face Gaskets - A special type of gasket geometry, which is not included in the Code sketches, or in the Code design rules, is the flange with a flat face and a gasket that extends from the ID of the flange to the OD, beyond the bolt circle. The gaskets used with this type of flange are usually quite soft. These flanges can be analyzed using the Taylor Forge calculation sheets.
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Flanges Number of Splits in the Ring - Enter the number of splits in the ring, if any, for loose type flanges. This value must be either 0, 1, or 2. Typically split flanges are ring-type flanges. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange - without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90º deg. from the splits in the other.
Figure 31: Single Split Ring
If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. Above diagram shows a ring with a single split.
Figure 32: Double Split Ring
If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange (without splits) using 0.75 times the design moment. The software automatically considers this. The flange thickness in the input (and the required value) is the thickness of the quarter piece. So, the thickness of the total ring is twice this value. The pair of rings shall be assembled so that the splits in one ring shall be 90º from the splits in the other. The above diagram shows a flange with two splits. Weld Leg at Back of Ring - Enter the length of the weld leg at the back of the ring. This value is added to the inside diameter during the design of ring type flanges to determine the minimum bolt circle when the design option is turned on. If you are performing a partial or regular analysis, CodeCalc will check to see if there is interference between the wrench and the weld. CodeCalc will print a brief message letting you know there is a potential problem. Type of Analysis - Enter the analysis type for the computations to be performed on this flange.
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Flanges Do not leave any fields blank. CodeCalc uses these values as initial guesses. Zeroes do not make good starting guesses. Analyze - For this analysis type, users must give the complete flange definition. The software computes the resulting stresses. Partial - For this analysis type, all information except for the flange thickness must be specified. The software selects a flange thickness such that the resulting flange stress equals the allowable stress. Design - For this analysis type, only the flange diameter and thickness, gasket and flange face geometry, and gasket properties are specified. The software computes all other flange dimensions and stresses. Print Final Results for Given Thickness? - When Partial is selected and this option is selected, the results display using the given thickness. If this option is cleared, the results display using the calculated required thickness. Design Pressure - Enter the internal design pressure. If the value entered in this field is negative, it will be treated as external pressure. Design Temperature - Enter the design temperature for the flange. This temperature will be used to interpolate the material allowable tables and external pressure curves. Flange Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Flange Thickness - Enter the flange thickness. The corrosion allowance will be subtracted from this value. CodeCalc will not automatically subtract the corrosion allowance off of the flange thickness. If you enter a corrosion allowance, you will be prompted whether or not you wish to corrode the flange thickness for the flange factor and stress computation. Corrosion Allowance - Enter the corrosion allowance for this flange. The value entered here will be subtracted from the flange and hub thicknesses to obtain the thicknesses actually used in the computations. Flange Inside Diameter - Enter the inner diameter of the flange. For integral type flanges, this value will also be the inner pipe diameter. This value is referred to as "B" in the ASME code. The corrosion allowance will be used to adjust this value - two times the corrosion allowance will be added to the uncorroded ID given by the user. See the figure in Flange Diameters. For blind flanges the Flange ID is 0.0. For Reverse flanges this is the B` dimension as shown in appendix 2 of the ASME Code.
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Flanges Flange Outside Diameter - Enter the outer diameter A of the flange, as defined in the ASME code. If the flange is corroded from the outside, use a corroded dimension.
Shell Material - Select the shell material name. This is used for computing the longitudinal hub allowable stress for optional type flanges, which are analyzed as integral. Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Are the Hub and Attached Shell Material the Same? - Select to indicate that the flange material is same as the attached shell material for an integral weld neck or reverse type flange. The larger of the shell allowable and the flange allowable are used to compute the required small end hub thickness for the integral flanges. Otherwise only the flange allowable will be used. For some materials with relatively low yield strength (e.g. stainless steels), the ASME code has established higher stress values. These higher stress values (indicated by the presence of the note g5) can lead to higher deformation. These material allowables are not used for applications where deformation can cause failure such as flanges. There could be a case where the flange allowables are lower as compared to the attached shell, for the same material. But, the small end hub thickness is checked as a cylinder so the allowable stresses of the attached shell should be used. Otherwise, the hub required thickness may be more than that of the attached cylinder. If you want the (higher) shell allowables to be used then check this box.
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Hub/Bolts Tab Flange Face Outer Diameter - Enter the outer diameter of the flange face. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. If there is no raise flange face, please enter gasket OD. See Flange Face Figure (on page 143). Flange Face Inner Diameter - Enter the inner diameter of the flange face. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. If there is no raise flange face, please enter the gasket ID. See Flange Face Figure (on page 143). Gasket Inner Diameter - Enter the inner diameter of the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. See Flange Face Figure (on page 143). Gasket Outer Diameter - Enter the outer diameter of the gasket. The soaftware uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. See Flange Face Figure (on page 143). Hub Thickness, Large End - Enter the thickness of the large end of the hub. This value is referred to as "g1" in the ASME code. The corrosion allowance will be subtracted from this value. It is permissible for the hub thickness at the large end to equal the hub thickness at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. See Flange Face Figure (on page 143). Hub Thickness, Small End - Enter the thickness of the small end of the hub. This value is referred to as "g0" in the ASME code. The corrosion allowance will be subtracted from this value. For weld neck flange types, this is the thickness of the shell at the end of the flange. For slip on flange geometries, this is the thickness of the hub at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. See Flange Face Figure (on page 143). Hub Length - Enter the hub length h, as defined in the ASME code. For flange geometries without hubs, this length can be zero. When analyzing an optional type flange that is welded at the hub end, the hub length should be the leg of the weld, and the thickness at the large end should include the thickness of the weld. When you analyze a flange with no hub, such as a ring flange, or a lap joint flange, enter zero for the hub length, the small end of the hub, and the large end of the hub. However, when you design a ring flange as a loose flange that has a fillet weld at the back, enter the size of a leg of the fillet weld as the large end of the hub. This ensures that the software designs the bolt circle far enough away from the back of the flange to get a wrench around the nuts. For more information, see Flange Face Figure (on page 143). Diameter of Bolt Circle - Enter the nominal bolt diameter. The tables of bolt diameter included in the software range from 0.5 to 4.0 inches. This value is used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field. Also, enter the root area of one bolt in the Root Area cell. Thread Series - The following bolt thread series tables are available: TEMA Bolt Table
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Flanges UNC Bolt Table User specified root area of a single bolt TEMA Metric Bolt Table British, BS 3643 Metric Bolt Table Irrespective of the table used, the values will be converted back to the user selected units. TEMA threads are National Coarse series below 1 inch and 8 pitch thread series for 1 inch and above bolt nominal diameter. The UNC threads available are the standard threads. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this field. This option is used only if bolt root area is greater than 0.0. Number of Bolts - Enter the number of bolts to be used in the flange analysis. This is usually an even number. The number of bolts is almost always a multiple of four. Use Full Flange Design Bolt Load (S*Ab)? - If this box is un-checked then flange design bolt load for the gasket seating condition is computed as: W = Sa * ( Am + Ab ) / 2 Otherwise it is computed as follows according to note 2 of App. 2-5 of the ASME code: W = Sa * Ab This equation can be used when additional safety against abuse is desired. Where, Sa = bolt ambient allowable stress Am = total required bolt area Ab = total available bolt area
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Gasket Data Tab Gasket Factor m - Specifies the ratio of the residual stress on the gasket under operating pressure to the operating pressure itself. The value of m is listed in ASME Sec. VIII Div. 1, App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Gasket Design Seating Stress Y - Specifies the stress on the gasket necessary to form to the face of the flange. The value of y is listed in ASME Sec. VIII Div. 1, App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Flange Face Facing Sketch - Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: Facing Sketch
Description
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Column for Gasket Seating (I,II) - The facing columns are listed in ASME Sec. VIII Div. 1, App. 2. As stated in the code, these are only suggested values. For more accurate values of m, y, and their relative facing columns please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Full Face Gasket Option - ASME Sec. VIII Div. 1 does not cover the design of flanges for which the gasket extends beyond the bolt circle diameter. Select this option to use a typical method for the design of these types of flanges is from the Taylor Forge Flange Design Bulletin. Gaskets for the full face flanges are usually of soft materials such as rubber or an elastomer, so that the bolt stresses do not go too high during gasket seating. The software adjusts the flange analysis and the design formulae to account for the full face gasket. There are 3 Full Face Gasket Flanges options: Program Selects - Select to automatically make the determination if this is a full face gasket flange, depending upon the input. If the gasket ID and OD matches with Flange ID and OD
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Flanges dimensions respectively (except for a blind flange) then it is determined to be a full face flange. See the figure below.
Full Face Gasket - Select if this is a full face gasket flange. Use this option when the gasket ID or OD does not match the flange ID/OD dimensions, but the gasket extends beyond the bolt circle diameter. See the figure below:
Not a Full Face - Select if this is not a full face gasket flange. Is There a Partition Gasket? - If your exchanger geometry has a pass partition gasket, check this entry. CodeCalc will then prompt for the overall length and width of the gasket. Length of Partition Gasket - This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. Width of Partition Gasket - Enter the width of the pass partition gasket. Using the gasket properties specified and the known width, CodeCalc will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Gasket Factor m - Specifies the ratio of the residual stress on the gasket under operating pressure to the operating pressure itself. The value of m is listed in ASME Sec. VIII Div. 1, App.
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Flanges 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Gasket Design Seating Stress - Specifies the stress on the gasket necessary to form to the face of the flange. The value of y is listed in ASME Sec. VIII Div. 1, App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Partition Gasket Facing Sketch - Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: Facing Sketch
Description
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Column for Gasket Seating (I, II) - The facing columns are listed in ASME Sec. VIII Div. 1, App. 2. As stated in the code, these are only suggested values. For more accurate values of m, y, and their relative facing columns please contact your gasket manufacturer. See, Table 2-5.1 Gasket Materials and Contact Facings Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Specify External Loads? - For leakage computations to be performed, the external loads acting on the flange must be specified. Select this option to enter the loading data. The loading data is typically from pipe stress analysis software, such as CAESAR II. Flanges are frequently subject to external forces and moments, in addition to internal pressure. The software calculates a roughly equivalent pressure for flanges loaded axially and/or in bending using the following formula: Peq = Pdes + 4 * F / 3.14 G2 + 16 * M / 3.14 * G3 Where: Peq = Equivalent pressure, psi Pdes = Design pressure, psi F = Axial force, lbs M = Bending moment, in-lbs G = Diameter of gasket load reaction, in.
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Flanges The software then uses the equivalent pressure as the design pressure. Node Number - Enter the node number of this flange. This entry represents the node point in a stress analysis model from which the loads are obtained. Axial Force - Enter the magnitude of the external axial force, which acts, on this flange. Bending Moment - Enter the magnitude of the external bending moment, which acts, on this flange. Mating Flange Loads? - If loads from the mating flange are to be considered, check this field. A pop-up spreadsheet will appear for additional data entry. This auxiliary bolt loading will only be used if it is greater than the standard bolt loads computed using the ASME formulas. The use of mating flange values for bolt design calculations will result in incorrect MAWP calculations. Do not calculate MAWP based on the mating flange values, but instead based on the values developed by this flange at a given pressure. Do not do a design when you have a mating flange, because the software selects a different values (such as bolt circle) from the one chosen for the other flange. You can however, do a partial thickness design. Mating Flange Bolt Load, Operating, WM1 - Enter the bolt load from the mating flange in the operating case. Mating Flange Bolt Load, Seating, WM2 - Enter the bolt load from the mating flange for seating conditions. Mating Flange Bolt Load, Design W - Enter the design bolt load for the mating flange. Apply Corrosion to the Flange Thickness? - If you check this field, the software uses the corrosion allowance as it always has when computing the final stresses on the flange. If you say no, when the stresses are computed, the corrosion is not subtracted from the flange thickness. Saying no here will typically produce a thinner flange that is not as highly stressed. Also the MAWP of the flange will usually be slightly higher. Since this is not directly addressed by any code, agreement on this subject is usually between the client and the manufacturer.
The flange thickness is used in several places throughout Appendix 2. The Code states that every dimension used should be corroded. In the flange stress calculations the flange thickness is used. However, some feel that the corrosion should not be taken off of the thickness for the stress calculations. Compute Thickness Based on Flange Rigidity? - Select this option to compute thickness so that corresponding rigidity index is 1.0. Appendix 2 contains equations that attempt to determine whether or not a given flange geometry will leak. If the computed rigidity factor is > 1.0, then leakage is predicted.
Appendix 2 calculations are mandatory as of Addenda-2005 and flange designs must satisfy these calculations. These rigidity factor calculations are not mandatory for Pre-1999 Addenda users Appendix S is non-mandatory appendix and that these calculations are also non-mandatory.
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Flanges
Results (Flanges) Flanges with Different Bending Moments: The flange design moments differ from the norm for external pressure, reverse flanges, and flat flanges. Under external pressure only the end load and flange pressure are included in the design, and their signs are reversed. For reverse flanges all the moments are present, but the moment arm hd is negative, making MD negative. The load HT is negative, and the moment arm ht may be either positive or negative. The absolute value of the moment is used in the calculations. For flat faced flanges an alternate value of hg (h''g) is used to calculate a reverse moment at the bolt circle. No calculations for seating conditions for full faced flanges are required.
Blind Flanges and Channel Covers: The ASME Code formula for a circular blind flange is: t = d * SQRT( C * P / S * E + 1.9 * W * Hg / S * E * d3 )
The first term in this formula is the bending of a flat plate under pressure. The second term is the bending of the plate due to an edge moment. The stress is limited to 1.5 times the allowable stress, but the 1.5 factor is already built into the equation. For seating conditions the first term is zero - the thickness of the flange depends only on the edge bending. For non-circular blind flanges the term Z is added to the first term in the square root. Once again, Z is a simple function of the ratio of the large dimension to the small dimension of the flange. It is interesting to note that the Code covers non-circular blind flanges, but no other type of non-circular flanges (not even in the rectangular vessel appendix). Channel covers designed to TEMA must meet at least the minimum thickness requirements of the Code. In addition, if there is a pass partition groove, the cover deflection is limited. The formula for flange deflection limitation is found in paragraph 9.21 of TEMA. The deflection is, of course, a function of t3 and G3. Thus, a very small increase in flange thickness will decrease the deflection significantly. The Seventh Edition of TEMA also gives recommended deflections as a function of flange size. The previous editions hid the actual deflection you were working toward in a thickness equation.
Allowable Flange Stresses: Allowable flange stresses are based on the ASME Code Allowable Stress for the flange material at the Ambient and Operating design temperatures. In the case of bending stresses, these allowable are multiplied by 1.5. This takes into account the higher maximum strain required to yield a section in bending versus pure tension. The stresses calculated and the allowable stresses are as follows:
148
Operating
Ambient
Longitudinal Hub Stress (bending)
1.5 x Sfo
1.5 x Sfa
Radial Flange Stress
1.0 x Sfo
1.0 x Sfa
Tangential Flange Stress
1.0 x Sfo
1.0 x Sfa
Maximum Average Stress
1.0 x Sfo
1.0 x Sfa
Stress in Bolts
1.0 x Sbo
1.0 x Sba
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Flanges Stress in Reverse Flanges
1.0 x Sfo
1.0 x Sfa
Stress in Full Faced Gasket Flanges
1.0 x Sfo
1.0 x Sfa
Where:
Sfo = ASME Code Allowable Stress for flange material at operating temperature. Sfa = ASME Code Allowable Stress for flange material at ambient temperature. Sb = ASME Code Allowable Stress for flange material at o ambient temperature. Sb = ASME Code Allowable Stress for bolt material at a ambient temperature.
Maximum Allowable Working Pressure: The following graph shows conceptually how the software extrapolates for the Maximum Allowable Working Pressure:
1. For Operating Pressure MAWP The software calculates the stresses at the pressure given and calculates the slope between the stress at zero pressure and the stress at the given pressure.
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Flanges The software extrapolates the slope out to the point where the stress is equal to the allowable stress. The pressure at this point is the maximum allowable working pressure.
2. For Gasket Seating MAWP Note that at low pressures the stress due to gasket seating is not a function of the design pressure. At higher pressures the stress is a function of pressure, and the MAWP can be calculated as described above, except that the extrapolation is from the point where pressure comes into the calculation of the seating stress. The software calculates the Gasket Seating MAWP and Operating MAWP based on the input geometry and pressure. In theory both MAWPs should be independent of the input pressure. However, because of the extrapolation algorithm, the estimate of the MAWP may depend on the pressure slightly (when the pressure is very small). Please note that in Partial or Design mode, the software calculates MAWP based on the required flange thickness.
Flange Rigidity Calculations Appendix 2 also contains equations that attempt to determine whether or not a given flange geometry will leak. The cases considered are ambient and operating. If the computed rigidity factor is > 1.0, then leakage is predicted. Appendix 2 calculations are mandatory as of Addenda-2005.
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SECTION 9
TEMA Tubesheets Home tab: Components > Add New TEMA Tubesheet Performs tubesheet thickness analysis for all tubesheet types, including fixed tubesheet exchangers, based on the Standards of the Tubular Exchanger Manufacturer's Association, 8th Edition, 1999 or PD 5500, 2004 (British standard). Flanged and flued (thick) expansion joint for a fixed tubesheet is also analyzed per TEMA and ASME Sec. VIII Div. 1 Appendix 5.
In This Section
Purpose, Scope, and Technical Basis (TubeSheets) .................... 151 Shell Tab (TEMA Tubesheets) ...................................................... 155 Channel Tab (TEMA Tubesheets) ................................................. 156 Tubes Tab (TEMA Tubesheets) .................................................... 157 Tubesheet Tab (TEMA Tubesheets) ............................................. 161 Expansion Joint Tab (TEMA Tubesheets) ..................................... 166 Tubesheet Extended as Flange Dialog (TEMA Tubesheets) ........ 169 Outer Cylinder Dialog Box ............................................................. 171 Shell Band Properties Dialog Box ................................................. 172 Multiple Load Cases Dialog Box (TEMA Tubesheets) .................. 173 Tubesheet Gasket Dialog Box ....................................................... 173 Fixed Tubesheet Exchanger Dialog Box ....................................... 176 Kettle Tubesheet Dialog Box ......................................................... 177 Results (Tubesheets) ..................................................................... 177
Purpose, Scope, and Technical Basis (TubeSheets) TUBESHEETS calculates required thickness and Maximum Allowable Working Pressure of tubesheets for all of the exchanger types described in the 8th Edition of the Standards of the Tubular Exchanger Manufacturers Association (TEMA) and PD 5500. It also calculates thermal stresses and forces in the shell and tubes of fixed tubesheet exchangers. Load on the Tube-Tubesheet joint is also checked per the method provided in the ASME and PD 5500 codes respectively. This program will analyze the following tubesheet types: Stationary tubesheets, gasketed between the shell and the channel. Stationary tubesheets, integral with the shell and the channel. Stationary tubesheets, integral with the shell only. Stationary tubesheets, integral with the channel only. U-tube exchangers, tubesheet gasketed between shell and channel U-tube exchangers, tubesheet integral with channel only. U-tube exchangers, tubesheet integral with shell only. U-tube exchangers, tubesheet integral with both shell and channel. Floating tubesheets, outside packed floating head (P). Floating tubesheets, floating head with backing device (S). Floating tubesheets, pull through floating head (T).
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TEMA Tubesheets Floating tubesheets, externally sealed floating head (W). Floating tubesheets, divided floating head. Fixed tubesheets, stationary tubesheet at both ends. The program does the required calculations for the thickness of a tubesheet that has been extended as a flange. It also calculates the required thickness of the extension. You must enter the geometry of the flange extension, including the gasket and bolting for the flange. TUBESHEETS takes into account the following additional loadings for fixed tubesheet exchangers: Expansion joints - thin walled, thick walled, or none. Tubesheets - integral, gasketed, or extended as flanges. Pressure and thermal loads - on shell, tubesheet, tubes and tube-to-tubesheet joints. Differential pressure designs. It is possible to analyze multiple load cases (startup, shut-down etc) for fixed tubesheets, in both the corroded and uncorroded condition.
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TEMA Tubesheets Program can also analyze a thick expansion joint attached to a fixed tubesheet. The expansion joint spring rate and stresses are computed per TEMA standard. The actual stresses are then compared with the allowables provided in ASME Sec. VIII Div. 1, Appendix 5 to check the joint's adequacy.
Figure 33: TEMA Tubesheet Module Geometry
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TEMA Tubesheets
Figure 34: Fixed Tubesheet Exchanger with Expansion Joint
Figure 35: Tubesheet Extended as a Flange Geometry
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Shell Tab (TEMA Tubesheets) Item Number - Type an ID number for the tubesheet. This might be the item number on the drawing, or numbers that start at 1 and increase sequentially. More than one pressure or temperature case can be run. Press the + key, enter a new tubesheet number and change the relevant input items. Description - Type an alphanumeric description for this item. This entry is optional. Entering a description will help you keep up with each item when reviewing the output. Merge - Use this option to import data from the Shells and Heads module. Select the shell you want to add to the model, and press enter, all the appropriate data for that shell is copied in automatically. Tubesheet Design Code - Select the design code to be used for designing the tubesheets. Options available are: TEMA - Tubular Exchanger Manufacturers Association, Inc. PD5500 - British standard (formerly known as BS 5500) ASME tubesheet can also be designed in the ASME tubesheet module. Shell Design Internal Pressure - Type the design pressure for the shell side of the exchanger. If the shell side has external pressure, enter a negative pressure. The program will add this pressure with the positive pressure on the tube (channel) side. Shell Metal Design Temperature - Enter the design metal temperature for the shell side components. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Shell Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Shell Wall Thickness - Type the minimum wall thickness for the shell of the exchanger. The program uses this value to calculate the characteristic diameter for all tubesheets. It is used in the computation of Beta as well as the spring rate and other factors. Shell Corrosion Allowance - Type the shell side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the shell.
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TEMA Tubesheets Shell Inside Diameter (at back of Tubesheet) - Enter the inside diameter for the shell of the exchanger. This value is used by the software to calculate the characteristic diameter for all tubesheets and the longitudinal shell stresses for fixed tubesheet exchangers.
Additional Input for PD 5500 or TEAM Fixed Tubesheet Shell Mean Metal Temperature - Enter the actual metal temperature for the shell under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Do not forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. For a fixed tubesheet, you can instruct the program, to evaluate multiple load cases. Refer to TEMA standard, section T-4 (8th Ed.) for guidance to compute the Mean Metal Temperatures.
Channel Tab (TEMA Tubesheets) Channel Design Internal Pressure - Enter the design pressure for the tube side of the exchanger. If the tube side has a vacuum design condition, enter a negative pressure. The software correctly combines this pressure with the positive pressure on the other side. For TEMA tubesheet calculation: If you specify a differential pressure in the differential pressure input field, the values on the shellside and tubeside will usually be ignored. The exception to this is fixed tubesheet exchangers, where the differential pressure field only serves as a flag to indicate to the program that the appropriate calculations for differential pressure should be performed. For ASME tubesheet calculation: To run a differential pressure case, click Use Differential Pressure Design in the Multiple Load Case dialog box. Merge - Use this option to import data from the Shells and Heads module. Select the shell you want to add to the model, and press enter, all the appropriate data for that shell is copied in automatically. Channel Metal Design Temperature - Enter the design metal temperature for the channel. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Channel Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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TEMA Tubesheets
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Channel Wall Thickness - Type the minimum wall thickness for the channel of the exchanger. The program uses this value to calculate the characteristic diameter for all tubesheet types. An example of such a parameter is the Beta dimension for fixed tubesheet exchangers. Channel Corrosion Allowance - Type the tube side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the channel. Channel Inside Diameter - Enter the inside diameter for the channel of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets.
Additional Input for PD 5500 or TEMA Fixed Tubesheet Tube Mean Metal Temperature - Enter the actual metal temperature for the tubes under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Do not forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. For a fixed tubesheet, you can instruct the program, to evaluate multiple load cases. Refer to TEMA standard, section T-4 (8th Ed.) for guidance to compute the Mean Metal Temperatures.
Tubes Tab (TEMA Tubesheets) Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Tube Design Temperature - Enter the design temperature of the tubes. This value will be used to look up the allowable stress values for the tube material from the material tables.
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TEMA Tubesheets Tube Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Wall Thickness - This value is used to determine the total tube area and stiffness. The following table gives thickness for some common tube gauges: B.W.G. Gauge Thickness (in) 7
0.180
8
0.165
10
0.134
11
0.120
12
0.109
13
0.095
14
0.083
15
0.072
16
0.065
17
0.058
18
0.049
19
0.042
20
0.035
22
0.028
24
0.022
26
0.018
27
0.016
Corrosion Allowance. - Enter the tube corrosion allowance. Number of Holes - Enter the number of tube holes in the tubesheet. This value is used to determine the total tube area and stiffness.
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TEMA Tubesheets For U-tube exchangers, the number of tube holes in the tubesheet is normally equal to two times the number of tubes. Pattern - Enter the pattern of the tube layout. The tube diameter, pitch, and pattern are used to calculate the term 'eta' in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. In the ASME code square patterns have a 90º layout angle and triangular patterns have a 60º angle. Outside Diameter - Enter the outside diameter of the tubes. This is usually an exact fraction, such as .5, .75, .875, 1.0, or 1.25 (inches). The tube diameter, pitch, and pattern are used to calculate the term 'eta' in the tubesheet thickness equation. These rules are the same for triangular, square, rotated triangular and rotated square layouts. Pitch - Enter the tube pitch, the distance between the tube centers. The tube diameter, pitch, and pattern are used to calculate the term "eta" in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Is this a Welded Tube (not Seamless)? - Check this box if the tube has a longitudinal weld seam or in other words it (not seamless). For computing allowable Tube-Tubesheet Joints loads and the longitudinal tube stress, the allowable stress of a seamless tube is needed. If the user selected a welded tube and clicks on this checkbox, then the tube allowable stress is divided by 0.85 to get an equivalent allowable of a seamless tube. This is per note in ASME Sec. VIII Div. 1 UW-20.3 and App. A. The reason for this is that the longitudinal stress does act across the longitudinal seam. So, the joint efficiency of the longitudinal seam is not used in the calculation. Tube to Tubesheet Joint Information? - Check this box to input information about the Tube-Tubesheet joint (weld, classification). This information will be used to determine the minimum acceptable fillet/groove weld size that connects the tube to the tubesheet and the allowable tube-to-tubesheet load. Differential Design Pressure - Enter the differential design pressure if you wish the program to use the differential design rules. The differential pressure is used as the design pressure on both the tubeside and the shellside, except for fixed tubesheet exchangers. In this case any number greater than zero serves as a flag to tell the program to turn on the special differential design pressure rules for fixed tubesheets. You must enter the shell side and tube side design pressures for fixed tubesheet exchangers.
PD 550 or TEMA Tubesheet Input Straight Length of Tubes between - Specify the tube length from either the inner tubesheet faces or outside tubesheet faces (total straight length), this is indicated using the corresponding input on this screen. Straight Length of Tubes - Enter the length of the tubes. For U-tubesheet exchangers this is the straight length of the tube. For fixed tubesheet exchanger this is the overall length from the inside face of one tubesheet to the inside face of the other tubesheet. This value is used to determine the thermal expansion of the tubes. This input is only needed for British tubesheets and TEMA fixed tubesheets. You can specify the tube length from either the inner tubesheet faces or outside tubesheet faces (total straight length). This is indicated using the corresponding input on this screen. End Condition k, - For computing the allowable tube compression, the values of k and SL are required. Where,
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TEMA Tubesheets SL = Unsupported Span of the tube k = Tube end condition corresponding to the span SL. The table below lists the values of k. k
Condition
0.60
For unsupported spans between two tubesheets.
0.80
For unsupported spans between a tubesheet and a tube support.
1.0
For unsupported spans between two tube supports.
For the worst case scenario, enter the values of k and SL that give the maximum combination of k * SL. SL for example, could be the distance between the tubesheet and the first baffle or the tube span between two support baffles. F1 calls different IDs in the two books, but content is the same. Maximun Unsupported Length SL - For computing the allowable tube compression, the values of k and SL are required. Where, SL = Unsupported Span of the tube k = Tube end condition corresponding to the span SL. The table below lists the values of k. k
Condition
0.60
For unsupported spans between two tubesheets.
0.80
For unsupported spans between a tubesheet and a tube support.
1.0
For unsupported spans between two tube supports.
For the worst case scenario, enter the values of k and SL that give the maximum combination of k * SL. SL for example, could be the distance between the tubesheet and the first baffle or the tube span between two support baffles. F1 calls different IDs in the two books, but content is the same. Length of Expanded Portion of Tube - The expanded portion of a tube is that part which is radially expanded outward within the tube hole. When the tube is expanded, it is also pressed into the tubesheet. Some tubes are welded into place and this value may be zero. The maximum this value can be is the thickness of the tubesheet. A fully expanded tube-tubesheet joint can reduce the tubesheet-required thickness.
TEMA Additional Input Perimeter of Tube Layout (if needed) - Enter the length of a path around the outside edge of the tube layout. This can be calculated by counting the number of tubes on the outside of the layout and multiplying that number by the tube pitch. When a tubesheet might be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. An error message displays when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. This input is only needed for TEMA tubesheets. Area of Tube Layout (if needed) - Enter the area enclosed by a path around the outside edge of the tube layout. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. An error message displays
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TEMA Tubesheets when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter.
PD 5500 Additional Input Diameter of Outer Tube Limit Circle - Enter the diameter of outer tube limit circle, denoted as Do in PD:5500. This input is only needed for British tubesheets (PD:5500). Area of Untubed Lanes (S) - Enter the total area of all the untubed lanes on the tubesheet. If there is no pass partition lane then this area is zero. See the figure below for a single pass exchanger, this area is UL1 * Do.
Figure 36: Area of Untubed Lanes
The maximum limiting value of AL is 4*Do*p. Where, Do = Equivalent diameter of outer limit circle. p = tube pitch UL1 = Distance between innermost tube hole centers (width of pass partition lane) Number of Grooves in Tube Hole - Enter number of grooves in the tube hole.
Tubesheet Tab (TEMA Tubesheets) Type of Tubesheet - The program analyzes the following tubesheet types. When one tubesheet is stationary and the other tubesheet is a floating type, then analyze the stationary tubesheet as one of the stationary types (listed below) and analyze the floating tubesheet as one of the tubesheet types (listed below). Examples include: AEP, AKT, AJW, NET, and so forth. If both tubesheets (front and rear) are stationary, then select the fixed tubesheet type. This can include any of the stationary tubesheet types as the front or rear tubesheet type. Choosing this geometry assures the differential thermal expansion (between the shell and the tubes) is properly accounted. Examples of some fixed configurations are BEM, NGN, AEL, and so forth. Use the table below to determine the correct tubesheet type.
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TEMA Tubesheets Stationary tubesheet, gasketed on both sides (A)
Stationary tubesheets, integral with the shell (B)
Stationary tubesheets, integral with the channel (C)
Stationary tubesheets, integral on both sides (N)
U-tube tubesheets gasketed on both sides (U)
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TEMA Tubesheets U-tube tubesheets integral with the channel (V)
U-tube tubesheets integral with the shell
Floating tubesheets, outside packed floating head (P)
See TEMA figure N-1.2
Floating tubesheets, head with backing device (S)
See TEMA figure N-1.2
Floating tubesheets, pull through floating head (T)
See TEMA figure N-1.2
Floating head, externally sealed floating tubesheet (W)
See TEMA figure N-1.2
Divided floating tubesheet (D)
See TEMA 7.132 type k
Fixed tubesheet exchanger - The following figure displays a NEN fixed two stationary tubesheets tubesheet exchanger. A fixed tubesheet (F) configuration can be comprised of any combination of stationary tubesheets.
Each end can be any type of fixation such as integral, gasketed. Tubesheet Metal Design Temperature - Enter the design metal temperature for the tubesheet. This is the design temperature for determining allowable stresses only. This temperature is not
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TEMA Tubesheets assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Tubesheet Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Tubesheet Extended as Flange? - Select if the tubesheet is extended and used as a bolted flange. If the tubesheet is extended but does not experience the bending moments of the bolts, then select Is Bolt Load Transferred to Tubesheet to allow input echo of the tubesheet extension information without transferring the bolt load to the tubesheet. For example, when the tubesheet is bolted between a pair of identical flanges, it will not experience a bending moment. It is only when the tubesheet replaces one of the flanges that a moment develops. Tubesheet Gasket - Enter the kind of gasketing associated with this tubesheet. Select None if the tubesheet is not sealed with a gasket on either side. Select Shell if the gasket is only on the shell side of the exchanger. Select Channel if the gasket is only on the channel side of the exchanger. Select Both if the gaskets are on both sides of the exchanger. The program will then evaluate the gasket you specify along with the pressure which causes the largest bending moment on the tubesheet. If the tubesheet has a circular gasket, even if the gasket is not extended as a flange, you must enter the details of the gasket, so that the program can correctly evaluate the mean diameter of the gasket load reaction (G).
to open the Tubesheet Gasket/Bolting Input Dialog Box and define the necessary Click properties. Merge Flange - Use this option to import data from the Shells and Heads module. Select the shell you want to add to the model, and press enter, all the appropriate data for that shell is copied in automatically. Depth of Groove in Tubesheet (if any) - If the tube sheet being analyzed has a center groove, enter the depth of the groove. This value will be added to the required thickness of the tube sheet + the corrosion allowances specified. Tubesheet Thickness - Enter the thickness of the tubesheet, or a reasonable estimate at the thickness if the actual thickness is unknown. This thickness should include any allowances for corrosion on the shell side or the tube side. The tubesheet thickness for fixed tubesheet exchangers is also used in the equivalent thermal pressure calculation. When you have finished your design you should come back and put the actual thickness into this field and make sure the required thickness does not change. Tubesheet Corrosion Allowance (Shell side) - Enter the tubesheet corrosion allowance for the shell side. This value is combined with the tubesheet corrosion allowance channel side to calculate the corroded thickness of the tubesheet.
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TEMA Tubesheets Tubesheet Corrosion Allowance (Channel side) - Enter the tubesheet corrosion allowance for the channel side. This value is combined with the tubesheet corrosion allowance shell side to calculate the corroded thickness of the tubesheet. G. dimension for Stationary tubesheet - Enter the G dimension of Stationary Tubesheet to be used for the some floating tubesheet types. If this input is left blank, then the program will compute the G from the specified gasket input. TEMA standard states that for all the floating tubesheet (except divided), the G shall be the G used for the stationary tubesheet. The T type floating tubesheet should also be checked with actual gasket G of the floating tubesheet.
TEMA Input Tubesheet Class - Select the appropriate TEMA class for designing this heat exchanger. R - Generally for severe requirements of petroleum and related processing applications. C - Generally for moderate requirements of commercial and general process applications. B - Generally for chemical process service. This will be used to compute the minimum required tubesheet thickness per RCB-7.13 in the TEMA standard.
PD 5500 Input How are tubesheets Clamped - Select the tubesheet edge condition. This determines how the tubesheet is supported at the edge by the shell or channel. This option is used for the PD:5500 code. Figure 3.9-6 in PD:5500 2003, illustrates the edge support conditions. The available options are listed in the table below: Stationary Simply/ Floating Simply
Select this option if both the stationary and the floating tubesheet are simply supported.
Stationary Simply/ Floating Clamped
Select this option if the stationary tubesheet is simply supported and the floating tubesheet is clamped.
Stationary Clamped/ Floating Simply
Select this option if the stationary tubesheet is clamped and the floating tubesheet is simply supported.
Stationary Clamped/ Floating Clamped
Select this option if both the stationary and the floating tubesheet are clamped.
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TEMA Tubesheets
Expansion Joint Tab (TEMA Tubesheets) Expansion Joint Type - Select the appropriate expansion joint type. The following options are available: None - Select this option when there is no expansion joint in the heat exchanger. Thin Expansion Joint - Select this option if the expansion joint is a bellows type expansion joint. The figure below shows an unreinforced bellows type expansion joint. In this case you should use the Thin Joint module to design the bellows type expansion joints (both reinforced and unreinforced). Then specify the computed spring rate.
Figure 37: Thin Expansion Joint
Thick Expansion Joint - Select this option if the expansion joint is: Flanged and flue Flanged only No flanged or no flue. Design Option - The following options are available: Existing - Select this option if you already know the spring rate of the flanged/flued expansion joint. Analyze - Select this option if you want the program to compute the spring rate of the expansion joint and stresses induced in the expansion joint. Expansion Joint Calculation Method - Enter the expansion joint calculation method. User input Sprint Rate Corroded/Uncorroded - Enter the spring rate for the thin walled (bellows) expansion joint or a thick walled (flanged/flued) expansion joint. If there is no expansion joint, this input should be disabled. The spring rate of the thin walled expansion joint (bellows kind) can be computed using the Thin Joint module of the program, which is based on ASME appendix 26. The spring rate of the thick walled expansion joint (flanged/flued kind) can be computed within the tubesheet modules when the user specifies the expansion joint design option as Analyze, and enters the expansion joint geometry. This calculation is per TEMA RCB-8. Alternatively, the user can also use the Thick joint module to compute the spring rate, but this is not a preferred way as it involves manual transfer of data between the tubesheet and Thick joint modules. The uncorroded and corroded spring rates will be used for running the multiple load cases in uncorroded and corroded condition.
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TEMA Tubesheets Expansion Joint Inside Diameter - Enter the inside diameter of the expansion joint, shown as ID in the figure below. This value is used by the program to calculate the force on the cylinder and the equivalent pressure of thermal expansion.
Figure 38: Expansion Joint
Expansion Joint Outside Diameter - Enter the outside diameter of the expansion joint, shown as OD in Figure D in Expansion Joint Inside Diameter. Expansion Joint Flange Wall Thickness, (te) - Enter the minimum thickness of the flange or web of the expansion joint, after forming. This is usually thinner than the unformed metal. This value is shown as te in Expansion Joint Inside Diameter. Expansion Joint Flange Corrosion Allowance - Enter the corrosion allowance for the expansion joint. This value will be subtracted from the minimum thickness of the flange or web for the joint. Some common corrosion allowances are listed below: 0.0625 inches (2 mm)
1/16"
0.125 inches (3 mm)
1/8"
0.25 inches (6 mm)
1/4"
Expansion Joint Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Expansion Joint Knuckle Offset Inside - Enter the distance from the shell cylinder to the beginning of the knuckle for an expansion joint with an inside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. In both cases this distance is frequently zero and, for an expansion joint with an outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint.
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TEMA Tubesheets Expansion Joint Knuckle Offset Outset - Enter the distance from the outer cylinder to the beginning of the knuckle for an expansion joint with an outside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. In both cases this distance is frequently zero, and, for an expansion joint with an outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint. Expansion Joint Knuckle Radius Inside - Enter the knuckle radius for an expansion joint with an inside knuckle. Enter zero for an expansion joint with a sharp inside corner. Expansion Joint Knuckle Radius Outside - Enter the knuckle radius for an expansion joint with an outside knuckle. Enter zero for an expansion joint with a sharp outside corner (Flanged Only). Number of Flexible Shell Elements (1 Confolution = 2 Fse) - Enter the number of flexible shell elements in the flanged/flued expansion joint. Two flexible shell elements constitute one convolution of the expansion joint.
Figure 39: Shell Side Geometry
Shell Cylinder Length (Li) - Enter the length of the shell cylinder to the nearest body flange or head. TEMA Paragraph RCB 8-21 includes the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if it is less than the cylinder length. See the figure in Expansion Joint Inside Diameter. Is there an outer cylinder? - Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolute (1 FSE). It may also be true when there is a relatively long cylindrical portion between two half convolutes, as in the case of certain inlet nozzle geometries for heat exchangers.
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TEMA Tubesheets See the figure in Expansion Joint Inside Diameter. Click to open the Outer Cylinder Dialog Box (on page 171, on page 208) and define more properties. Desired Cycle life - Enter the number of desired pressure cycles for this exchanger. This will be compared with the actual computed cycle life of the expansion joint. Print Detailed Expansion Joint Calculations? - Select this option to print the detailed expansion.
Tubesheet Extended as Flange Dialog (TEMA Tubesheets) Outside Diameter of Flanged Portion - Enter the outer diameter of the flange. This value is referred to as "A" in the ASME code. Thickness of Extended Portion of Tubesheet - Enter the flange thickness. This thickness will be used in the calculation of the required thickness. The final results should therefore, agree with this thickness to within about five percent. Since the ASME Code does not have a single equation to compute this required thickness, the appropriate formula from TEMA 8th edition was used. Bolt Circle Diameter - Enter the diameter of the bolt circle of the flange.
Thread Series - The following bolt thread series tables are available: TEMA Bolt Table UNC Bolt Table User specified root area of a single bolt TEMA Metric Bolt Table British, BS 3643 Metric Bolt Table Irrespective of the table used, the values will be converted back to the user selected units. TEMA threads are National Coarse series below 1 inch and 8 pitch thread series for 1 inch and above bolt nominal diameter. The UNC threads available are the standard threads. Select Bolt Size - Select the bolt size.
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TEMA Tubesheets Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. This value will be used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the Root Area cell. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this field. This option is used only if bolt root area is greater than 0.0. Number of Bolts - Enter the number of bolts to be used in the flange analysis. This is usually an even number. The number of bolts is almost always a multiple of four. Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Fillet Weld Between Flange and Shell/Channel - Enter the fillet weld height between the tubesheet flange and the shell or channel outside surface. CodeCalc will use this number to calculate g1 (hub thickness at the large end). Is the Bolt Load transferred to the Tubesheet - Check this box if the bolt load is transferred to the tubesheet, which is extended as the flange. If the tubesheet is gasketed with both the shell and channel flanges, then tubesheet can still be extended but the bolt load is not transferred to the tubesheet extension. In that case, you can uncheck this box. But, carefully consider all the possible cases such the hydrotest. If this box is unchecked then the required thickness of the tubesheet extension is not computed. Ratio of Required Thickness of Tubesheet Flanged Extension - If it is desired to reduce the required thickness of the tubesheet flanged Extension, then specify the ratio of the Required thicknesses of Tubesheet Flanged Ext. and the Tubesheet. This is used in TEMA RCB 7.1342 for U-tube tubesheet exchangers This is an optional input and this ratio should be less than 1.0 and more than 0.2. The default value is 1.0. Operating Flange Bolt Load (Wm1) - Specify the alternate operating bolt load such as from the mating flange. This value will be used if it is greater than the operating bolt load computed by the program. Seating Flange Bolt Load (Wm2) - Specify the alternate seating flange bolt load such as from the mating flange. This value will be used if it is greater than the seating bolt load computed by the program.
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TEMA Tubesheets Flange Design Bolt Load (W) - Specify the alternate flange design bolt load such as from the mating flange. This value will be used if it is greater than the flange design bolt load computed by the program.
Outer Cylinder Dialog Box Topics
Outer Cylinder on the Thick Expansion Joint ................................ 171 Outer Cylindrical Element Corrosion Allowance ............................ 171 Outer Cylindrical Element Length (Lo) .......................................... 171
Outer Cylinder on the Thick Expansion Joint Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolution (1 FSE). It may also be true when there is a relatively long cylindrical portion between two half convolutions, as in the case of certain inlet nozzle geometries for heat exchangers.
Figure 40: Expansion Joint
Outer Cylindrical Element Corrosion Allowance Enter the corrosion allowance for the outer cylindrical element.
Outer Cylindrical Element Length (Lo) Enter the length of the outer cylinder to the nearest body flange or head, or to the centerline of the convolute. TEMA Paragraph RCB 8-21 includes the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length.
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TEMA Tubesheets This value is shown in the figure below as 'lo'.
Figure 41: Expansion Joint
Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Shell Band Properties Dialog Box Topics
Shell Thickness Adjacent to Tubesheet ........................................ 173 Shell Band Corrosion Allowance ................................................... 173 Length of Shell Thickness Adjacent to Tubesheet, front end L1 ... 173 Length of Shell Thickness Adjacent to Tubesheet, rear L1 ........... 173
Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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TEMA Tubesheets
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Shell Thickness Adjacent to Tubesheet Enter the thickness of the shell bands ts1.
Shell Band Corrosion Allowance Enter the corrosion allowance for the shell band.
Length of Shell Thickness Adjacent to Tubesheet, front end L1 Enter the front end length l1 for the shell band.
Length of Shell Thickness Adjacent to Tubesheet, rear L1 Enter the rear end length l1' for the shell band.
Multiple Load Cases Dialog Box (TEMA Tubesheets) Shell-side Vacuum Pressure - When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example for full atmospheric vacuum condition enter a value of 15.0 psig. If no value is specified, then zero psi will be used. Channel-side Vacuum Pressure - When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example for full atmospheric vacuum condition enter a value of 15.0 psig. If no value is specified, then zero psi will be used.
Tubesheet Gasket Dialog Box Flange Face Inner Diameter - Enter the inner diameter of the flange face. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. If there is no raise flange face, please enter the gasket ID. See Flange Face Figure (on page 143). Flange Face Outer Diameter - Enter the outer diameter of the flange face. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. If there is no raise flange face, please enter gasket OD. See Flange Face Figure (on page 143).
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TEMA Tubesheets Gasket Inner Diameter - Enter the inner diameter of the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. See Flange Face Figure (on page 143). Gasket Outer Diameter - Enter the outer diameter of the gasket. The soaftware uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. See Flange Face Figure (on page 143). Mating Flange Hub Thickness, Small End - Enter the flange hub thickness. Mating Flange Hub Thickness, Large End - Enter the flange hub thickness. Gasket Factors m/y - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Flange Face Facing Sketch - Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: Facing Sketch
Description
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Flange Face Facing Column - Enter the partition gasket column for gasket seating. These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbing Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Full Face Gasket Option - ASME Sec. VIII Div. 1 does not cover the design of flanges for which the gasket extends beyond the bolt circle diameter. Select this option to use a typical method for the design of these types of flanges is from the Taylor Forge Flange Design Bulletin. Gaskets for the full face flanges are usually of soft materials such as rubber or an elastomer, so that the bolt stresses do not go too high during gasket seating. The software adjusts the flange
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TEMA Tubesheets analysis and the design formulae to account for the full face gasket. There are 3 Full Face Gasket Flanges options: Program Selects - Select to automatically make the determination if this is a full face gasket flange, depending upon the input. If the gasket ID and OD matches with Flange ID and OD dimensions respectively (except for a blind flange) then it is determined to be a full face flange. See the figure below.
Full Face Gasket - Select if this is a full face gasket flange. Use this option when the gasket ID or OD does not match the flange ID/OD dimensions, but the gasket extends beyond the bolt circle diameter. See the figure below:
Not a Full Face - Select if this is not a full face gasket flange. Length of Partition Gasket - This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. Width of Partition Gasket - Enter the width of the pass partition gasket. Using the gasket properties specified and the known width, CodeCalc will compute the effective seating width and compute the gasket loads contributed by the partition gasket.
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TEMA Tubesheets
Fixed Tubesheet Exchanger Dialog Box Tubesheet Mean Metal Temperature - Enter the actual metal temperature for the tubesheet under a realistic operating condition. This value does not affect the thermal expansion design, but it is used to determine the elastic modulus of the tubesheet. Refer to TEMA standard, section T-4 (8th Ed.) for guidance to compute the Mean Metal Temperatures. Is This a Kettle Type Tubesheet - Check this option if the shell is shaped like a Kettle. Kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in TEMA standard Eighth Edition. Run Multiple Load Cases for Fixed Tubesheet - Check this box if you want to run multiple load cases for the tubesheet design, per the TEMA standard. Load Case #
Corroded
Uncorroded
1
Fvs + Pt - Th + Ca
Fvs + Pt - Th - Ca
2
Ps + Fvt - Th + Ca
Ps + Fvt - Th - Ca
3
Ps + Pt - Th + Ca
Ps + Pt - Th - Ca
4
Fvs + Fvt + Th + Ca
Fvs + Fvt + Th - Ca
5
Fvs + Pt + Th + Ca
Fvs + Pt + Th - Ca
6
Ps + Fvt + Th + Ca
Ps + Fvt + Th - Ca
7
Ps + Pt + Th + Ca
Ps + Pt + Th - Ca
8
Fvs + Fvt - Th + Ca
Fvs + Fvt - Th - Ca
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Load Case Description
Fvt, Fvs - User-defined Shell-side and Tube-side vacuum pressures or 0.0 Ps, Pt - Shell-side and Tube-side Design Pressures Th - With or Without Thermal Expansion Ca - With or Without Corrosion Allowance
CodeCalc User's Guide
TEMA Tubesheets
Kettle Tubesheet Dialog Box Port Cylinder Length - Enter the length of the Kettle port cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Port Cylinder Thickness - Enter the thickness of the Kettle port cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Mean Diameter of Port Cylinder - Enter the mean diameter of the kettle port cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Kettle Cylinder Length - Enter the length of the kettle cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Kettle Cylinder Thickness - Enter the thickness of the kettle cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Mean Diameter of Kettle Cylinder - Enter the mean diameter of the Kettle cylinder. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Axial Length of Kettle Cone - Enter the axial length of the Kettle cone. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition). Kettle Cone Thickness - Enter the thickness of the Kettle cone. This dimension is needed if the shell is shaped like a Kettle. The Kettle-type configuration is illustrated in Figures N-1.2 and N-2 in the TEMA Standard (Eighth Edition).
Results (Tubesheets) Intermediate Calculations for Tubesheets Extended as Flange: Two major additions to the tubesheet calculations occur when a tubesheet is extended as a flange. First, a moment is added to the pressure moment, which governs the thickness of most tubesheets. Second, a moment exists on the portion of the tubesheet, which serves as the flange, and the effects of this moment must be evaluated. The TEMA standard requires that these conditions be evaluated using the rules in the ASME Code, Appendix 2. Those rules, in turn, require the complete evaluation of bending moments on the flange. It is those bending moment calculations, which are reflected in this section of the output. The flange design rules in PD:5500 are also very similar to the ASME Appendix 2 rules. These calculations represent the basic bolt loading for the flanged portion of the tubesheet, and will be the same for the mating flange. The actual bending moments may change when compared to the mating flange. The flanged extension of the tubesheet is calculated as a ring type flange. Since no stresses are shown, you need to check the adequacy of the bolting by comparing the required bolt area to the actual bolt area. The bolt spacing correction factor is automatically included in the bending moment, such that the moment is the force times the distance times the bolt correction.
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TEMA Tubesheets Geometric Constants, Pressure and Thickness Calculations: The tube diameter, pitch, and pattern are used to calculate the term 'eta' in the tubesheet thickness equation. These rules are same for triangular, rotated triangular, square, and rotated square layouts. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. You will receive an error message when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. The G dimension is calculated based on the exchanger type and either the diameter of the pressure component or the mean diameter of the gasket. TEMA standard states that for all the floating tubesheet (except divided), the G shall be the G used for the stationary tubesheet. The T type floating tubesheet should also be checked with actual gasket G of the floating tubesheet. In these cases, user can enter the G dimension of the stationary tubesheet. Similarly, the F dimension is calculated based on the exchanger type and the type of connection to the shell and channel. These calculations are based on Table RCB-7.132 and Table RCB-7.133.
Differential Expansion Pressure: The program contains tables of Young's modulus and the coefficient of thermal expansion. It selects these values from the tables based on the materials classification you enter on the material editing screen of the input spreadsheet. You should verify that the program has selected the right identification number for the material. You should also check the values to ensure that they agree with your expectations. A good place to find this data, and the source of these tables in the program, is the TEMA Standard, tables D-10 and D-11. The following table displays the program identification numbers for the materials in this standard:
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Chart Number
Cross Ref. to Elastic Chart
Chart Name
1
3
TE-1 : Carbon and Low Alloy Steels
2
4
B31.3 : 5Cr - 9Cr
3
6
B31.3 : 18Cr - 8Ni
4
6
TE-1 : 27Cr
5
6
B31.3 : 25Cr20Ni
6
8
B31.3 : 67Ni30Cu
7
1
B31.3 : 3.5Ni
8
10
B31.3 : Aluminum
9
7
B31.3 : Cast Iron
10
13
B31.3 : Bronze
11
12
B31.3 : Brass
12
9
B31.3 : 70 Cu - 30Ni
13
6
B31.3 : Ni - Fe - Cr
14
6
B31.3 : Ni - Cr - Fe
15
7
B31.3 : Ductile Iron
CodeCalc User's Guide
TEMA Tubesheets Chart Number
Cross Ref. to Elastic Chart
Chart Name
16
14
TEMA : Plain Carbon Stl & C - Mn Stl.
17
14
TEMA : C - Si, C - 1/2Mo & Cr - 1/2Mo
18
14
TEMA : C - Mn - Si, 1-1/4Cr - 1/2Mo & 3Cr 1Mo
19
14
TEMA : Mn - Mo
20
20
TEMA : 2 - 1/2 & 3 - 1/2Ni
21
17
TEMA : 2 - 1/4Cr - 1Mo
22
18
TEMA : 5Cr - 1/2Mo
23
18
TEMA : 7Cr - 1/2Mo & 9Cr - 1Mo
24
19
TEMA : 12Cr & 13Cr
25
19
TEMA : 15Cr & 17 Cr
26
15
TEMA : TP316 & TP317
27
15
TEMA : TP304
28
15
TEMA : TP321
29
15
TEMA : TP347
30
15
TEMA : 25 Cr-12Ni, 23 Cr-12Ni, 25Cr-20Ni
31
23
TEMA : Aluminum 3003
32
23
TEMA : Aluminum 6061
33
32
TEMA : Titanium, Grades 1, 2, 3, 7
34
21
TEMA : Ni-Cu (Alloy 400)
35
24
TEMA : Ni - Cr - Cr - Fe (Alloy 600)
36
25
TEMA : Ni - Fe - Cr (Alloy 800 & 800H)
37
35
TEMA : Ni - Fe - Cr - Mo - Cu (Alloy 825)
38
34
TEMA : Ni - Mo (Alloy B)
39
27
TEMA : Ni - Mo-Cr (Alloy 276)
40
28
TEMA : Nickel (Alloy 200)
41
33
TEMA : 70-30 Cu - Ni
42
22
TEMA : 90 - 10 & 80 - 20 Cu - Ni
43
29
44
30
TEMA : Brass
45
29
TEMA : Aluminum Bronze
46
29
TEMA : Copper - Silicon
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TEMA : Copper
179
TEMA Tubesheets Chart Number
Cross Ref. to Elastic Chart
Chart Name
47
31
TEMA : Admiralty
48
37
TEMA : Zirconium
49
15
TEMA : Cr - Ni - Fe - Mo - Cu - Cb (Alloy 20Cb)
50
38
TEMA : Ni - Cr -Mo - Cb (Alloy 625)
51
39
TEMA : Tantalum
52
40
TEMA : Tantalum with 2.5% Tungsten
53
43
TEMA : 17 - 19 CR ( TP 439 )
54
44
TEMA : AL-6XN
55
47
TEMA : 2205 (S311803)
56
48
TEMA : 3RE60 (S31500)
57
41
TEMA : 7 MO (S32900)
58
42
TEMA : 7 MO PLUS (S32950)
59
45
TEMA : AL 29-4-2
60
46
TEMA : SEA-CURE
61
16
TEMA : C-Si, C-1/2 Mo & Cr- 1/2Mo
62
16
TEMA : C-Mn-Si, 1-1/4Cr-1/2Mo & 3 CR 1Mo
63
17
TEMA : C-Mn-Si 1-1/4Cr-1/2Mo & 3 CR 1Mo
When PD:5500 is selected, then the material band is mapped to nearest TEMA number, which is then used to look up the Young's modulus and the coefficient of thermal expansion. This is necessary since 5500 does not provide tables of thermal expansion versus temperature. When a fixed tubesheet is analyzed, the program calculates the following information: 1. The minimum tubesheet thickness per RCB-7.131. 2. The values G, F, and ETA per RCB-7.132 and RCB-7.133 3. The equivalent differential expansion pressure per RCB-7.161 4. The equivalent bolting pressure per RCB-7.162 5. The effective shell side design pressure per RCB-7.163 6. The effective tube side design pressure per RCB-7.164 7. The required thickness per RCB-7.132 or RCB-7.133 8. The shell longitudinal stress per RCB-7.22 9. The tube longitudinal stress per RCB-7.23 10. The allowable tube compressive stress per RCB-7.24 11. The tube to tubesheet joint loads per RCB-7.25 If the tube or shell longitudinal stresses are being exceeded, it can be caused by the differential thermal expansion between the tubes and the shell. For example, when a tube is under
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TEMA Tubesheets compressive stress and the shell is under tensile stress, this indicates that the tube is trying to expand more than the shell. In this case an expansion joint can be used to relieve this axial stress. You can either put a thin expansion joint by checking the appropriate box (designed using the Thin Joint module) or a thick expansion joint (which can be designed the Tubesheet module or the Thick Joint module).
Display of Results on Status Bar As the user enters the data, program performs the calculation and displays the important results on the status bar. Any error messages are also displayed. This allows a quick design of the tubesheet and makes it easier to try various configurations to select the best one. Any failures are indicated in red. Here is a sample:
Designing a Thick Expansion Joint in the Tubesheet Module: After you input the thick expansion joint geometry in the Tubesheet module, the program uses the following process to design the expansion joint: 1. Compute the expansion joint spring rate 2. Use the expansion joint spring rate in the fixed tubesheet calculations 3. Use the results of the tubesheet calculation, along with the prime pressures (P’s, P’t, Pd) to compute the expansion joint stresses. 4. Run a corresponding expansion joint calculation for each tubesheet load case. The program displays the results for the worst case. (detailed results are also available). The procedure followed when designing PD:5500 tubesheets is similar to the one shown here.
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TEMA Tubesheets
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SECTION 10
ASME Tubesheets Home tab: Components > Add New ASME Tubesheet Calculates the required thickness for tubesheets and shell/channel/tube stresses according to the ASME Code Section VIII Division 1 part UHX, 2007 Edition. Tubesheet types that are addressed are U-tube, fully fixed and floating. CodeCalc also computes the allowable Tube-Tubesheet joint load per ASME Sec. VIII Appendix A. Flanged and flued (thick) expansion joint for a fixed tubesheet is also analyzed per TEMA standard, 8th edition and ASME Sec. VIII Div. 1 Appendix 5.
In This Section
Purpose, Scope, and Technical Basis ........................................... 183 Shell Tab ........................................................................................ 185 Channel Tab .................................................................................. 186 Tubes Tab ...................................................................................... 187 Tubesheet Tab ............................................................................... 192 Expansion Joint Tab ...................................................................... 205 Tubesheet Extended As Flange Dialog Box .................................. 209 Additional Input U-tube Tubesheets Dialog Box ............................ 209 Results (ASME Tubesheets) ......................................................... 211
Purpose, Scope, and Technical Basis The ASME TUBESHEETS module is based on the ASME Code Section VIII Division 1 part UHX. This module will also compute loads on the tubes and compare them to their allowable loads per the appropriate equation in Appendix A. Gasketed geometries for both fixed, floating and U-tube exchangers are also analyzed as well as the thickness of the flanged extension (the TEMA equation has been used). This module is good for both square or rectangular tube patterns. When this module is executed it will display the output including equations for a given input. Afterwards, CodeCalc will iterate for the required thickness of the tubesheet. The shell side and tubeside corrosion allowances will then be added to these final results. CodeCalc also performs the plasticity calculations for fixed tubesheets if high discontinuity stresses exist at the attachment between the tubesheet and shell or channel. CodeCalc contains all of the graphs and functions that appear in section UHX. The software analyzes all the load cases as per the section UHX, which includes various combinations of pressure and temperature, in both the uncorroded and corroded (if specified) conditions. A summary table is provided at the end of the output. User can choose to view the detailed printout of any load case.
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ASME Tubesheets The software can also analyze a thick expansion joint attached to a fixed tubesheet. The expansion joint spring rate and stresses are computed per TEMA standard. The actual stresses are then compared with the allowables provided in ASME Sec. VIII Div. 1, Appendix 5 to check the joint's adequacy.
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ASME Tubesheets
Shell Tab Item Number - Type an ID number for the tubesheet. This might be the item number on the drawing, or numbers that start at 1 and increase sequentially. More than one pressure or temperature case can be run. Press the + key, enter a new tubesheet number and change the relevant input items. Merge Shell - Use this option to import data from the Shells and Heads module. Select the shell you want to add to the model, and press enter, all the appropriate data for that shell is copied in automatically. Description - Type an alphanumeric description for this item. This entry is optional. Entering a description will help you keep up with each item when reviewing the output. Shell Design Pressure - Type the design pressure for the shell side of the exchanger. If the shell side has external pressure, enter a negative pressure. The program will add this pressure with the positive pressure on the tube (channel) side. Merge TEMA Tubesheets - Select to merge the TEMA tubesheets. Shell Wall Thickness - Type the minimum wall thickness for the shell of the exchanger. The program uses this value to calculate the characteristic diameter for all tubesheets. It is used in the computation of Beta as well as the spring rate and other factors. Shell Corrosion Allowance - Type the shell side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the shell. Shell Inside Diameter - Enter the inside diameter for the shell of the exchanger. This value is used by the software to calculate the characteristic diameter for all tubesheets and the longitudinal shell stresses for fixed tubesheet exchangers. Shell Design Temperature - Enter the design metal temperature for the shell. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Shell Circumferential Joint Efficiency, Esw - Enter the joint efficiency of the circumferential joint in the shell. This is used in the calculation of the allowable for the shell axial stress in the case of fixed tubesheet exchangers.
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ASME Tubesheets
Channel Tab Channel Type - Select Cylinder, Hemispherical head, or Floating Head as the channel type. Merge - Use this option to import data from the Shells and Heads module. Select the shell you want to add to the model, and press enter, all the appropriate data for that shell is copied in automatically. Channel Design Pressure - Enter the design pressure for the tube side of the exchanger. If the tube side has a vacuum design condition, enter a negative pressure. The software correctly combines this pressure with the positive pressure on the other side. For TEMA tubesheet calculation: If you specify a differential pressure in the differential pressure input field, the values on the shellside and tubeside will usually be ignored. The exception to this is fixed tubesheet exchangers, where the differential pressure field only serves as a flag to indicate to the program that the appropriate calculations for differential pressure should be performed. For ASME tubesheet calculation: To run a differential pressure case, click Use Differential Pressure Design in the Multiple Load Case dialog box. Channel Wall Thickness - Type the minimum wall thickness for the channel of the exchanger. The program uses this value to calculate the characteristic diameter for all tubesheet types. An example of such a parameter is the Beta dimension for fixed tubesheet exchangers. Channel Corrosion Allowance - Enter the tube side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the channel. Channel Inside Diameter - Enter the inside diameter for the channel of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets. Channel Design Temperature - Enter the design metal temperature for the tubesheet. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Channel Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
186
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
CodeCalc User's Guide
ASME Tubesheets
Tubes Tab Tube Design Temperature - Enter the design temperature of the tubes. This value will be used to look up the allowable stress values for the tube material from the material tables. Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Wall Thickness - Enter the wall thickness of the tubes. This value is used to determine the total tube area and stiffness. The following table displays thicknesses for some common tube gauges:
B.W.G. Gauge
Thickness (Inches)
B.W.G. Gauge
Thickness (Inches)
7
.180
17
.058
8
.165
18
.049
10
.134
19
.042
11
.109
22
.028
13
.095
24
.022
14
.083
26
.018
15
.072
27
.016
16
.065
Corrosion Allowance - Enter the tube corrosion allowance. Number of Holes - Enter the number of tube holes in the tubesheet. This value is used to determine the total tube area and stiffness. For U-tube exchangers, the number of tube holes in the tubesheet is normally equal to two times the number of tubes. Pattern - Enter the pattern of the tube layout. The tube diameter, pitch, and pattern are used to calculate the term 'eta' in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. In the ASME code square patterns have a 90º layout angle and triangular patterns have a 60º angle. Outside Diameter - Enter the outside diameter of the tubes. This is usually an exact fraction, such as .5, .75, .875, 1.0, or 1.25 (inches). The tube diameter, pitch, and pattern are used to
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ASME Tubesheets calculate the term 'eta' in the tubesheet thickness equation. These rules are the same for triangular, square, rotated triangular and rotated square layouts. Pitch - Enter the tube pitch, the distance between the tube centers. The tube diameter, pitch, and pattern are used to calculate the term "eta" in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Does this Tube have a Longitudinal Weld? - Click this box if you are using a welded tube (longitudinal seam) and not a seamless one. When selecting the tube material you can encounter allowables in two forms: Material specification is for the welded material - The material allowable in this case includes a weld Joint Efficiency of 0.85. When checking the longitudinal tube stress as in part UHX the tube allowable without the Joint efficiency is used. To calculate the pressure stress (hoop stress) the allowable including the joint efficiency is used. Material specification is for the Seamless or Seamless/Welded material - In this case the Joint efficiency is not applied to the allowables listed in the code. Hence the part UHX uses tube allowables as it is, while the pressure calculation applies the efficiency of 0.85. Refer to the notes for the material specification. Tube to Tubesheet Joint Information - Check this box to input information about the Tube-Tubesheet joint (weld, classification). This information will be used to determine the minimum acceptable fillet/groove weld size that connects the tube to the tubesheet and the allowable tube-to-tubesheet load. Radius to Outermost Tube Hole Center - Enter the distance from the centerline of the exchanger to the centerline of the outermost tube. Distance between Innermost Tube Centers (UL) - The ASME defines this input also as the largest center-to-center distance between adjacent tube rows. This could also be the width of the pass partition lane. This is not the tube pitch. If there are not pass partitions, then this value must be 0.0. Length of Expanded Portion of Tube - The expanded portion of a tube is that part which is radially expanded outward within the tube hole. When the tube is expanded, it is also pressed into the tubesheet. Some tubes are welded into place and this value may be zero. The maximum this value can be is the thickness of the tubesheet. A fully expanded tube-tubesheet joint can reduce the tubesheet-required thickness. Pass Partition Groove Depth (hg) - Enter the tube side pass partition groove depth. Perimeter of Tube Layout (if needed) - Enter the length of a path around the outside edge of the tube layout. This can be calculated by counting the number of tubes on the outside of the layout and multiplying that number by the tube pitch. When a tubesheet might be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. An error message displays when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. This input is only needed for TEMA tubesheets. Area of Tube Layout (if needed) - Enter the area enclosed by a path around the outside edge of the tube layout. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. An error message displays when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. Straight Length of Tubes - Enter the length of the tubes. For U-tubesheet exchangers this is the straight length of the tube. For fixed tubesheet exchanger this is the overall length from the inside face of one tubesheet to the inside face of the other tubesheet. This value is used to
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ASME Tubesheets determine the thermal expansion of the tubes. This input is only needed for British tubesheets and TEMA fixed tubesheets. You can specify the tube length from either the inner tubesheet faces or outside tubesheet faces (total straight length). This is indicated using the corresponding input on this screen. Straight Tube Length measured between - Specify the tube length from either the inner tubesheet faces or outside tubesheet faces (total straight length), this is indicated using the corresponding input on this screen. End Condition k - For computing the allowable tube compression, the values of k and SL are required. Where, SL = Unsupported Span of the tube k = Tube end condition corresponding to the span SL. The table below lists the values of k. k
Condition
0.60
For unsupported spans between two tubesheets.
0.80
For unsupported spans between a tubesheet and a tube support.
1.0
For unsupported spans between two tube supports.
For the worst case scenario, enter the values of k and SL that give the maximum combination of k * SL. SL for example, could be the distance between the tubesheet and the first baffle or the tube span between two support baffles. F1 calls different IDs in the two books, but content is the same. Maximum Unsupported Length SL - For computing the allowable tube compression, the values of k and SL are required. Where, SL = Unsupported Span of the tube k = Tube end condition corresponding to the span SL. The table below lists the values of k. k
Condition
0.60
For unsupported spans between two tubesheets.
0.80
For unsupported spans between a tubesheet and a tube support.
1.0
For unsupported spans between two tube supports.
For the worst case scenario, enter the values of k and SL that give the maximum combination of k * SL. SL for example, could be the distance between the tubesheet and the first baffle or the tube span between two support baffles. F1 calls different IDs in the two books, but content is the same.
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ASME Tubesheets
Tube to Tubesheet Joint Input Dialog Box Fillet Weld Length, af - If the tubes on your exchanger are welded to the tubesheet, then enter the fillet weld or groove weld leg length. Some designs incorporate either only a groove or fillet weld. Sometimes both are used. These values are used to determine the weld strengths and the required weld sizes. Refer to paragraph UW-20 in the ASME Code for more details. Groove Weld Length, ag - If the tubes on your exchanger are welded to the tubesheet, then enter the fillet weld or groove weld leg length. Some designs incorporate either only a groove or fillet weld. Sometimes both are used. These values are used to determine the weld strengths and the required weld sizes. Refer to paragraph UW-20 in the ASME Code for more details. Tube Joint Strength Type - Following options are available for the connecting tube/tubesheet welds: Full Strength
A full strength tube-to-tubesheet weld is one in which the design strength is equal to or greater than the maximum allowable axial tube strength. In other words the joint is at least as strong as the tube.
Partial Strength
A partial strength weld can be designed based on the actual tube-tubesheet axial load
Seal Weld/No Weld
No calculations are performed in this case.
Information on these weld types can be found in the ASME Code Section VIII Division 1 paragraph UW-20. Design Strength (Fd) (not needed for fixed tubesheet) - The term Fd is defined in the Code paragraph UW-20. The design strength should not be greater than Ft (tube strength), which is p*t(do - t)Sa. This value is used to determine the minimum acceptable fillet/groove weld size that connects the tube to the tubesheet. This value is required for U-tube tubesheet exchanger. It is optional for fixed and floating tubesheet exchangers. For partial strength tube-to-tubesheet welds on fixed/floating tubesheet exchangers, the higher of the actual tube-to-tubesheet load and the user entered design strength will be used to size welds. For full strength tube-to-tubesheet welds on fixed/floating tubesheet exchangers, tube strength (Ft) is used to size welds. Method for Tube-Tubesheet Joint Allowance Load - The following methods are available: ASME Sec. VIII Div. I App. A
This method is available for fixed and floating tubesheet heat exchangers. It covers many types of tube-tubesheet joints, such as welded, brazed and expanded.
ASME Sec. VIII Div. I UW-20
This method provides rules for computation of allowable loads for Full strength and Partial strength Tube-Tubesheet welds.
Tube-Tubesheet Joint Type - On selecting the appropriate Tube joint type, the program automatically fills in the value of factor Fr.
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ASME Tubesheets The ASME Code tube joint reliability factor is found in the ASME Code, Section VIII, Division 1, Table A-2, and is used to calculate the allowable tube-to-tubesheet joint loads. A typical value for tubes rolled into two grooves is 0.70. Enter a value between 1 and 11 based on the following table from the ASME VIII appendix A table A-2. Type
Joint Description
Fr.(test)
Fr.(no test)
1
a
Welded only, a ≥ 1.4t
1.00
.80
2
b
Welded only t ≤ a < 1.4t
.70
.55
3
b-1
Welded only a < t
.70
..
4
c
Brazed examined
1.00
.80
5
d
Brazed not fully examined
0.50
.40
6
e
Welded a ≥ 1.4t, exp.
1.00
.80
7
f
Welded a < 1.4t, exp, 2 grooves
.95
.75
8
g
Welded a < 1.4t, exp, 1 grooves
.85
.65
9
h
Welded a < 1.4t, exp, 0 grooves
.70
.50
10
i
Expanded, enhanced with 2 or more grooves
.90
.70
11
j
Expanded, enhanced with single groove
.80
.65
12
j
Expanded, not enhanced (no grooves)
.60
.50
Is Tube-TubeSheet Joint Tested - Check this box if the Tube-Tubesheet joint is tested. In that case the program will use the higher value of factor fr from the table A-2 in ASME code, Sec VIII, Div 1. ASME Tube Joint-Reliability Factor (table A-2) - Enter a value between .40 and 1.0 based on the following table from ASME VIII appendix A table A-2. This is needed when the tube connection class is not specified above. Type
Joint Description
Fr.(test)
Fr.(no test)
1
a
Welded only, a ≥ 1.4t
1.00
.80
2
b
Welded only t ≤ a < 1.4t
.70
.55
3
b-1
Welded only a < t
.70
..
4
c
Brazed examined
1.00
.80
5
d
Brazed not fully examined
0.50
.40
6
e
Welded a ≥ 1.4t, exp.
1.00
.80
7
f
Welded a < 1.4t, exp, 2 grooves
.95
.75
8
g
Welded a < 1.4t, exp, 1 grooves
.85
.65
9
h
Welded a < 1.4t, exp, 0 grooves
.70
.50
10
i
Expanded, enhanced with 2 or more
.90
.70
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ASME Tubesheets grooves 11
j
Expanded, enhanced with single groove
.80
.65
12
j
Expanded, not enhanced (no grooves)
.60
.50
Tube expansion, Po - Enter the Interface pressure (Po) between the tube and the tubesheet that remains after expanding the tube at fabrication. This pressure is usually established analytically or experimentally. But, must consider the effect of change in material strength at operating temperature. This input is required only for the tube joint types i, j and k, as defined in table A-2 in ASME Sec VIII, Div-1 App. A. Differential Thermal Expansion, PT - Enter the Interface pressure (PT) between the tube and the tubesheet due to differential thermal growth. This pressure is usually established analytically or experimentally This input is required only for the tube joint types i, j and k, as defined in table A-2 in ASME Sec VIII, Div-1 App. A.
Tubesheet Tab Type of Tubesheet - Choose the type of tubesheet that you will be analyzing. ASME has four distinct types of tubesheets for analysis purposes. These are Fixed and U Tube, Stationary and Floating tubesheets. A fixed tubesheet exchanger is one that is subject to loads arising from differential thermal expansion between the tubes and the shell. It consists of stationary tubesheets on both sides. A fixed tubesheet exchanger can be further classified into Configurations A, B, C or D. U Tube exchangers can be categorized as integral with the shell, channel, both or gasketed on both sides. Floating tubesheet heat exchangers consist of a stationary tubesheet and a floating tubesheet. Based on the selected tubesheet type, the program will automatically reset other inputs on this dialog, such as tubesheet gasketed with which side or tubesheet integral with which side. Some Tubesheet configurations are illustrated below: Tubesheet is integral with the Shell and is gasketed on the Channel side and is not extending as a flange.
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ASME Tubesheets Tubesheet is integral with the Shell and is gasketed on the Channel side and is extending as a flange.
Tubesheet is gasketed on both the Shell and the Channel sides and is not extended as a flange. In an alternative arrangement the tubesheet is extending as a flange.
Tubesheet is integral with both the Shell and the Channel. This is a fixed tubesheet exchanger; flanged and flued expansion joint is used to reduce the differential thermal expansion between the tubes and the shell.
Stationary and U-Tube Tubesheet Configurations Permitted per ASME Section UHX: a
Tubesheet integral with both the shell and the channel.
b
Tubesheet integral with the shell, gasketed with the channel and extended as a flange.
c
Tubesheet integral with the shell, gasketed with the channel and not extended as a flange.
d
Tubesheet gasketed with both the shell and the channel
e
Tubesheet integral with the channel, gasketed with the shell and extended as a flange.
f
Tubesheet integral with the channel, gasketed with the shell and not extended as a flange.
Floating Tubesheet Configurations Permitted per ASME Section UHX: A
Tubesheet integral
B
Tubesheet gasketed and extended as a flange.
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ASME Tubesheets C
Tubesheet gasketed and not extended as a flange.
D
Tubesheet internally sealed
Fixed Tubesheet Configurations Permitted per ASME Section UHX: a
Tubesheet integral with both the shell and the channel.
b
Tubesheet integral with the shell, gasketed with the channel and extended as a flange.
c
Tubesheet integral with the shell, gasketed with the channel and not extended as a flange.
d
Tubesheet gasketed with both the shell and the channel
Floating Tubesheet Exchanger Type - Choose the floating tubesheet exchanger, the following types are listed in the ASME code: Floating tubesheet exchanger with an immersed Floating head. Stationary tubesheet can be configuration a, b, c, d, e, or f and floating tubesheet can be configuration A, B, or C. Floating tubesheet exchanger with an Externally Sealed Floating head. Stationary tubesheet can be configuration a, b, c, d, e, or f and floating tubesheet is configuration A. Floating tubesheet exchanger with an Internally Sealed Floating head. Stationary tubesheet can be configuration a, b, c, d, e, or f and floating tubesheet is configuration D.
Stationary Tubesheet configurations allowed Per ASME section UHX: a - Tubesheet integral with both Shell and Channel b - Tubesheet integral with Shell, gasketed with Channel, with Tubesheet extended as a Flange c - Tubesheet integral with Shell, gasketed with Channel, with Tubesheet not extended as a Flange d - Tubesheet gasketed with both Shell and Channel e - Tubesheet integral with Channel, gasketed with Shell, with Tubesheet extended as a Flange f - Tubesheet integral with Channel, gasketed with Shell, with Tubesheet not extended as a Flange.
Floating Tubesheets configurations allowed Per ASME section UHX: A - Tubesheet integral B - Tubesheet gasketed and extended as a Flange C - Tubesheet gasketed and not extended as a Flange D - Tubesheet Internally Sealed. Tubesheet Metal Design Temperature - Enter the design metal temperature for the tubesheet. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties.
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ASME Tubesheets 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Tubesheet Thickness - Enter the thickness of the tubesheet, or a reasonable estimate at the thickness if the actual thickness is unknown. This thickness should include any allowances for corrosion on the shell side or the tube side. The tubesheet thickness for fixed tubesheet exchangers is also used in the equivalent thermal pressure calculation. When you have finished your design you should come back and put the actual thickness into this field and make sure the required thickness does not change. Tubesheet Corrosion Allowance (Shell Side) - Enter the tubesheet corrosion allowance for the shell side. This value is combined with the tubesheet corrosion allowance channel side to calculate the corroded thickness of the tubesheet. Tubesheet Corrosion Allowance (Channel Side) - Enter the tubesheet corrosion allowance for the channel side. This value is combined with the tubesheet corrosion allowance shell side to calculate the corroded thickness of the tubesheet. Outside Diameter of Tubesheet - Enter the outside diameter of the tubesheet. This value is referred to as "A" in the ASME code. For the tubesheet extended as a flange, this will be the diameter of the extended portion of the tubesheet. Tubesheet Gasket - Enter the kind of gasketing associated with this tubesheet. Select None if the tubesheet is not sealed with a gasket on either side. Select Shell if the gasket is only on the shell side of the exchanger. Select Channel if the gasket is only on the channel side of the exchanger. Select Both if the gaskets are on both sides of the exchanger. The program will then evaluate the gasket you specify along with the pressure which causes the largest bending moment on the tubesheet. If the tubesheet has a circular gasket, even if the gasket is not extended as a flange, you must enter the details of the gasket, so that the program can correctly evaluate the mean diameter of the gasket load reaction (G). to open the Tubesheet Gasket/Bolting Input Dialog Box and define the necessary Click properties. Tubesheet Integral With - Select the side to which the Tubesheet is integral. Tubesheet Extended as Flange? - Select if the tubesheet is extended and used as a bolted flange. If the tubesheet is extended but does not experience the bending moments of the bolts, then select Is Bolt Load Transferred to Tubesheet to allow input echo of the tubesheet extension information without transferring the bolt load to the tubesheet. For example, when the tubesheet is bolted between a pair of identical flanges, it will not experience a bending moment. It is only when the tubesheet replaces one of the flanges that a moment develops. Dimen. G for Backlog Ring - Area of Untubed Lanes (AL) - This input is used for two types of ASME tubesheet geometries: If the tubesheet has a backing ring, then enter the G1 dimension for the backing ring. G1 is the mid point of the contact between the backing flange and the tubesheet. In this case it is a required input. If the tubesheet is gasketed with both the Shell and the Channel, then enter the channel gasket reaction diameter, Gc, in this input. The program computes the Shell gasket reaction
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ASME Tubesheets diameter, Gs from the gasket/flange properties specified. In this case, this input is optional, required only if Gc is different from Gs. Is Exchange in Creep Range (skip EP, use 35 for SPS)? - Enter the total area of all the untubed lanes on the tubesheet. If there is no pass partition lane then this area is zero. See the figure below for a single pass exchanger, this area is UL1 * Do.
Figure 42: Area of Untubed Lanes
The maximum limiting value of AL is 4*Do*p. Where, Do = Equivalent diameter of outer limit circle. p = tube pitch UL1 = Distance between innermost tube hole centers (width of pass partition lane) Area of Untubed Lanes (AL) - Select this option if the exchanger is inside the creep range as defined in the ASME code.
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Tubesheet Exchanger Dialog Box Shell Metal Temperature at Tubesheet Rim - Enter the actual metal temperature for the shell at the Tubesheet, under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don't forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. Channel Metal Temperature at Tubesheet at Rim - Enter the actual metal temperature for the channel at the Tubesheet, under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don't forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. Tubesheet Metal Temperature at Tubesheet Rim - Enter the actual metal temperature for the tubesheet at the rim, under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don't forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. Modulus of Elasticity - When there is an external pressure value, enter the elastic modulus of the material from Subpart 3 of Section II, Part D at design temperature. Coefficient of Thermal Expansion - The thermal expansion reference number is a value that points to or corresponds to a set of data set forth in ASME Section II Part D, tables TE-1, 2 and so on. Unfortunately, many materials have a composition or UNS number that does not match the criteria of what is supplied in the ASME Code. In these cases, the reference number will be brought in as zero. If this happens, you will need to enter in an appropriate value. Thermal expansion coefficients are important especially if you are analyzing a heat exchanger.
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ASME Tubesheets
Multiple Load Cases Dialog Box Shell-side Vacuum Pressure - When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example for full atmospheric vacuum condition enter a value of 15.0 psig. If no value is specified, then zero psi will be used. Channel-side Vacuum Pressure - When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example for full atmospheric vacuum condition enter a value of 15.0 psig. If no value is specified, then zero psi will be used. Use the Differential Pressure Design - Check this box if design is based on differential pressure case. In this case only certain load cases will be performed, as indicated by the ASME code. Differential Design Pressure (used if >0) - Enter the differential design pressure if you want the program to use the differential design rules. The differential pressure is used as the design pressure on both the tube side and the shell side, except for fixed tubesheet exchangers. In this case any number greater than zero serves as a flag to tell the program to turn on the special differential design pressure rules for fixed tubesheets. You must enter the shell side and tube side design pressures for fixed tubesheet exchangers. Select Load Cases for Detailed Printout - When analyzing the design with the multiple load cases, the program will generate summarized results for all the load cases in tabular form. To see the detailed equations and intermediate calculations for one or more load cases, select those load cases. The following load cases are performed for TEMA fixed tubesheets: Load Case # Load Case Description Corroded
Uncorroded
1
Fvs + Pt - Th + Ca
Fvs + Pt - Th - Ca
2
Ps + Fvt - Th + Ca
Ps + Fvt - Th - Ca
3
Ps + Pt - Th + Ca
Ps + Pt - Th - Ca
4
Fvs + Fvt + Th + Ca
Fvs + Fvt + Th - Ca
5
Fvs + Pt + Th + Ca
Fvs + Pt + Th - Ca
6
Ps + Fvt + Th + Ca
Ps + Fvt + Th - Ca
7
Ps + Pt + Th + Ca
Ps + Pt + Th - Ca
8
Fvs + Fvt - Th + Ca
Fvs + Fvt - Th - Ca
For ASME Tubesheets only certain load cases will be run based on type of the tubesheet and the heat exchanger. These following load cases are performed for ASME fixed and floating tubesheet exchangers: Load Case # Load Case Description
198
Corroded
Uncorroded
1
Fvs + Pt - Th + Ca
Fvs + Pt - Th - Ca
2
Ps + Fvt - Th + Ca
Ps + Fvt - Th - Ca
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Ps + Pt - Th + Ca
Ps + Pt - Th - Ca
4
Fvs + Fvt + Th + Ca
Fvs + Fvt + Th - Ca
5
Fvs + Pt + Th + Ca
Fvs + Pt + Th - Ca
6
Ps + Fvt + Th + Ca
Ps + Fvt + Th - Ca
7
Ps + Pt + Th + Ca
Ps + Pt + Th - Ca
For ASME stationary tubesheet configuration "d" and ASME floating tubesheet configurations "B", "C" and "D", the design is based only on load cases 1, 2 and 3. The following load cases are performed for ASME U-tube tubesheet exchangers. Load Case # Load Case Description Corroded
Uncorroded
Fvs + Pt - Th + Ca
Fvs + Pt - Th - Ca
Ps + Fvt - Th + Ca
Ps + Fvt - Th - Ca
Ps + Pt - Th + Ca
Ps + Pt - Th - Ca
For all ASME exchangers, if vacuum pressures are specified, then an additional load case would be run: 8
Fvs + Fvt - Th + Ca
Fvs + Fvt - Th - Ca
Additionally, if the differential pressure design option is checked, then only certain load cases will be run.
Fvt, Fvs - User-defined Shell-side and Tube-side vacuum pressures or 0.0. Ps, Pt - Shell-side and Tube-side Design Pressures. Th - With or Without Thermal Expansion. Ca - With or Without Corrosion Allowance.
Tubesheet Gasket/Bolting Input Dialog Box Flanged Portion Inner Diameter - Enter the internal diameter of the shell/channel or floating head to which the tubesheet is gasketed. If this value is blank, the software uses either the shell or channel internal diameter, based on the gasketed side the tubesheet. This input is needed for a floating tubesheet exchanger that is gasketed to the floating head. For tubesheets that are gasketed with both the shell and channel, this input is for the shell side. Flanged Portion Outer Diameter - Enter the outer diameter of the flanged portion (shell/channel/floating head) to which the tubesheet is gasketed. If this input is left blank, it is set equal to the tubesheet OD. Specify this input, for cases where flanged portion OD is different from the tubesheet OD. For tubesheets that are gasketed with both the shell and channel, this input is for the shell side. Flange Face Inner Diameter - Enter the inner diameter of the flange face. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket.
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ASME Tubesheets If there is no raise flange face, please enter the gasket ID. See Flange Face Figure (on page 143). Flange Face Outer Diameter - Enter the outer diameter of the flange face. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. If there is no raise flange face, please enter gasket OD. See Flange Face Figure (on page 143). Gasket Inner Diameter - Enter the inner diameter of the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. See Flange Face Figure (on page 143). Gasket Outer Diameter - Enter the outer diameter of the gasket. The soaftware uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. See Flange Face Figure (on page 143). Flange Hub Thickness, Small End - Enter the flange hub thickness. Flange Hub Thickness, Large End - Enter the flange hub thickness. Gasket Factors m - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Gasket Factors y - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Flange Face Facing Sketch - Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: Facing Sketch
Description
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
3
1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Flange Face Facing Column - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings
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ASME Tubesheets Gasket Thickness - Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6. Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Full Face Gasket Option - ASME Sec. VIII Div. 1 does not cover the design of flanges for which the gasket extends beyond the bolt circle diameter. Select this option to use a typical method for the design of these types of flanges is from the Taylor Forge Flange Design Bulletin. Gaskets for the full face flanges are usually of soft materials such as rubber or an elastomer, so that the bolt stresses do not go too high during gasket seating. The software adjusts the flange analysis and the design formulae to account for the full face gasket. There are 3 Full Face Gasket Flanges options: Program Selects - Select to automatically make the determination if this is a full face gasket flange, depending upon the input. If the gasket ID and OD matches with Flange ID and OD dimensions respectively (except for a blind flange) then it is determined to be a full face flange. See the figure below.
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ASME Tubesheets Full Face Gasket - Select if this is a full face gasket flange. Use this option when the gasket ID or OD does not match the flange ID/OD dimensions, but the gasket extends beyond the bolt circle diameter. See the figure below:
Not a Full Face - Select if this is not a full face gasket flange.
Partition Gasket for tubeside (if present) Length - This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. Width - Enter the width of the pass partition gasket. Using the gasket properties specified and the known width, CodeCalc will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Gasket Factors m - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Gasket Factors y - These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Flange Face Facing Sketch - Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations:
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Facing Sketch
Description
1a
flat finish faces
1b
serrated finish faces
1c
raised nubbin-flat finish
1d
raised nubbin-serrated finish
2
1/64 inch nubbin
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1/64 inch nubbin both sides
4
large serrations, one side
5
large serrations, both sides
6
metallic O-ring type gasket
Flange Face Facing Column - Enter the partition gasket column for gasket seating. These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings Gasket Thickness - Enter the thickness of the partition gasket. This value is only required for facing sketches 1c and 1d. Nubbin Width - If applicable, enter the nubbin width for the pass partition gasket. This value is only required for facing sketches 1c, 1d, 2 and 6. Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Thread Series - The following bolt thread series tables are available: TEMA Bolt Table UNC Bolt Table User specified root area of a single bolt TEMA Metric Bolt Table British, BS 3643 Metric Bolt Table Irrespective of the table used, the values will be converted back to the user selected units. TEMA threads are National Coarse series below 1 inch and 8 pitch thread series for 1 inch and above bolt nominal diameter. The UNC threads available are the standard threads. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this field. This option is used only if bolt root area is greater than 0.0. Select Bolt Size - Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. This value will be used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the Root Area cell.
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ASME Tubesheets Bolt Circle Diameter - Enter the diameter of the bolt circle of the flange.
Nominal Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. This value will be used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the Root Area cell. Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Alternate Bolt Loads (used if > calculated values) Operating, WM1 - Specify the alternate operating bolt load such as from the mating flange. This value will be used if it is greater than the operating bolt load computed by the program. Setting, WM2 - Specify the alternate seating flange bolt load such as from the mating flange. This value will be used if it is greater than the seating bolt load computed by the program. Design, W - Specify the alternate flange design bolt load such as from the mating flange. This value will be used if it is greater than the flange design bolt load computed by the program.
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Expansion Joint Tab Expansion Joint Design Option - The following options are available: Existing - Select this option if you already know the spring rate of the flanged/flued expansion joint. Analyze - Select this option if you want the program to compute the spring rate of the expansion joint and stresses induced in the expansion joint. Expansion Joint Calculation Method - Enter the expansion joint calculation method. User Input Spring Rate Corroded - Enter the spring rate for the thin walled (bellows) expansion joint or a thick walled (flanged/flued) expansion joint. If there is no expansion joint, this input should be disabled. The spring rate of the thin walled expansion joint (bellows kind) can be computed using the Thin Joint module of the program, which is based on ASME appendix 26. The spring rate of the thick walled expansion joint (flanged/flued kind) can be computed within the tubesheet modules when the user specifies the expansion joint design option as Analyze, and enters the expansion joint geometry. This calculation is per TEMA RCB-8. Alternatively, the user can also use the Thick joint module to compute the spring rate, but this is not a preferred way as it involves manual transfer of data between the tubesheet and Thick joint modules. The uncorroded and corroded spring rates will be used for running the multiple load cases in uncorroded and corroded condition. User Input Spring Rate Corroded/Uncorroded - Enter the spring rate for the thin walled (bellows) expansion joint or a thick walled (flanged/flued) expansion joint. If there is no expansion joint, this input should be disabled. The spring rate of the thin walled expansion joint (bellows kind) can be computed using the Thin Joint module of the program, which is based on ASME appendix 26. The spring rate of the thick walled expansion joint (flanged/flued kind) can be computed within the tubesheet modules when the user specifies the expansion joint design option as Analyze, and enters the expansion joint geometry. This calculation is per TEMA RCB-8. Alternatively, the user can also use the Thick joint module to compute the spring rate, but this is not a preferred way as it involves manual transfer of data between the tubesheet and Thick joint modules. The uncorroded and corroded spring rates will be used for running the multiple load cases in uncorroded and corroded condition.
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ASME Tubesheets Expansion Joint Inside Diameter - Enter the inside diameter of the expansion joint, shown as ID in the figure below. This value is used by the program to calculate the force on the cylinder and the equivalent pressure of thermal expansion.
Figure 43: Expansion Joint
Expansion Joint Outside Diameter - Enter the outside diameter of the expansion joint, shown as OD in Figure D in Expansion Joint Inside Diameter. Exp. Jt. Flange Wall Thk. (te) - Enter the minimum thickness of the flange or web of the expansion joint, after forming. This is usually thinner than the unformed metal. This value is shown as te in Expansion Joint Inside Diameter. Exp. Jt. Corr. Allw. - Enter the corrosion allowance for the expansion joint. This value will be subtracted from the minimum thickness of the flange or web for the joint. Some common corrosion allowances are listed below: 0.0625 inches (2 mm)
1/16"
0.125 inches (3 mm)
1/8"
0.25 inches (6 mm)
1/4"
Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Expansion Joint Knuckle Offset Inside - Enter the distance from the shell cylinder to the beginning of the knuckle for an expansion joint with an inside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. In both cases this distance is frequently zero and, for an expansion joint with an outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint.
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ASME Tubesheets Expansion Joint Knuckle Offset Outside - Enter the distance from the outer cylinder to the beginning of the knuckle for an expansion joint with an outside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. In both cases this distance is frequently zero, and, for an expansion joint with an outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint. Expansion Joint Knuckle Radius Inside - Enter the knuckle radius for an expansion joint with an inside knuckle. Enter zero for an expansion joint with a sharp inside corner. Expansion Joint Knuckle Radius Outside - Enter the knuckle radius for an expansion joint with an outside knuckle. Enter zero for an expansion joint with a sharp outside corner (Flanged Only). Number of Flexible Shell Elements (1 Convolution = 2Fse) - Enter the number of flexible shell elements in the flanged/flued expansion joint. Two flexible shell elements constitute one convolution of the expansion joint.
Figure 44: Shell Side Geometry
Shell Cylinder Length (Li) - Enter the length of the shell cylinder to the nearest body flange or head. TEMA Paragraph RCB 8-21 includes the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if it is less than the cylinder length. See the figure in Expansion Joint Inside Diameter. Is there an outer cylinder? - Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolute (1 FSE). It may also be true when there is a relatively long cylindrical portion between two half convolutes, as in the case of certain inlet nozzle geometries for heat exchangers.
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ASME Tubesheets See the figure in Expansion Joint Inside Diameter. Click to open the Outer Cylinder Dialog Box (on page 171, on page 208) and define more properties. Desired Cycle life - Enter the number of desired pressure cycles for this exchanger. This will be compared with the actual computed cycle life of the expansion joint. Print Detailed Expansion Joint Calculations? - Select this option to print the detailed expansion. Outer Cylinder on the Thick Expansion Joint - Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolution (1 FSE). It may also be true when there is a relatively long cylindrical portion between two half convolutions, as in the case of certain inlet nozzle geometries for heat exchangers.
Figure 45: Expansion Joint
Outer Cylindrical Element Corrosion Allowance - Enter the corrosion allowance for the outer cylindrical element. Outer Cylindrical Element Length (Lo) - Enter the length of the outer cylinder to the nearest body flange or head, or to the centerline of the convolute. TEMA Paragraph RCB 8-21 includes the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length. This value is shown in the figure below as 'lo'.
Figure 46: Expansion Joint
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ASME Tubesheets Outer Cylindrical Element Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Used to select the data you want to use.
Tubesheet Extended As Flange Dialog Box Thickness of Extended Portion of Tubesheet - Enter the flange thickness. This thickness will be used in the calculation of the required thickness. The final results should therefore, agree with this thickness to within about five percent. Since the ASME Code does not have a single equation to compute this required thickness, the appropriate formula from TEMA 8th edition was used. Is the Bolt Load transferred to the Tubesheet - Check this box if the bolt load is transferred to the tubesheet, which is extended as the flange. If the tubesheet is gasketed with both the shell and channel flanges, then tubesheet can still be extended but the bolt load is not transferred to the tubesheet extension. In that case, you can uncheck this box. But, carefully consider all the possible cases such the hydrotest. If this box is unchecked then the required thickness of the tubesheet extension is not computed.
Additional Input U-tube Tubesheets Dialog Box Stress Reduction Options - For U-tube tubesheets which are over-stressed at the tubesheet to integral cylinder junction, one of the following options can be used to overcome the overstress: Increase Tubesheet Thickness Increase Integral Cylinder Thickness Increase Both Cylinder and Tubesheet Perform Elastic Plastic Calculation Analyze as Simply Supported None Shell Band Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only
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ASME Tubesheets information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Shell Thickness Adjacent to Tubesheet - Enter the thickness of the shell bands ts1. Shell Band Corrosion Allowance - Enter the corrosion allowance for the shell band. Length of Shell Thk. Adjacent to Tubesheet, front end L1 - Enter the front end length l1 for the shell band. Length of Shell Thk. Adjacent to Tubesheet, rear end L1 - Enter the rear end length l1' for the shell band.
These values of m and y are listed in ASME Sec. VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y please contact your gasket manufacturer. See Table 2-5.1 Gasket Materials and Contact Facings
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CodeCalc User's Guide
ASME Tubesheets
Results (ASME Tubesheets) Part UHX of the Code is divided into four major sections. The first section discusses u-tube exchangers, the second discusses fixed tubesheet exchangers, the third section discusses floating tubesheet exchangers and the fourth section discusses tube-to-tubesheet joint weld. There is a sequence of steps to follow when performing calculations for each type of exchanger. CodeCalc will perform each step and print the applicable formula substitution and answers for each step. All results shown are for the given geometry. In addition, the program will iterate for the minimum thickness of the tubesheet. If needed CodeCalc will also perform the second elastic iteration if high discontinuity stresses exist. The program can run multiple load cases for the fixed tubesheet design as per the ASME code. The table below displays the load cases that are considered for a fixed tubesheet exchanger. Load Case # Corroded
Uncorroded
1
Fvs+Pt-Th-Ca
Fvs+Pt-Th
2
Ps+Fvt-Th-Ca
Ps+Fvt-Th
3
Ps+Pt-Th-Ca
Ps+Pt-Th
4
Fvs+Fvt+Th-Ca
Fvs+Fvt+Th
5
Fvs+Pt+Th-Ca
Fvs+Pt+Th
6
Ps+Fvt+Th-Ca
Ps+Fvt+Th
7
Ps+Pt+Th-Ca
Ps+Pt+Th
8
Fvs+Fvt-Th+Ca
Fvs+Fvt-Th-Ca
Fvt, Fvs - User defined Shell side and Tubeside vacuum pressures or 0.0. Ps, PT - Shell side and Tube-side Design Pressures. Th - With or without Thermal Expansion. Ca - With or without Corrosion Allowance When running these load cases the program automatically adjusts the allowable stresses based on if it is a pressure only load case or pressure + thermal load case. Upset conditions may need to be analyzed. You can enter your own shell/channel vacuum pressures for the multi-case analysis, e.g. 0, 15 psi. This will simulate one of the process fluid streams being stopped, while the other stream continues. In addition to satisfying stress criteria for the tubesheet, the tubes must also be capable of withstanding the axial forces imposed on them due to differential thermal expansion. These forces must be less than the allowable force on the tube per the ASME code equations (App A or UW-20). Tube stresses are also checked against the criteria in section UHX.. Finally, discontinuity stresses must be less than their allowables. If these allowables are exceeded, CodeCalc will perform a second elastic iteration. This is where the plasticity of the integral component is considered. Typically, when this iteration is performed, the stress values will decrease below their allowable values. If for any reason they do not, the geometry of the unit must be reconsidered. If your tubesheet contains a center groove, the groove depth should be subtracted from the overall tubesheet thickness. Bending stress at the junction of shell/channel and tubesheet can also be reduced by having a local shell band adjacent to the tubesheet.
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ASME Tubesheets Display of Results on Status Bar As the user enters the data, program performs the calculation and displays the important results on the status bar. Any error messages are also displayed. This allows a quick design of the tubesheet and makes it easier to try various configurations to select the best one. Any failures are indicated in red. Here is a sample:
Designing a Thick Expansion Joint in the Tubesheet Module: After you input the thick expansion joint geometry in the Tubesheet module, the program uses the following process to design the expansion joint: 1. Compute the expansion joint spring rate 2. Use the expansion joint spring rate in the fixed tubesheet calculations 3. Use the results of the tubesheet calculation, along with the prime pressures, P’s, P’t, and Pd (computed using the TEMA standard) to compute the expansion joint stresses. 4. Run a corresponding expansion joint calculation for each tubesheet load case. The program displays the results for the worst case (detailed results are also available).
Tubesheet MAWP and MAPnc The program will compute the MAWP, maximum allowable working pressure for both the shellside and tubeside. The MAPnc is maximum allowable pressure in the new and cold condition. This is also computed for both sides. If a thick (flanged and flued) expansion joint is specified then MAWP/MAPnc will also be computed for it. Program computes MAWP/MAPnc by setting the pressure on one side to 0 and then iteratively changing the pressure on the other side to find the maximum permissible pressure. The summary table is provided with these maximum pressures and corresponding stress ratios for the various stress conditions.
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SECTION 11
Horizontal Vessels Home tab: Components > Add New Horizontal Vessel Calculates stresses in horizontal pressure vessels created by the combination of internal pressure and the weight of the vessel, its contained liquid and stiffener rings. If included in the analysis, additional loads due to wind per ASCE-98/02,95 93, UBC-97/94, IBC 2003 and earthquake will be included. The program is based on Stresses in Large Horizontal Cylindrical Pressure Vessels on Two Saddle Supports, The Welding Research Supplement, 1951 and subsequent interpretations of that work. This is also called Zick's Analysis.
In This Section
Saddle Wear Plate Design............................................................. 213 Vessel Tab ..................................................................................... 216 Shell/Head Tab .............................................................................. 218 Saddle/Wear Tab ........................................................................... 220 Saddle Webs and Base Plate Dialog Box ..................................... 220 Stiffening Ring Tab (Horizontal Vessels) ....................................... 221 Longitudinal Loads Tab (Horizontal Vessels) ................................ 222 Seismic Loads Tab (Horizontal Vessels) ....................................... 223 Wind Loads Tab (Horizontal Vessels) ........................................... 224 Results ........................................................................................... 226
Saddle Wear Plate Design The horizontal vessels considered by CodeCalc are assumed to have saddle supports. One of the problems with this type of support is the high localized stress, which exists in the vessel in the region of saddles. Typically, the highest stress is the outside circumferential stress at the saddle horn. The ASME code does not address the details of saddle support design, nor does it offer guidance in the computation of the resulting vessel stresses. Instead, the code directs designers to other references for these methods. To date, the design of saddle supports and their associated stresses are based on past practice and experience, without theoretical analysis. A recent paper published in the Journal of Pressure Vessel Technology addresses the issue of local vessel stresses due to saddle supports. This paper (Effectiveness of Wear Plate at the Saddle Support, Ong Lin Seng, Transactions of the ASME, Journal of Pressure Vessel Technology, Vol 114, February 1992) provides a method for the estimation of the wear plate thickness, extension above the saddle horn, and the amount of stress reduction. (It is interesting to note that this paper suggests some of Zick's recommendations are non-conservative.) This optimum thickness of the wear plate is a function of the mean radius of vessel, the thickness of vessel, and the width of wear plate. The optimum wear plate thickness is determined for both welded and non-welded conditions, with wear plate angular extensions of 5, 10, and 15 degrees. Restrictions of this method: 1. The saddle angle must be greater than 120 degrees. Saddle angles of 120 degrees with an appropriate wear plate can result in a 15 to 40 percent stress reduction at horn of the saddle. Larger saddle angles cause a greater stress reduction for the same wear plate ratios.
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Horizontal Vessels 2. The value of (r/b) * sqrt(r/t) must be between 10 and 60, when this term is not within this range, no thickness will be selected. (r = mean radius of the vessel, b = width of the wear plate, t = thickness of the vessel) The conclusions drawn in this paper are: 1. The peak stress in the vessel at the saddle horn can be reduce from 15 to 40 percent when a wear plate is used if the wear plate has the same thickness as the vessel and extends at least 5 degrees above the saddle horn. 2. The peak stress in the vessel remains at the saddle horn when using a thin wear plate. 3. The stress reduction does not vary greatly with a variation in saddle support angle. 4. A welded wear plate reduces stresses better than a non-welded wear plate.
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Horizontal Vessels Horizontal Vessel Geometry
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Horizontal Vessels Wear Plate and Saddle Details for a Typical Horizontal Tank
Vessel Tab Item Number - Type an item number for the horizontal vessel. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Vessel Design Pressure - Enter the pressure under which the horizontal vessel is operating. A positive entry indicates internal pressure while a negative number indicates external pressure. No external pressure check for adequate wall thickness will be performed. Use the shell program and analyze the geometry before using the HORIZVES module. Vessel Design Temperature - Enter the operating temperature of the vessel. The temperature is used to determine the allowable stress of the material from the material database. If the temperature is changed, the allowable stress of the material at operating temperature changes accordingly. Corrosion Allowance - Enter the allowance given for corrosion. The corrosion allowance cannot be greater than the vessel wall thickness, but it must be greater than zero (0). Some common corrosion allowance values are: 0.0625 - 1/16"
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Horizontal Vessels 0.1250 - 1/8" 0.2500 - 1/4" Density of Stored Liquid - Enter the density of the fluid in the horizontal vessel. If you have more than one fluid consideration, such as test (water) or operating, you may need to have more than one model with the respective densities. You can enter a number of specific gravity units and CodeCalc will convert the number entered to the current set of units. To do this, enter a number followed by the letters sg. Liquid Height from bottom of Tank (used if > 0) - Enter the height of the liquid in the tank. Normally, a Zick analysis is run with the vessel full of water; however, it may be necessary to run a partially filled tank for wind or seismic analysis for an operating type load case. Extra Weight, ie. (platforms, insulation, piping) - Enter any additional weight present on the vessel. Additional weight can come from insulation, steel structures, or piping loads. There is no screen range checking for this value since it may be positive or negative. However, if the value is negative, it should not be greater than the total weight of the vessel. Saddle Reaction Force Factor - Enter the factor the saddle reaction force due to the Wind or Earthquake transverse load. The recommended value is three (3). The value of six (6) is conservative in that it assumes that the maximum edge load is uniform across the entire base, when, in reality, it occurs only at the edge. A more accurate method is to convert this triangular loading into a more realistic uniform load, which leads to a value of 3. The following illustration shows the end view of a horizontal vessel with a transverse load, simulating Wind/Seismic loading:
Figure 47: Saddle Reaction Force Factor
The saddle reaction load Fst (or Fwt for wind) due to the transverse load Ft is: Fst (or Fwt) = ftr * Ft * B / E. Distance from Vessel Centerline to Saddle Base - Enter the distance from the center of the vessel to the bottom of the saddle support. This distance must be greater than the vessel outside radius.
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Horizontal Vessels Check Saddle Webs & Base Plate? - If you want the software to perform computations on the structure that supports the vessel, select this option. The software will compute the inertias, moments, and forces on the members necessary to perform an AISC unity check. Apply Wind Loads to Vessel? - Select this option to consider wind loads. If you select this option, other information, such as wind speed and input prompts must be defined. Apply Seismic Loads to Vessel? - If seismic loads are a design consideration, select this option. Both seismic and wind loads will increase the saddle load reaction forces, resulting in higher vessel stresses. Apply Longitudinal Loads to Vessel? - Displays the Longitudinal Loads dialog box in which you can specify the friction coefficient Mu and a user-defined longitudinal force. Stiffening Ring Present? - If the vessel is equipped with stiffening rings, select this option. Stiffening rings are used to reduce stresses in the vicinity of the saddle supports and are also used to meet external pressure requirements. When equipped with rings, the assumption is that there are either one or two rings located directly over the saddle. The rings are assumed to span 360-degrees (saddle bearing angle) around the vessel. This option is mainly used for the calculation of the ring weight.
Shell/Head Tab Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Shell Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
CodeCalc User's Guide
Horizontal Vessels Shell Diameter - Enter the shell diameter with respect to the shell and head diameter basis. The diameter must be greater than 0 and greater than 2.0 times the wall thickness. Shell Length, Tangent-to-Tangent - Enter the length of the cylindrical shell from tangent-to-tangent. Shell Thickness - Enter the un-corroded thickness of the shell. The software will automatically corrode the wall thickness as necessary. Some common thickness values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" 0.3750 - 3/8" 0.4375 = 7/16" 0.5000 - 1/2" 0.6250 - 5/8" 0.7500 - 3/4" 0.8750 - 7/8" 1.000 - 1" Shell Joint Efficiency - Enter the seam efficiency of the shell. This value is greater than 0 and less than or equal to 1.0. This entry is used to compute the required thickness of the shell. Value
Result
1.00
Full radiography
0.85
Spot X-Ray
0.70
No - Radiography
Type of Head - Select the type of head that is used on the vessel ends: Elliptical, Torispherical, Hemispherical, or Flat. If you select Flat, the software presumes the head is round and the same diameter as the shell. Aspect Ratio for Elliptical Head - The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1, elliptical head the aspect ratio is 2.0. Knuckle Ratio (L/r) for Torisperical Heads - The knuckle ratio for a torispherical head is defined as the crown radius of the head divided by the knuckle radius. This ratio is typically 16.6667:1, which means that you would enter a value of 16.667. Because this is a ratio, this value is unitless. Crown Radius for Torisperical Heads - Enter the crown radius of the torispherical head in this cell. Refer to Shells and Heads (on page 49). Head Thickness - Enter the uncorroded thickness of the head. The value must be greater than 0.0. Effects of corrosion are handled automatically. Head Joint Efficiency - Enter the seam efficiency of the shell. This value is greater than 0 and less than or equal to 1.0. This entry is used to compute the required thickness of the shell. Value
Result
1.00
Full radiography
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Horizontal Vessels 0.85
Spot X-Ray
0.70
No - Radiography
Shell/Head Diameter Basis - Select one of the following: OD (outside diameter) or ID (inside diameter).
Saddle/Wear Tab Distance from Saddle to Vessel Tangent - Enter the length from the vessel tangent to the saddle support. This distance must be positive and less than 1/2 of the vessel tangent-to-tangent length. Saddle Width - Enter the width of the surface on the saddle support that will contact with the vessel. This dimension is also the width of the side ribs. It is noted as dimension b in most pressure vessel text literature and is shown in the way in the CodeCalc manual. It is also dimension Gb in the rib dimension illustration. Saddle Bearing Angle - Enter the number of degrees that the saddle bears on the shell surface. Valid entries range from 120- to 180-degrees. Wear Pad Thickness - Enter the thickness of the wear pad, if there is one on the vessel. The wear pad is generally a rectangular piece of pipe or plate that is bent to conform to the outside of the vessel. The wear pad fits in between the saddle support and the vessel wall. Its function is to reduce local stresses in the area of the saddle support at the vessel wall. If the distance from the vessel tangent to the saddle location is less than or equal to the shell radius/2.0 and the wear pad extension above the horn of the saddle is greater than the shell radius divided by 10.0, then the thickness of the wear pad will be included. If this is not the case then the shell thickness, ca, will be used. Wear Pad Extension Above Horn of Saddle - If the vessel has a wear pad and it extends above the horn of the saddle, enter that extension distance here. For more information on wear pads, see Wear Pad Thickness. Wear Pad Width - Enter the width of the wear pad, if one exists. The width of the wear pad is measured along the long axis of the vessel. The wear pad is usually slightly wider than the saddle support.
Saddle Webs and Base Plate Dialog Box Baseplate Length - Enter the length of the base plate. This is typically referred to as dimension A. This value is usually close to the diameter of the vessel. Baseplate Thickness - Enter the thickness of the baseplate. If you want to consider any external corrosion or erosion, enter the corroded thickness value, instead of the uncorroded value. The baseplate thickness will be computed using a beam bending type equation found in pressure vessel texts. The baseplate thickness is not a function of the number of ribs. Baseplate Width - Enter the width of the base plate. This is the short dimension. Number of Ribs (including outside ribs) - Enter the number of ribs in your design. This number should include the outside ribs. Rib Thickness - Enter the thickness of the ribs. The ribs run in a direction that is parallel to the long axis of the vessel. Any external corrosion allowance should be taken into account when this value is entered.
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Horizontal Vessels Web Thickness - Enter the thickness of the Webs. The webs run in a direction perpendicular to the long axis of the vessel. Any external corrosion should be taken into account when this value is entered. Web Location - Specify the web location. Center webs run through the middle of the base plate, whereas Side webs run along the edge of the base plate. Height of Center Web - Enter the height of the center web as it extends from the bottom of the base to the shell ID (inside diameter). Design Temperature of Saddle/Baseplate - Enter the temperature at which the vessel will be operating. The temperature will be used to determine the allowable stress of the material chosen. If the temperature is changed, the allowable stress of the material at operating temperature will change accordingly. Saddle/Baseplate/Web/Rib Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Stiffening Ring Tab (Horizontal Vessels) Stiffening Ring Location - Select OD (outside diameter) if the stiffening rings are located on the outside of the vessel; if the rings are located inside the vessel, then select ID (inside diameter). Stiffening Ring Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Stem of Tee Stiffener, Height (Corroded) - Enter the stem height (in inches) of the tee stiffener.
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Horizontal Vessels Stem of Tee Stiffener, Thickness (Corroded) - Enter the stem thickness (in inches) of the tee stiffener. Cross of Tee Stiffener, Width (Corroded) -Enter the cross width (in inches) of the tee stiffener. Cross of Tee Stiffener, Thickness (Corroded) - Enter the cross thickness (in inches) of the tee stiffener. Moment of Inertia of Stiffening Ring - Enter the moment of inertia of the ring about its neutral axis. For typical cross-sections, this property can be calculated or looked up in a handbook--such as the AISC steels handbook-- that lists properties of steel shapes. If the stiffening ring properties cannot be defined in any other way, you can use the options in the Generic Ring Properties section to define the required values. Cross Sectional Area of Stiffening Ring - Enter the user-defined cross-sectional area of the ring. This number can be calculated or "looked up" in a steels handbook, such as the AISC steels handbook. Distance to Ring Centroid from Shell Surface - Enter the distance to the centroid of the beam section--I, T, and so forth--that is used to reinforce the cone/cylinder junction. You can usually find this information in the Manual of Steel Construction for common beam sections. Height of Stiffener from Shell Surface - Do one of the following: If the stiffening ring is on the outside of the vessel, then enter the distance from the outside shell surface to the top most part of the ring. If the ring is on the inside of the vessel, then enter the distance from the inner surface of the shell to the top of the ring.
Longitudinal Loads Tab (Horizontal Vessels) Friction Coefficient Mu - Enter the friction coefficient between the saddle and the foundation. The frictional force is caused by expansions and contraction of the vessel shell if the operating system varies from the atmospheric temperature. The following table shows some values of friction coefficient, taken from Pressure Vessel Design Manual by Dennis R. Moss 2nd edition, page 156. Surfaces
Friction Factor (mm)
Lubricated Steel-to-Concrete
0.45
Steel-to-Steel
0.40
Lubrite-to-Steel Temperature over 500-degrees (F) Temperature 500-degrees (F) or less Bearing pressure less than 500 psi
0.15 0.10 0.15
Teflon-to-Teflon Bearing pressure 800 psi or more Bearing pressure 300 psi or less
0.06 0.1
User-Defined Longitudinal Force - Enter any additional longitudinal force acting on the horizontal vessel. The largest of the longitudinal forces--user-defined, Wind/Seismic, and due to friction--are used for designing the horizontal vessel. Examples can be prior deflection or turbo bundle pullout load for a heat exchanger.
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Horizontal Vessels
Seismic Loads Tab (Horizontal Vessels) Seismic Zone Identifier - Select the seismic zone in which your vessel is operating. The seismic zones are pictured in ASCE #7 and reproduced in the accompanying illustration. A value of 0 will not increase the saddle reaction force. An Identifier of 5 (Zone 4) will produce the highest saddle load reactions. These values are derived from UBC. The basic equation for lateral G force is : Cs = Z I C / Rw : Rw = 3, C = 2.75, I = 1.0 Seismic Zone
Cs
0
0.0
1
0.069
2a
0.138
2b
0.184
3
0.275
4
0.367
The following illustration shows a seismic risk map of the United States from the ASCE code:
User-Entered Seismic Factor Cs - When you enter a valid seismic zone and leave this field blank or at 0, the software uses the following table of coefficients: Zone
Cs
0
0.0
1
0.069
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Horizontal Vessels 2a
0.138
2b
0.184
3
0.275
4
0.367
This number is then used in conjunction with the operating weight of the vessel to compute the forces that act on the saddle supports. If for any reason the table value of Cs is unacceptable, entry of a non-zero value will cause this to be used in lieu of the table value. This can occur if the building code in your project specifications is different from the one used by the software.
Wind Loads Tab (Horizontal Vessels) Additional Area (Insulation Are, Structures) - If necessary, enter any additional area exposed to the wind from piping, platforms, insulation, and so forth, you want considered. The software will automatically compute an effective diameter with the input diameter known. User-Defined Wind Pressure on Vessel - If your vessel specification calls for a constant wind pressure design, and you know what that pressure is, enter it here. Most Wind Design codes have minimum wind pressure requirements, so check those carefully. The wind pressure will be multiplied by the area calculated by the program to get a shear load and a bending moment. If you enter a positive number here, the software will use this number regardless of the information in the following cells. Wind Design Code - Specify the wind design standard. You can select from the available options: ASCE 7-93, ASCE 7-95, ASCE 7-98/02 / IBC 2003, or UBC 94/97. To use a different wind code, you can compute and enter the design wind pressure; the software will multiply the wind pressure by the area to compute the wind load. Force Coefficient (Cf) - Enter the force coefficient, or shape factor, for the vessel. This factor takes into account the shape of the structure. This factor is also known as the pressure coefficient, Cq in the UBC Wind code. The acceptable range of input is between 0.5 and 1.2. This can also be seen in the following codes: ANSI A58.1, refer to Table 12 ASCE 7-93, refer to tables 11-14, pages 21-22 ASCE 7-95, refer to tables 6-6 to 6-10, pages 32-33 ASCE 7-98, refer to tables 6-9 to 6-13 ASCE 7-2002, refer to tables 6-18 to 6-22, pages 68-72 UBC-1997 code, refer to table 16-H. Importance Factor (I) - Enter the value of the importance factor that you wish the program to use. The importance factor accounts for the degree of hazard to life and property. The software will use this value directly without modification. Values of typical importance factors for ASCE 7-93, ASCE 7-95/98/02 and UBC 1997 standards are listed in the following tables. 1.11.
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The following values are used for ASCE 7-93. In general, this value ranges from .95 to
Category
100 mi from Hurricane Oceanline
At Oceanline
I
1.00
1.05
II
1.07
1.11
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Horizontal Vessels III
1.07
1.11
IV
0.95
1.00
Category Classification: I
buildings and structures not listed below
II
buildings and structures where more than 300 people congregate in one area
III
buildings designed as essential facilities, hospitals etc.
IV
buildings and structures that represent a low hazard in the event of a failure
Most petrochemical structures are 1, Importance I. ASCE-7-95/98/02: In general this value ranges from .77 to 1.15. It is taken from table 6-2 of the ASCE 95 standard or table 6-1 from the 98 standard. Category
Importance Factor (I)
I
0.87
II
1.00
III
1.15
IV
1.15
In the 98 standard for Wind Speeds > 100 mph for category I, the importance factor can be 0.77. Category Classification: I
buildings and other structures that represent a low hazard to human life in the event of failure
II
buildings and structures except those listed in categories I, III and IV
III
buildings and structures that represent a substantial hazard in the event of a failure
IV
buildings designed as essential facilities, hospitals, and so on.
Most petrochemical structures are 1, Importance I. For UBC 1997 code these values are listed in the following table. Category
Importance Factor (I)
I, Essential facilities
1.15
II, Hazardous facilities
1.15
III, Special occupancy structures
1.00
IV, Standard occupancy structures
1.0
Basic Wind Speed (V) - Enter the design value of the wind speed. The wind speeds vary according to geographical location and/or to company/vendor standards. The following list shows some typical wind speeds in miles per hour. 85.0 miles per hour 100.0 miles per hour 110.0 miles per hour 120.0 miles per hour Enter the lowest value reasonably allowed by the standards you are following, since the wind design pressure and force increase as the square of the speed.
Wind Exposure - This category reflects the characteristics of ground surface irregularities for the site at which the structure is to be constructed. Use the table below to determine the appropriate exposure category for the ASCE codes.
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Horizontal Vessels Exposure Category
Description
A
Large city centers with at least 50% of the buildings having a height in excess of 70 feet.
B
Urban and suburban areas, wooded areas, or other terrain with numerous closely spaced obstructions having the size of single family dwellings.
C
Open terrain with scattered obstructions having heights generally less than 30 feet. This category includes flat, open country and grasslands.
D
Flat, unobstructed coastal areas directly exposed to wind flowing over large bodies of water.
Most petrochemical sites use a value of 3, or Exposure Category C. UBC Exposure Factor as defined in UBC-91 Section 2312: Exposure Category
Description
B
Terrain with building, forest or surface irregularities 20 feet or more in height covering at least 20 percent or the area extending one mile or more from the site.
C
Terrain which is flat and generally open, extending one-half mile or more from the site in any full quadrant.
D
The most severe exposure with basic wind speeds of 80 mph or more. Terrain which is flat and unobstructed facing large bodies of water over one mile or more in width relative to any quadrant of the building site. This exposure extends inland from the shoreline 1/4 mile or 0 times the building (vessel) height, whichever is greater.
Most petrochemical sites use a value of 3, or Exposure Category C. This value is used to set the Gust Factor Coefficient (Ce) found in Table 16-G. Height of Vessel Centerline Above Grade - Enter the height of the vessel above the surface of the earth (grade). Type of Hill - Enter the type of hill: None, 2-D Ridge, 2-D Escarpment, or 3-D Axisymmetric Hill. For more information, see ASCE 7-95, Fig. 6-2. Height of Hill or Escarpment (H) - Enter height of hill or escarpment relative to the upwind terrain. For more information, see ASCE 7-95 Fig. 6-2. Distance to Site (x) - Enter distance (upwind or downwind) from the crest to the building site. For more information, see ASCE 7-95 Fig. 6-2. Distance to Crest (Lh) - Enter the distance upwind of crest to where the difference in ground elevation is half the height of hill or escarpment. For more information, see ASCE 7-95 Fig. 6-2 for details.
Results CodeCalc determines the volume of the vessel as well as the empty and full weights. These weights are computed with the vessel in the corroded condition. Knowing the weights may be useful for cost estimating and for design of supporting attachments, such as lifting lugs. The longitudinal stresses displayed in the output include the stresses due to internal pressure. Since these are normal stresses they are added together. The allowable tension is the basic operating allowable times the joint efficiency. The compressive allowable is the factor B taken from UG-23 using the materials chart for the given material. The tangential shear in the shell varies depending on whether the shell is stiffened or the head acts as a stiffener, or neither of these cases. Tangential stress in the head only exists if the head
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Horizontal Vessels is close enough to the saddle to be used as a stiffener. The allowable stress in shear is 80% of the allowable tensile stress for the head or shell. The stress at the horn of the saddle depends on the location of the saddle and the equivalent thickness of the saddle and wear pad. It is zero if rings stiffen the shell. This stress is always compressive and the allowable stress is a negative of the minimum of 1.5 times the allowable tensile stress and 0.9 times the yield stress. Use of the head as a stiffener creates additional tension stress in the head. The allowable additional stress in the vessel head is limited to 0.25 times the allowable tension stress in the head. If pressure is added, the resulting stress must be less than 1.25 times the allowable tensile stress. If the tip of the stiffening ring is in compression, its allowable will be -0.5 times the yield stress. If a tensile condition exists, the basic material allowable will be used.
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SECTION 12
Rectangular Vessels (App. 13) Home tab: Components > Add New Rectangular Vessel Performs stress calculations and maximum allowable working pressure calculations for the rectangular, obround, and circular vessels described in the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2001, A-2003, Appendix 13. The calculations are taken from sections 13-6 through 13-13. The Rectangular Vessels module analyzes the following vessels: Fig. 13-2 (a)(1) - Vessel with equal long-side and short-side thickness. (Figure A) Fig. 13-2 (a)(2) - Vessel with differing long-side thickness. (Figure B) Fig. 13-2 (a)(3) - Vessel with rounded corners. (Figure C) Fig. 13-2 (a)(4) - Reinforced vessel. (Figure D) Fig. 13-2 (a)(5) - Non-continuous reinforced vessel with rounded corners.(Figure E) Fig. 13-2 (a)(6) - Non-continuous reinforced vessel with rounded corners. (Figure F) Fig. 13-2 (a)(7) - Rectangular vessel with single stay plate/row of bars. (Figure G) Fig. 13-2 (a)(8) - Rectangular vessel with two stay plates/rows of bars. (Figure H) Fig. 13-2 (b)(1) - Obround vessel. (Figure I) Fig. 13-2 (b)(2) - Reinforced obround vessel. (Figure J) Fig. 13-2 (b)(3) - Obround vessel with single stay plate/row of bars. (Figure K) Fig. 13-2 (c)(1) - Circular vessel with single diametral plate. (Figure L) The software first performs ligament efficiency calculations for those vessels with holes in the side plates. The membrane and bending ligament efficiencies are used to adjust the stress calculations at the mid-side of the plates. The ligament efficiency calculations are based on section 13-6, and are performed for both uniform and multi diameter hole patterns. After the ligament efficiencies are determined, the software performs the individual stress calculations. Membrane, bending, and total stress calculations are performed as prescribed by the Code in Sections 13-7 through 13-13. These stresses are compared to their allowables and a highest percentage of allowable calculation is performed. The final calculation performed by the Rectangular Vessels module is the maximum allowable working pressure (MAWP) calculation. The software computes an MAWP for all three types of stresses (Membrane, Bending, and Total). Additionally, depending on the specific geometry of those vessels stayed by bars, an additional MAWP is computed per Equation 2 of UG-47.
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Rectangular Vessels (App. 13) Rectangular Vessels takes full account of the corrosion allowance. The software uses the corroded condition for all dimensions in its calculations. The only exception is the reinforcement calculations. The reinforcing member is assumed to be entered in its corroded state.
Figure 48: Rectangular vessel with equivalent long side thickness (Vessel Type A1)
Figure 49: Rectangular vessel with different long side thickness (Vessel Type A2)
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Figure 50: Rectangular vessel with rounded corner (Vessel Type A3)
Figure 51: Reinforced rectangular vessel (Vessel Type A4)
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Figure 52: Non-continuously reinforced rectangular vessel (Vessel Type A5)
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Figure 53: Non-continuously reinforced vessel with rounded corners (Vessel Type A6)
Figure 54: Vessel stayed by stay plate/stay bars (Vessel Type A7 or A7-B)
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Figure 55: Vessel stayed by stay plates/stay bars (Vessel Type A8 or A8-B)
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Figure 56: Reinforced Obround Vessel (Vessel Type B2)
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Figure 57: Circular vessel stayed by single diametral plate (Vessel Type C1)
In This Section
Vessel Tab ..................................................................................... 239 Short Side Tab ............................................................................... 256 Long Side Tab ............................................................................... 258 Reinforcing Bar Options ................................................................. 260 Reinforcing Section Options .......................................................... 261 Results ........................................................................................... 261
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Vessel Tab Item Number - Type an item number for the rectangular vessel. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Design Internal Pressure - Enter the internal design pressure. For vessel type C1, this is the entry for P1.
Figure 58: Design Internal Pressure for Type C1
If analyzing vessel type C1, be aware that the P1 value is associated with only one of the two chambers. If both chambers are operating at the same pressure, then an equal value must be entered for P2. Design Temperature - Enter the temperature associated with the internal design pressure. The software automatically updates the materials properties for built-in materials when you change the design temperature. If you entered the allowable stresses manually, you are responsible for updating them for the given temperature. Shell Section Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Vessel Corrosion Allowance - Enter the allowance given for corrosion. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar.
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Rectangular Vessels (App. 13) Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Figure Number for Type of Vessel - Enter the ID of the type of rectangular vessel to be analyzed. The possible ID types are as follows: ID Number
Figure 13-2 from ASME Sec. VIII Div. 1 Appendix 13
A1
A2
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Rectangular Vessels (App. 13) A3
A4
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Rectangular Vessels (App. 13) A5
A6
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Rectangular Vessels (App. 13) A7
A7-B
Figure 13-2 (a)(7) is of a vessel with single central stay plate. This type can also be used for vessels with unequal compartments as shown in Figures 13-2(a) (9/10), by using the maximum dimension (h) from among the two compartments.
Same as item number A7 but with Stay bars.
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Rectangular Vessels (App. 13) A8
A8-B
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Figure 13-2 (a)(8) is of a vessel stayed by two Stay plates. This type can also be used for vessels with unequal compartments as shown in Figures 13-2(a) (9/10), by using the maximum dimension (h) from among the two compartments.
Same as item number A8 but with Stay bars.
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B2
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Rectangular Vessels (App. 13) B3
B3-B
Same as item number B3 but with Stay bars.
C1
Figure 59: Design Internal Pressure for Type C1
Min. Thick of End Closure Plate/Vessel Head (t5) - Enter the minimum thickness of the end plate. If a valid thickness is entered, the end plate will be analyzed per UG-34. If the thickness value is entered as zero, or left blank, no calculation is performed on the end plate. C-Factor for End Closure Plate/Vessel Head - The C Factor is used in the equation to compute the required thickness of welded end plates. Typical values are 0.2 or 0.3. For more information, see UG-34.
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Figure A1 Dialog Box Design External Pressure - Enter the design external pressure for figure A1 or A2 if you wish to have the external pressure calculations performed. When entered, external pressure stress calculations, as well as vessel stability calculations, will be performed. Modulus of Elasticity - When there is an external pressure value, enter the elastic modulus of the material from Subpart 3 of Section II, Part D at design temperature. Length of Vessel - Enter the length dimension of vessel. This entry is required for vessel type C1 and for the external pressure calculations in vessel types A1 and A2.
Figure A2 Dialog Box Modulus of Elasticity - When there is an external pressure value, enter the elastic modulus of the material from Subpart 3 of Section II, Part D at design temperature. Design External Pressure - Enter the design external pressure for figure A1 or A2 if you wish to have the external pressure calculations performed. When entered, external pressure stress calculations, as well as vessel stability calculations, will be performed. Length of Vessel - Enter the design external pressure for figure A1 or A2 if you wish to have the external pressure calculations performed. When entered, external pressure stress calculations, as well as vessel stability calculations, will be performed. Min. Thick of 2nd Long-Side Plate - Enter either the minimum thickness of the second long-side plate used to build the vessel or the minimum thickness measured for an existing vessel. This option is only used in the analysis of vessel type A2 (Figure B). Appendix 13 allows vessels of this type to have differing long-side thickness. This option is required if you are analyzing vessel type A2. Radius of Corner Section - Type the radius of the corner section for vessels A3 and A5. The software assumes each of the corner sections to have equivalent radii. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Pitch Distance Between Reinforcing Members - Type the maximum pitch distance between reinforcing members. This value must be greater than or equal to the width of the reinforcing member. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1.
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Rectangular Vessels (App. 13) Delta - Type the material parameter used to calculate pitch. The following materials are listed in Appendix 13, Table 13-8(3): Material
English
Carbon Steel
6000
15754.54
Austenitic SS
5840
15334.42
6180
16227.17
Ni-Fe-Cr
6030
15833.31
Aluminum
3560
9347.69
Nickel Copper
5720
15019.33
Unalloyed Titanium
4490
11789.65
Ni-Cr-Fe
SI
Radius of Corner Section - Type the radius of the corner section for vessels A3 and A5. The software assumes each of the corner sections to have equivalent radii.
Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Pitch Distance Between Reinforcing Members - Type the maximum pitch distance between reinforcing members. This value must be greater than or equal to the width of the reinforcing member. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Delta - Type the material parameter used to calculate pitch. The following materials are listed in Appendix 13, Table 13-8(3): Material
English
Carbon Steel
6000
15754.54
Austenitic SS
5840
15334.42
6180
16227.17
Ni-Fe-Cr
6030
15833.31
Aluminum
3560
9347.69
Nickel Copper
5720
15019.33
Unalloyed Titanium
4490
11789.65
Ni-Cr-Fe
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Rectangular Vessels (App. 13) Radius of Corner Section - Enter either the minimum thickness of the second long-side plate used to build the vessel or the minimum thickness measured for an existing vessel. This option is only used in the analysis of vessel type A2 (Figure B). Appendix 13 allows vessels of this type to have differing long-side thickness. This option is required if you are analyzing vessel type A2.
Stay Plate/Reinforcment Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Pitch Distance Between Reinforcing Members - Type the maximum pitch distance between reinforcing members. This value must be greater than or equal to the width of the reinforcing member. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Delta - Type the material parameter used to calculate pitch. The following materials are listed in Appendix 13, Table 13-8(3): Material
English
Carbon Steel
6000
15754.54
Austenitic SS
5840
15334.42
6180
16227.17
Ni-Fe-Cr
6030
15833.31
Aluminum
3560
9347.69
Nickel Copper
5720
15019.33
Unalloyed Titanium
4490
11789.65
Ni-Cr-Fe
SI
Radius of Corner Section - Type the radius of the corner section for vessels A3 and A5. The software assumes each of the corner sections to have equivalent radii.
Short-Side Unreinforced Length Dimension (L11) - Enter the unreinforced length dimension for vessel A6. This dimension is L11 for the short-side. Long-Side Unreinforced Length Dimension (L21) - Enter the unreinforced length dimension for vessel A6. This dimension is L21 for the long-side. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click
to open the Material Database Dialog Box (on page 385).
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Rectangular Vessels (App. 13) The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B. Min Thick/Dia of Stay Plate/Rod (t4) - Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry only when you are analyzing vessel types A8 or A8-B. Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar. The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B.
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Rectangular Vessels (App. 13) Min Thick/Dia of Stay Plate/Rod (t4) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B. Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar. The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Is the Stay Plate Welded to the End Plate? - Check this box for the software to perform the end plate calculations based on the entire long-side length. If you do not check this box, the software uses the dimensions of the compartment formed by the stay plate. Pitch Distance Between Bars of Diameter - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B. Min Thick/Dia of Stay Plate/Rod (t4) - Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry only when you are analyzing vessel types A8 or A8-B. Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar.
The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16"
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Rectangular Vessels (App. 13) 0.1250 - 1/8" 0.2500 - 1/4" Is the Stay Plate Welded to the End Plate? - Check this box for the software to perform the end plate calculations based on the entire long-side length. If you do not check this box, the software uses the dimensions of the compartment formed by the stay plate. Pitch Distance Between Bars of Diameter t3 - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. Pitch Distance Between Bars of Diameter t4 - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B. Min Thick/Dia of Stay Plate/Rod (t4) - Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry only when you are analyzing vessel types A8 or A8-B. Stay Plate Corrosion Allowance Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar.
The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Is the Stay Plate Welded to the End Plate? - Check this box for the software to perform the end plate calculations based on the entire long-side length. If you do not check this box, the software uses the dimensions of the compartment formed by the stay plate.
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Rectangular Vessels (App. 13) Pitch Distance Between Bars of Diameter t3 - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. Pitch Distance Between Bars of Diameter t4 - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Pitch Distance Between Reinforcing Members - Type the maximum pitch distance between reinforcing members. This value must be greater than or equal to the width of the reinforcing member. C-Factor (From UG-7) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Delta - Type the material parameter used to calculate pitch. The following materials are listed in Appendix 13, Table 13-8(3): Material
English
Carbon Steel
6000
15754.54
Austenitic SS
5840
15334.42
6180
16227.17
Ni-Fe-Cr
6030
15833.31
Aluminum
3560
9347.69
Nickel Copper
5720
15019.33
Unalloyed Titanium
4490
11789.65
Ni-Cr-Fe
SI
Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material.
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Rectangular Vessels (App. 13) 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B. Min Thick/Dia of Stay Plate/Rod (t4) - Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry only when you are analyzing vessel types A8 or A8-B. Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar.
The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Is the Stay Plate/Rod Welded to the End Plate - Check this box for the software to perform the end plate calculations based on the entire long-side length. If you do not check this box, the software uses the dimensions of the compartment formed by the stay plate.
Figure B3-B Dialog Box Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B.
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Rectangular Vessels (App. 13) Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar. The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Is the Stay Plate/Rod Welded to the End Plate? - Check this box for the software to perform the end plate calculations based on the entire long-side length. If you do not check this box, the software uses the dimensions of the compartment formed by the stay plate. Pitch Distance Between Bars - Type the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. C-Factor (From UG-47) - Specify the attachment factor for braced and stayed surfaces. This factor is taken from UG-47; the default value is 2.1. Vessel Radius - Enter the inside radius of vessel type C1. Length of Vessel - Enter the length dimension of vessel. This entry is required for vessel type C1 and for the external pressure calculations in vessel types A1 and A2. Pressure in 2nd Compartment - Type the internal pressure of the second compartment in vessel C1. You must enter an internal design pressure that is less than or equal to P1. In the event that the two compartments have equivalent pressure, the value entered for P2 must equal the value entered for P1. If left blank, a value of zero is used for P2. Stay Plate/Reinforcement Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Stay Plate Corrosion Allowance - Enter the appropriate corrosion allowance. The software adjusts the actual thickness and the inside diameter of the vessel and adjusts the actual thickness and the outside diameter of the stay plate/bar. The stay plate/bar will be corroded twice to account for the fact that they are exposed to fluid on both sides. Consequently, enter the corrosion allowance of only one side. Some common corrosion allowance values are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4"
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Rectangular Vessels (App. 13) Min Thick/Dia of Stay Plate/Rod (t3) - Enter the minimum thickness of the stay plate or the diameter of the rod, if analyzing a stayed vessel. This is a required entry when you are analyzing vessel types A7, A7-B, A8, A8-B, B3, or B3-B.
Short Side Tab Short-Side Length Dimension (H, L1, Le, or 2R) - Enter the design length of the short-side of the vessel. This dimension is dependent on the particular vessel being analyzed as indicated in the following table: A1
H - Inside length of long-side of vessel
A2
h - Inside length of long-side of vessel
A3
L1 - Half-length of short-side minus the corner radius
A4
H - Inside length of short-side of vessel
A5
L3 - Half-length of short-side of vessel
A6
L3 - Half-length of short-side of vessel
A7
h - Inside length of short-side of vessel
A7-B
h - Inside length of short-side of vessel
A8
h - Inside length of short-side of vessel
A8-B
h - Inside length of short-side of vessel
B1
2R - Inside Diameter of Rounded Short-side
B2
2R - Inside Diameter of Rounded Short-side
B3
2R - Inside Diameter of Rounded Short-side
B3-B
2R - Inside Diameter of Rounded Short-side
C1
*** No Entry Required ***
Min. Thick of Short-Side Plates (t1) - Enter the minimum thickness of the short-side plate used to build the vessel, or the minimum thickness measured for an existing vessel. The short-side thickness value is a required entry for all vessel types. When the Code specifies a single thickness (A3 and C1), the short-side thickness is used for both t1 and t2.
Short-Side Joint Efficiency Factor (Mid-Side) - Enter the efficiency of the welded joint for vessels with welded joints. This joint efficiency value will be used to adjust the corner and the mid-side allowable stress values. The mid-side joint efficiencies will not be used if there are holes on the side of the vessel. Instead, the ligament efficiencies will be used to adjust the actual stress values. Typical values are: 1.00 Full Radiography 0.85 Spot X - Ray 0.70 No - Radiography For help determining this value, refer to Section VIII, Div. 1, Table UW-12. Corner Section Joint Efficiency Factor - Enter the efficiency of the welded joint for vessels with welded joints. This joint efficiency value will be used to adjust the corner and the mid-side allowable stress values. The mid-side joint efficiencies will not be used if there are holes on the side of the vessel. Instead, the ligament efficiencies will be used to adjust the actual stress values. Typical values are: 1.00 Full Radiography
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0.85 Spot X - Ray 0.70 No - Radiography
For help determining this value, refer to Section VIII, Div. 1, Table UW-12. Threaded Holes in Short Side Plate? - If the plate has uniform or multi-diameter holes, check this option to enter the pitch, diameter, and depth parameters. Ligament efficiency calculations will be performed in order to adjust the calculated actual stress values. Center to Center Distance Between Holes - If the plate has uniform or multi-diameter holes, check this option to enter the pitch, diameter, and depth parameters. Ligament efficiency calculations will be performed in order to adjust the calculated actual stress values. Diameter of Hole - Type the diameter (d0, d1, d2) of the hole of corresponding length (T0, T1, T2). If the hole is of uniform diameter, then a value for d0 is the only required entry.
Figure 60: Hole Diameter to Corresponding Lengths and Center-to-Center
The values for d0, d1, and d2 must be entered in decreasing diameter size. Depth of Hole - Type the depth (T0, T1, T2) of the hole of corresponding diameter (d0, d1, d2). If the hole is of uniform diameter, then a value for T0 is the only required entry.
Figure 61: Hole Diameter to Corresponding Lengths and Center-to-Center
The sum of the values for T0, T1, and T2 must equal to the entire side thickness. Ligament Efficiencies - Enter ligament efficiencies for tube spacing. Distance from Neutral Axis - Enter the neutral axis distance. Type of Short-Side Reinforcement - Enter the index for the type of reinforcement on the rectangular vessel.
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None - No reinforcing ring. Bar - Enter the width and thickness of the bar. Section - Enter the moment of inertia, cross-sectional area, and the distance from the shell to the centroid of the beam.
Long Side Tab Long-Side Length Dimension (h, L2, L4, or 2R) - Enter the design length of the long-side of the vessel. This dimension is dependent on the particular vessel being analyzed as indicated in the following table: A1
h - Inside length of long-side of vessel
A2
h - Inside length of long-side vessel
A3
L2 - Half-length of long-side minus the corner radius
A4
h - Inside length of long-side of vessel
A5
L4 - Half-length of long-side
A6
L4 - Half-length of long-side of vessel
A7
h - Inside length of long-side of vessel
A7-B
h - Inside length of long-side of vessel
A8
h - Inside length of long-side of vessel
A8-B
h - Inside length of long-side of vessel
B1
L2 - Half-length of long-side of vessel
B2
L2 - Half-length of long-side of vessel
B3
L2 - Half-length of long-side of vessel
B3-B
L2 - Half-length of long-side of vessel
C1
*** No Entry Required ***
Min. Thick of Long-Side Plates (t2) - Enter the minimum thickness of the long-side plate used to build the vessel, or the minimum thickness measured for an existing vessel. The short-side thickness value is a required entry for all vessel types. Per Appendix 13, vessels A3 and C1 (Figure 20C and 20K, respectively) are assumed to have equivalent long and short-side thicknesses. Thus, the long-side thickness is not a required entry for these two vessel types.
Long-Side Joint Efficiency Factor (Mid-Side) - Enter the efficiency of the welded joint for vessels with welded joints. This joint efficiency value will be used to adjust the corner and the mid-side allowable stress values. The mid-side joint efficiencies will not be used if there are holes on the side of the vessel. Instead, the ligament efficiencies will be used to adjust the actual stress values. Typical values are: 1.00 Full Radiography 0.85 Spot X - Ray 0.70 No - Radiography For help determining this value, refer to Section VIII, Div. 1, Table UW-12. Threaded Holes in Long-Side Plates - If the plate has uniform or multi-diameter holes, check this option to enter the pitch, diameter, and depth parameters. Ligament efficiency calculations will be performed in order to adjust the calculated actual stress values.
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Rectangular Vessels (App. 13) Center to Center Distance Between Holes - Enter the maximum pitch distance between holes in the side plates of the vessel being analyzed. This pitch distance (P) is shown in the following illustration. This value must be greater than the diameter of the hole
Figure 62: Hole Diameter to Corresponding Lengths and Center-to-Center
Diameter of Hole - Type the diameter (d0, d1, d2) of the hole of corresponding length (T0, T1, T2). If the hole is of uniform diameter, then a value for d0 is the only required entry.
Figure 63: Hole Diameter to Corresponding Lengths and Center-to-Center
The values for d0, d1, and d2 must be entered in decreasing diameter size.
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Rectangular Vessels (App. 13) Depth of Hole - Type the depth (T0, T1, T2) of the hole of corresponding diameter (d0, d1, d2). If the hole is of uniform diameter, then a value for T0 is the only required entry.
Figure 64: Hole Diameter to Corresponding Lengths and Center-to-Center
The sum of the values for T0, T1, and T2 must equal to the entire side thickness. Ligament Efficiencies em / eb - Enter ligament efficiencies for tube spacing. Distance from Neutral Axis ci - Enter the neutral axis distance. Type of Long-Side Reinforcement - Enter the index for the type of reinforcement on the rectangular vessel. None - No reinforcing ring. Bar - Enter the width and thickness of the bar. Section - Enter the moment of inertia, cross-sectional area, and the distance from the shell to the centroid of the beam.
Reinforcing Bar Options Outside Distance from Outside of Vessel - Type the distance from the outer surface of the vessel to the outermost point on the reinforcing bar or beam. Length of Reinforcing Member - For vessel type A5, this entry represents the entire length of the discontinuous reinforcement. No entry is required for other vessel types. In all cases the program includes the vessel wall in the calculation of the moment of inertia. Width of Reinforcing Member - Type the width of the reinforcing member. This value is the distance that the reinforcement remains in contact with the vessel wall. This value cannot be greater than the reinforcement pitch, as that would indicate that the reinforcement if overlapping.
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Reinforcing Section Options Cross-Sectional Area of Reinforcing Member - Type the cross sectional area for the beam section which is being used as reinforcement. Moment of Inertia of Reinforcing Member - Type the moment of inertia for the beam section which is being used as a reinforcement in the direction parallel to the surface of the vessel. Centroid Distance from Outside of Vessel - Type the distance from the surface of the vessel to the centroid of the reinforcing ring. This distance should be measured normal to the vessel surface. Outside Distance from Outside of Vessel - Type the distance from the outer surface of the vessel to the outermost point on the reinforcing bar or beam. Length of Reinforcing Member (If Discontinuous) - For vessel type A5, this entry represents the entire length of the discontinuous reinforcement. No entry is required for other vessel types. In all cases the program includes the vessel wall in the calculation of the moment of inertia. Width of Reinforcing Member - Type the width of the reinforcing member. This value is the distance that the reinforcement remains in contact with the vessel wall. This value cannot be greater than the reinforcement pitch, as that would indicate that the reinforcement if overlapping.
Results The software performs the following types of calculations for rectangular vessels.
Topics
Ligament Efficiency Calculations ................................................... 261 Reinforcement Calculations ........................................................... 262 Stress Calculations ........................................................................ 262 Allowable Calculations ................................................................... 263 Highest Percentage of Allowable Calculations .............................. 263 MAWP Calculations ....................................................................... 263 External Pressure Calculations...................................................... 264
Ligament Efficiency Calculations When the side plates have uniform or multi-diameter holes, ligament efficiency calculations are performed according to Section 13-6. In the case of uniform diameter holes, the ligament efficiency factors em and eb for membrane and bending stresses, respectively, are considered to be the same. In the case of multi-diameter holes (see Figure M), the neutral axis of the ligament may no longer be at mid-thickness of the plate; in this case, for bending loads, the stress is higher at one of the plate surfaces than at the other surface. If the calculated values of em and eb are lower than the entered midpoint joint efficiencies, the calculated stress values are divided by these calculated ligament efficiencies. It is important to note that if the stresses have been adjusted by the ligament efficiencies, then the calculations for the allowable stresses will assume an E value of 1.0. This avoids incorrectly increasing the stress values while decreasing the allowables at the same time.
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Reinforcement Calculations Reinforcement calculations performed for vessels A4, A5, and B2 (Figures D, E, and J), are discussed in section 13-8. The rectangular vessel program only addresses those vessels in which the reinforcement on opposite side plates has the same moment of inertia. Additionally, the reinforcement for vessels A4 and B2 is assumed to be continuous, while A5 is assumed to be non-continuous. The first reinforcement calculation is that of the maximum pitch between reinforcing member center lines. Equation 1 of UG-47 is used to set a basic maximum distance. Using this maximum value, equations (1a)-(1d) in Section 13-8 are used to obtain a maximum value for both the long and short-side plates. The minimum calculated value shall be considered the maximum distance between reinforcement center lines. In addition to the above calculations, the geometry of the reinforcement must be checked. Specifically, the width of the reinforcing members cannot physically exceed the pitch. Once the pitch is determined, the moment of inertia of the composite section (shell and reinforcement) is determined by the Area-Moment method. The moment of inertia calculations are performed for locations where the plate is in compression, and then also performed for locations where the plate is in tension. Equation (2) of Section 13-8 is used to calculate the maximum width of the shell plate which can be used to compute the effective moments of the composite section at locations where the shell plate is in compression. At locations where the shell plate is in tension, an effective width equal to the actual pitch distance is used in the computations.
Stress Calculations Stress calculations are performed for membrane, bending, and total stresses. The calculations are performed for both the inner and outer surface of the long and short-side plates. These actual stress values are displayed along with their allowables in tabular form. A positive (+) stress indicates tensile stress, while a negative (-) stress indicates compressive stress. As previously discussed, the calculated values for the membrane and bending stresses are adjusted by the ligament efficiency calculations if em and eb are less than the joint efficiency E. At the mid-side locations, the stresses are increased by dividing the calculated value by the membrane or bending ligament efficiency. When plates have holes but the ligament efficiencies are higher than the joint efficiency E, there is no adjustment to the stress calculations; the allowables are adjusted by the value E. Calculations performed on stay plates/bars are membrane stresses, and these stresses are used in the MAWP calculations for membrane stresses. Computation of the stresses on end plates is performed if a thickness value for the end plate is input. The calculations are performed per UG-34 with a C factor entered by the user. These stresses are not used in the computation of the MAWP.
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Allowable Calculations Membrane stresses are in general compared to the adjusted allowable stress, SE. For reinforced members, the software compares the membrane stress to the lower of the plate allowable stress or beam allowable stress. Also, when there are holes in the side, the joint efficiency may be set to 1.0 in favor of a membrane efficiency which is factored into the actual stress calculation as necessary. Bending stresses and total stresses are in general compared to 1.5 times the adjusted allowable stress, SE. For reinforced members the program compares the actual stress to the lower of the plate allowable stress or beam allowable stress, and also to the lower of 2/3 times the plate yield stress or beam yield stress. It chooses the lowest of these four combinations as the allowable for reinforced cases. Note also that when there are holes in the side, the joint efficiency at the mid-side may be set to 1.0 in favor of a membrane efficiency which is factored into the actual stress calculations as necessary.
Highest Percentage of Allowable Calculations After performing the actual stress calculation and computing the allowable stresses at all locations, the software computes the highest stress/allowable ratio for each of the three stress types. The software displays the highest percentage of the allowable used and the actual stress value that this percentage relates to.
MAWP Calculations The software calculates the Maximum Allowable Working Pressure (MAWP) for each of the three stress types. The computation of the MAWP is performed by setting the stress equations equal to the allowables and solving for P. The minimum computed P value is considered to be the maximum allowable working pressure for the particular stress type. When analyzing vessels A7-B or A8-B (Figures G and H stayed by bars), an additional pressure rating is computed. If the long-side height is greater than the pitch of the stay bars, then a pressure rating is computed per Eq. (2) of UG-47 with the long-side height substituted for the pitch. If this value of pressure is less than the previously calculated MAWPs, then this becomes the vessel pressure rating. Similarly for vessel B3-B (Figure K stayed by bars), if (L2 + R/2) is greater than the pitch, then an additional pressure rating is computed per Eq. (2) of UG-47 with (L2 + R/2) substituted for the pitch.
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External Pressure Calculations External pressure calculations are performed on vessel A1 and A2 if you have entered a value for the external pressure. These calculations are performed per Appendix 13, Section 13-14 as follows: 1. The external pressure is substituted for the internal pressure, and the calculations discussed previously are performed again. 2. The four side plates and the end plates are checked for stability per equation (1) of 13-14(b). 3. The entire cross section is checked for column stability in accordance with equation (1) from paragraph 13-14(c).
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SECTION 13
Legs and Lugs Home tab: Components > Add New Leg/Lug Analyzes structural members (legs), support lugs and lifting lugs. The following information is required for each of these analysis types: Vessel design internal pressure Design temperature for the attachment Vessel outside diameter Weight of vessel operating and dry Vessel dimensions Additional horizontal force on vessel Location of horizontal force above grade The design temperature for the attachment is used to compute the material properties for attachment being analyzed. In most cases the actual attachment temperature will be different from the vessel design temperature. The controlling stress for support lug and vessel leg calculations is the yield stress. The material yield stress can be looked up in the tables in ASME Section II Part D. The weight of the vessel should be the weight of the vessel while it is operating. This should include operating fluid, trays, insulation etc. Support lug calculations should use the same loading conditions. However since vessels are typically lifted "dry" the empty weight of the vessel should be used when performing lifting lug calculations. There is a separate field for lifting weight of the vessel.
Support Legs The number of vessel legs must be between 3 and 16. The program computes the number of legs for bending and shear of the vessel. CodeCalc must have a valid material from which to determine material properties. You can select the material from the Material Database by selecting the material database lookup button. If a material is not contained in the database, you can enter its specification and properties manually by selecting Tools/ Edit/Add Materials, from the Main Menu. Currently there are 929 structural shapes in the AISC database. CodeCalc is intended to perform unity checks on I-beam and angle type sections. AISC's method for computing unity checks for angle type sections are rather complicated when compared to the corresponding method used for "I" type sections. Each beam section has a strong and weak orientation. If the beam is attached such that the tangent to the vessel is parallel to the beam's strong axis this designation is considered strong, otherwise it is weak. If the legs are cross braced, bending stresses are significantly reduced.
Support Lugs If the number of support lugs to be analyzed is between 2 and 16, CodeCalc assumes that each support lug has two gussets equally spaced about a bolt hole. The distance between gussets is used to determine the bending stress in the lug bottom plate. The lug bottom plate is analyzed as a beam on simple supports, where the support spacing is the gusset spacing. The allowable
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Legs and Lugs stress in bending is 66 percent of the yield stress, per the AISC manual. In addition, the stress in the gusset is one half of the lug force divided by the gusset area. This compression is compared to the AISC compression allowable. Usually when analyzing stresses in the lug plate the stresses in the wall of the vessel at the attachment location should be checked. This can be accomplished by checking the box to perform WRC 107 analysis from within the support lug dialog.
Lifting Lugs There are two types of lifting lug orientations; flat and perpendicular. Flat lugs are generally welded below the top head seam and extend far enough above the seam for the lifting cables to clear the head and its nozzles. Perpendicular lugs (ears) are used to clear some obstruction at or near the top head (such as a body flange) by moving the support point away from the vessel shell. They are also used as tailing lugs. The width of the lug is its dimension in the direction of orientation described above. The length is in the vertical direction relative to the vessel. The length of the welds will also need to be entered. For flat lugs the weld at the bottom will usually be the same as the lug width. For perpendicular lugs the weld length will be the same as the thickness of the lug. CodeCalc will take the square root of the sum of the squares (W, N, and T) to determine the total shearing load. The forces W and N cause bending loads on flat lugs, while W and T cause bending loads on perpendicular lugs. The corner of the weld group is where the stress will be checked.
Baseplates Baseplate thickness calculation is included in the vessel leg analysis for I-beam, pipe, and angle leg only, and can be activated by clicking the Analyze Baseplate check box. The design is based on the method for I-beam leg described in the Pressure Design Manual by D. Moss and is applied to the other leg shapes. CodeCalc will assume the following for all Baseplate Thickness calculations: Strong axis leg orientation. Bolts are installed along the length sides only (B dimension). The leg is attached symmetrically on the baseplate. It is advisable to check the baseplate dimensions using the graphic feature of CodeCalc.
Trunnions A hollow or solid circular trunnion with or without pad reinforcement can be analyzed using the TRUNNION DESIGN module. The main considerations regarding the trunnion design are stresses at the vessel/trunnion junction and on the trunnion itself. Bending stress, shear stress, bearing stress and unity check are calculated and compared with the appropriate allowables. Local stresses at the junction can be analyzed using the WRC 107 Analysis Selection check box. The lifting orientation, vertical and horizontal positions, and the orthogonal input forces are needed for WRC 107 Analysis. CodeCalc assumes that the loads entered act on one trunnion. Typically vessels are lifted with two trunnions thus the load is divided between them. An option is to analyze the trunnion with the maximum load acting on that trunnion during the lift. The program multiplies this lifting load by the importance factor specified by the user. Before the analysis it is advisable to check the trunnion dimensions and the forces' magnitude and direction using the graphic feature in CodeCalc. The program does not subtract corrosion allowance (if any) and then enter the dimensions.
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Legs and Lugs In This Section
Legs and Lugs Tab ........................................................................ 267 Loads Tab ...................................................................................... 272 Lifting Lug Dialog Box .................................................................... 278 Support Lug Dialog Box ................................................................. 281 Vessel Leg Tab .............................................................................. 284 Trunnion Tab ................................................................................. 286 Output ............................................................................................ 288 Leg Results .................................................................................... 289 Baseplate Results .......................................................................... 289 Trunnion Results ............................................................................ 289
Legs and Lugs Tab Item Number - Enter the ID number of the item. This can be the item number on the drawing or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional. Design Pressure - Enter the design pressure at which the vessel will be operating. This value is not used by this module. However, the pressure is used by the WRC107/FEA module. Design Temperature of Attachment - The temperature entered in this box should correspond to the temperature of the attachment in question. It would be reasonable to assume that vessel legs are much cooler than the actual metal temperature of the pressure vessel. The controlling stress for leg and support lug design is the yield stress of the material at the leg/lug temperature. If the attachment is not at ambient, enter the yield stress at that temperature. This value is available in ASME Section II Part D. Conversely, vessel lifting lugs use the basic allowable stress of the material for their design. CodeCalc will use the allowable stress of the metal at the design temperature. Outside Diameter of Vessel - Enter the outside diameter of the vessel to which the supports are attached. Any factors such as external corrosion should be accounted for at this time. The software assumes the vessel is one diameter from the top to the bottom of the vessel. Shell Thickness - Enter the shell thickness. This input is used in the case of a support lug with full reinforcement ring and for the WRC 107 analysis of the trunnion. Shell thickness is required to compute the area and moment of inertia of the shell-ring junction. Shell Corrosion Allowance - Enter the shell corrosion allowance. This input, along with the shell thickness is used only in the case of a support lug with a full reinforcement ring. Shell thickness is required to compute the area and Moment of Inertia of the shell-ring junction. Tangent-to-Tangent Length of Vessel - Enter the tangent-to-tangent length of the vessel. This input, in addition to the leg length or the height of bottom tangent, is used by the software to compute the vessel centroid. Shell Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Legs and Lugs Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Type of Analysis - Select from the following analysis type: Support Lug - Indicates that the vessel is supported by support lugs. Selecting this option prompts you for all of the information necessary to determine the stresses in these types of supporting attachments. For more information, see Support Lug Tab (see "Support Lug Dialog Box" on page 281). Vessel Leg - Indicates that the vessel is supported on legs. Selecting this option prompts you for all of the information necessary to perform an AISC unity check on the vessel legs. Along with the leg design, you can also design the baseplate and anchor bolts. For more information, see Vessel Leg Tab (on page 284). Lifting Lug - Indicates that the vessel is to be lifted by lug type attachments. Selecting this option prompts you for information pertaining to the lifting lugs. For more information, see Lifting Lug Tab (see "Lifting Lug Dialog Box" on page 278). Trunnion - Indicates that a vessel is to be lifted by a trunnion. Selecting this option prompts you for information pertaining to trunnion design. You can also choose to perform the local stress analysis automatically on the trunnion, per the WRC 107 method. For more information, see Trunnion Tab (on page 286). Analyze Baseplate? -Indicates that you are designing the baseplate and anchor bolts according to Moss and Bednar. For more information about the options that appear, see Baseplate (on page 269).
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Baseplate Specifies parameters for baseplates.
Design Method Moss - This design method considers the following: The Total Number of Bolt per Base Plate should be an even number. The program assumes that the bolts are located along the length (B) of the base plate as shown in the figure. In case there is no wind/earth quake/horizontal loads, the Number of Bolt in Tension per Base Plate is not required. If there is wind/earth quake/horizontal loads, the Number of Bolt in Tension per Base Plate should be the number of bolts along one length dimension, shown as three bolts in the figure. When this input is left blank, its value is assumed to be half of the total number of bolts. The program assumes the leg is attached symmetrically on the base plate. The Distance from the Edge of the Leg to the Bolt Hole, the "z" dimension, is same along the width and along the length.
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Legs and Lugs AISC - In this method, the thickness of the baseplate is calculated by assuming the baseplate is in compression state. The anchor bolts are sized to resist the lifting force/moment. Please refer to second edition of Pressure Vessel Design Handbook by Bednar page 153. In the Analyze mode, the baseplate thickness is calculated using the input baseplate dimensions (B &D). However, in the Optimize mode, the baseplate thickness is calculated by maximizing the use of the concrete strength. Please refer to AISC Handbook page 3-106. The Total Number of Bolt per Base Plate is assumed to carry the entire lifting load on the baseplate. It is up to the user to specify the location of each bolt. The Number of Bolt in Tension per Base Plate input is not required. The Distance from the Edge of the Leg to the Bolt Hole, the "z" dimension, is not required.. The program assumes the leg is attached symmetrically on the base plate. Design - In the Analyze mode, the baseplate thickness is calculated using the input baseplate dimensions (B &D). However, in the Optimize mode, the baseplate thickness is calculated by maximizing the use of the concrete strength. Please refer to AISC Handbook page 3-106.
Baseplate Baseplate Length, B - Specifies the length (B) of the baseplate. Baseplate Width, D - Specifies the width (D) of the baseplate. Baseplate Thickness - Specifies the thickness of the baseplate. Baseplate Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Bolts Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
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Legs and Lugs Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Distance from the Edge of the Leg to the Bolt Hole Center, Z - Specifies the distance from the edge of the leg to the bolt hole center. Thread Series - The following bolt thread series tables are available: TEMA Bolt Table UNC Bolt Table User specified root area of a single bolt TEMA Metric Bolt Table British, BS 3643 Metric Bolt Table Irrespective of the table used, the values will be converted back to the user selected units. TEMA threads are National Coarse series below 1 inch and 8 pitch thread series for 1 inch and above bolt nominal diameter. The UNC threads available are the standard threads. Nominal Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the Bolt Root Area box. Bolt Corrosion Allowance - If there is any corrosion allowance for the bolts, then enter it here. The nominal bolt size is corrected for this allowance. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this box. Total Number of Bolts per Baseplate - Specifies the number of bolts per baseplate. Number of Bolts in Tension per Baseplate - Specifies the number of bolts in tension per baseplate. Select Bolt Size - Select the bolt size from the list.
Concrete Properties Nominal Compressive Stress of Concrete - Enter the Nominal Compressive stress of the Concrete to which the basering/baseplate is bolted. This value is f'c in Jawad and Farr or FPC in Meygesy. A typical entry is 3000 psi. Water Content, U.S. Gallons
f'c, 28 day Ultimate
per 94-lb Sack of Cement
Compressive Strength, psi
7.5
2000
6.75
2500
6
3000
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Legs and Lugs
Loads Tab Specifies parameters for leg and lug loads. Additional Horizontal Force on Vessel - Enter the additional horizontal force exerted on the vessel due to external loads. An example of such would be the reaction imposed by the thermal expansion of a piping system. The location of this distance above the base point will also need to be entered. A Vessel on Legs:
A Vessel on Lugs:
Location of Horizontal Force Above Base Point - Specifies the location of the horizontal force. Empty Weight of Vessel - Specifies the weight of the vessel without contents. Operating Weight of Vessel (total vertical load) - Specifies the total weight of the vessel. This weight should include all operating fluids, equipment loads, and other equipment attached to the vessel. Height of Bottom Tangent Above Base Point - Enter the distance from the ground to the bottom tangent of the vessel. If you are performing a leg analysis, this distance should be equal to the length of the legs. This value will be used along with the tangent-to-tangent length to determine the centroid where the wind loads and seismic shear loads are applied. These horizontal shear forces cause bending around the legs and support lugs. Occasional Load Factor (AISC A5.2) - With many types of construction codes an occasional load factor can be used to increase the allowable stress for an event that is considered
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Legs and Lugs occasional in nature. Such occasional loads are Wind, Seismic and the lifting of a vessel. The occasional load factor will be multiplied by other terms in the allowable stress equation to get the overall allowable. If you do not wish to take credit for such an increase in the allowable, enter 1 in this field. The default is 1.33. Apply Wind Loads to Vessel? - Analyzes the wind or seismic effect on the tower vessel. The software prompts you to enter the necessary information to calculate the wind pressure acting on the vessel. The wind parameters are from ASCE #7. If you are using a different wind code, calculate the wind pressure manually and enter that value in the applicable field. For more information, see Wind Loads (on page 273). Apply Seismic Loads to Vessel? - Analyzes the seismic effect on the tower vessel. With the operating weight and the seismic zone or zone coefficient, the software calculates the lateral force acting at the center of the vessel. For more information, see Seismic Zone Identifier in the Seismic Loads (on page 276).
Wind Loads Specifies parameters for wind loads. Additional Area (Insulation Area, Structures) - You may want to consider the additional area exposed to the wind from piping, platforms, insulation and so on. CodeCalc will automatically compute an effective diameter with the input diameter known. Wind Pressure on Vessel - If your vessel specification calls out for a constant wind pressure design, enter appropriate wind pressure here. Most Wind Design codes have minimum wind pressure requirements, so check those carefully. The wind pressure will be multiplied by the area calculated by the program to get a shear load and a bending moment. If you enter a positive number, CodeCalc will use this number regardless of the information in the following boxes.
Wind Design Code Input Wind Design Code - You can choose the following wind design standards: ASCE 7-93 ASCE 7-95 ASCE 7-98/02 / IBC 2003 UBC 94/97 For a different wind code, you can compute and enter the design wind pressure and the program will multiply the wind pressure by the area to compute the wind load. Force Coefficient (Cf) - Enter the force coefficient for vessel here. This factor accounts for the shape of the structure. This factor is known as pressure coefficient, Cq in the UBC wind code. The acceptable range of input is between 0.5 and 1.2. This can be seen as: ANSI A58.1 refer to Table 12 ASCE 7-93 refer to tables 11-14, p21-22 ASCE 7-95, refer to tables 6-6 to 6-10, p32-33 ASCE 7-98, refer to tables 6-9 to 6-13 ASCE 7-2002, refer to tables 6-18 to 6-22, p68-72 UBC-1997 code, refer to table 16-H. Importance Factor (I) - Enter the value of the importance factor that you want the program to use. The importance factor accounts for the degree of hazard to life and property. Please note
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Legs and Lugs the program will use this value directly without modification. Values of typical importance factors are listed below for ASCE 7-93, ASCE 7-95/98/02 and UBC 1997 standards. ASCE7-93: Following values are used for ASCE 7-93. In general this value ranges from .95 to 1.11. Category
100 mi from Hurricane Oceanline
At Oceanline
I
1.00
1.05
II
1.07
1.11
III
1.07
1.11
IV
0.95
1.0
Category Classification: I - Buildings and structures not listed below II - Buildings and structures where more than 300 people congregate in one area III - Buildings designed as essential facilities, hospitals and so on. IV - Buildings and structures that represent a low hazard in the event of a failure Most petrochemical structures are 1, Importance I. ASCE-7-95/98/02: In general this value ranges from .77 to 1.15. It is taken from table 6-2 of the ASCE 95 standard or table 6-1 from the 98 standard. Category
Importance Factor (I)
I
0.87
II
1.00
III
1.15
IV
1.15
In the 98 standard for Wind Speeds > 100 mph for category I, the importance factor can be 0.77. Category Classification: I - Buildings and other structures that represent a low hazard to human life in the event of failure II - Buildings and structures except those listed in categories I, III and IV III - Buildings and structures that represent a substantial hazard in the event of a failure IV - Buildings designed as essential facilities, hospitals etc. Most petrochemical structures are 1, Importance I. UBC: UBC 1997 code values are listed as follows:
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Category
Importance Factor (I)
I, Essential facilities
1.15
II, Hazardous facilities
1.15
III, Special occupancy structures
1.00
IV, Standard occupancy structures
1.00
CodeCalc User's Guide
Legs and Lugs Basic Wind Speed (V) - Enter the design value of the wind speed. These will vary according to geographical location and according to company or vendor standards. Here are a few typical wind speeds in miles per hour. 85.0 miles per hour 100.0 miles per hour 110.0 miles per hour 120.0 miles per hour Enter the lowest value reasonably allowed by the standards you are following, because the wind design pressure (and thus force) increases as the square of the speed. Wind Exposure - Reflects the characteristics of ground surface irregularities for the site at which the structure is to be constructed. For ASCE codes, the exposure categories are as follows, Exposure Category
Description
A
Large city centers with at least 50% of the buildings having a height in excess of 70 feet.
B
Urban and suburban areas, wooded areas, or other terrain with numerous closely spaced obstructions having the size of single family dwellings.
C
Open terrain with scattered obstructions having heights generally less than 30 feet. This category includes flat, open country and grasslands.
D
Flat, unobstructed coastal areas directly exposed to wind flowing over large bodies of water. Most petrochemical sites use a value of 3 (exposure C).
UBC Exposure Factor UBC Exposure Factor is defined in UBC-91 Section 2312: Exposure Category
Description
B
Terrain with building, forest or surface irregularities 20 feet or more in height covering at least 20 percent or the area extending one mile or more from the site.
C
Terrain which is flat and generally open, extending one-half mile or more from the site in any full quadrant.
D
The most severe exposure with basic wind speeds of 80 mph or more. Terrain which is flat and unobstructed facing large bodies of water over one mile or more in width relative to any quadrant of the building site. This exposure extends inland from the shoreline 1/4 mile or 0 times the building (vessel) height, whichever is greater.
Most petrochemical sites use a value of 3, exposure C. This value is used to set the Gust Factor Coefficient (Ce) found in Table 16-G. Type of Hill - See ASCE 7-95 Fig. 6-2 for detail.
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Legs and Lugs None 2-D Ridge 2-D Escarpment 3-D Axisym. Hill Height of Hill or Escarpment (H) - Enter the height of the hill or escarpment relative to the upwind terrain. See ASCE 7-95 Fig. 6-2 for detail -- H. Distance to Site (x) - Enter the distance (upwind or downwind) from the crest to the building site. See ASCE 7-95 Fig. 6-2 for detail -- x. Distance to Crest (Lh) - Enter the distance upwind of the crest to where the difference in ground elevation is half the height of the hill or escarpment. See ASCE 7-95 Fig. 6-2 for details -- Lh. Natural Frequency of the Structure (Fn) - Enter the natural frequency for the structure. The program will use ASCE 7-95 part 6.6 category III if Fn less than 1.0 Hz or TANTAN/OD > 4.0. Damping Factor (beta) - Enter the damping ratio for the structure if you like to use ASCE 7-95 part 6.6 category III (if Fn less than 1.0 Hz or TANTAN/OD > 4.0).
Seismic Loads Specifies parameters for seismic loads. Seismic Zone Identifier - Select the seismic zone from the list. For seismic design of vessels, CodeCalc uses the following tables of Coefficients. These coefficients are taken from the Uniform Building Code (1988). Seismic Zone
Cs
0
0.0
1
0.069
2a
0.138
2b
0.184
3
0.275
4
0.367
The Cs factor from the chart will be multiplied by the operating weight of the vessel to produce a horizontal shear force which acts midway up the vessel.
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Legs and Lugs User Entered Seismic Factor Cs - If the Seismic Zone Identifier values are not satisfactory, enter your own value of Cs in the User Entered Seismic factor box. This value can be between 0.0 and 0.5. The following chart shows the various seismic zones.
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Lifting Lug Dialog Box Specifies parameters for lifting lugs.
Lifting Lug Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Lug Orientation to Vessel - Select the orientation for the lug. Flat - Indicates that the lug extends in the same direction as the vessel axis. This is a flat orientation.
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Legs and Lugs Perpendicular - Indicates that the lug extends radially away from the vessel wall. These lugs are referred to as ear type lugs. They are typically used on the tops of horizontal vessels. If you are working with a perpendicular lug and there will be no bending stresses in the lug, you will need to set the offset dimensions (moment arms) to 0. The program will run, but may give some warnings. This type of lifting lug would be one on the top of a horizontal vessel and the vessel would be lifted by a spreader bar equally distributing the weight load directly over each lug. Thus there would be no bending. Contact Width or Height (Perp. Lug) of Lifting Lug (w) - The width of the lug is its dimension in the direction of orientation described in the lug orientation to vessel cell. For a perpendicular lifting lug this is the total height of the lug. Thickness of Lifting Lug (t) - Enter the thickness of the plate from which the lifting lug was constructed. Diameter of Hole in Lifting Lug (dh) - Most lifting lugs have a circular hole cut or drilled into them. Enter the diameter of this hole. Radius of Semi-circular Arc of Lifting Lug (r) - Enter the radius of the semi-circular part of the lifting lug where the hole is located. Typically this will be circular on flat lugs and semi-circular on perpendicular lugs. Height of the Lug from Bottom to Center of Hole (h) - Enter the distance along the axis of the vessel from the center of hole to the bottom of the lug. Offset from Vessel OD to Center of Hole (off) - Enter the distance from the center of the hole to base of the lifting lug. For perpendicular lugs, this will be to the vessel OD. If the orientation is flat, this will be 1/2 the thickness of the lug. Minimum thickness of Fillet Weld around Lug - This minimum is usually the distance from the root to the surface of the fillet weld (root dimension), and is not the fillet weld leg size. Length of weld along side of Lifting Lug (wl) - Enter the length of the long welds on the side of the lifting lug. CodeCalc will multiply this value by two when determining the weld area. Length of Weld along bottom of Lifting Lug (wb) - Enter the length of the short weld. This is usually the bottom weld.
Lift Information and Loads on one Lug Lift Orientation (optional) - Enter the vessel lift orientation, for the lifting lug/trunnion analysis. This value is only used for information purpose. Axial Force - Enter the component of the force on the lifting lug/trunnion, along the axis of the vessel. Before the version 6.3 of CodeCalc and 4.2 of PVElite, this load was computed from the weight of the vessel. Now, you should enter the corresponding load depending upon the lift position and the lug/trunnion arrangement. CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 (or more) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift.
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Legs and Lugs The program multiplies this lifting load by the importance factor specified by the user.
Normal Force - Enter the component of the force on the lifting lug/trunnion, perpendicular to the wall of the vessel. This load will cause an axial stress on a perpendicular lug and a bending stress on a flat lug. CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 (or more) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift. The program multiplies this lifting load by the importance factor specified by the user. For the horizontal lift position, this load will include part of the weight of the vessel. Tangential Force - Enter the component of the force on the lifting lug/trunnion tangent to the wall of the vessel. This load will cause a major axis bending stress on a perpendicular lug and a minor axis bending stress on a flat lug. CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 (or more) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift. The program multiplies this lifting load by the importance factor specified by the user. Impact Factor - When the vessel is lifted from the ground, it may be yanked suddenly. The impact factor takes this into account. This value typically ranges from 1.5 to 2.0, although values as high as 3.0 may be entered in. The program multiplies the lifting loads by the impact factor.
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Support Lug Dialog Box Specifies parameters for support lugs. Lug With Full Reinforcing Rings? - Indicates that the lug includes full reinforcing rings. Number of Support Lugs - Enter the number of support lugs on which the vessel is supported. This number must be greater than 2 and less than 16. Lug distance from Base Point - Enter the distance from grade to the centroid of the support lug attachment weld. This is used to determine the reaction load on each support lug.
Distance from OD to Lug MidPoint (dlug) - Enter the distance from the outside wall of the vessel to where the support lug attaches/rests on/to the supporting member. This distance should be as short as possible to minimize bending on the support lug and the vessel wall. Force Bearing Width (wfb) - Enter the force bearing width. This is the width for bearing support. Radial Width of Bottom Plate (wpl) - Enter the radial width of the support lug. This distance is how far from the vessel wall the plate extends. Effective Force Bearing Width (lpl) - For lugs with bottom plate and no continuous rings, this value is typically equal to the distance between gussets plus two times the gusset plate thickness. For support lugs with a continuous top and bottom rings, enter the length of the bottom plate located on a support.
Thickness of Bottom Plate (tpl) - Enter the thickness of the plate on which the gussets rest. The bottom support plate is analyzed as a beam on simple supports where the support spacing is the distance between gussets. The allowable stress is 66% of the yield stress per the AISC steel construction manual. Distance between Gussets (dgp) - Enter the gusset spacing in this box. CodeCalc assumes that support lugs have two gussets, equally spaced about a bolt hole (support point). Mean width of Gussets (wgp) - Enter the average width of the gusset plate. The width is radially from the OD of the vessel. If the top and bottom of the gussets are different widths, add them up and divide the result by 2. Use the current units.
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Legs and Lugs Height of Gussets (hgp) - Enter the distance along the axis of the vessel that the gusset plate extends. This length will be used in the AISC formulation to determine the stress in the gussets. Thickness of Gussets (tgp) - Enter the thickness of the gusset plate in the current units. Radial Width of Top Plate/Ring (wtp) - The radial width of the top bar/ring is how far from the vessel wall the top plate/ring extends. If there is no top bar/ring, enter 0 here. Thickness of Top Plate/Ring (ttp) - Enter the thickness of the top bar plate/ring in the current units. If there is no top bar plate or top ring, enter 0 here.
WRC 107 Input Perform WRC-107 Analysis? - Indicates whether or not to perform WRC 107 calculations on the Support Lug to Vessel junction. WRC 107 only addresses rectangular, square or round attachment shapes, but other shapes (such as support lug) can be modeled by converting to an equivalent rectangle which has: The same moment of Inertia The same ratio of length to width of the original attachment. Program uses this approach to convert the lug into an equivalent rectangle. This approach is referenced in WRC bulletin 198 by Dogde as, simple and direct, but is not derived by any mathematical or logical reasoning. So, very large or critical loads should, be examined in depth. Pad Width/Length (Optional) - The reinforcing pad width is measured along the circumferential direction of the vessel. The pad width must be greater than attachment width. The length of the attachment is measured along the long axis of the vessel.
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Legs and Lugs If the box is checked to perform the analysis and the pad properties are entered in, the program will compute the stresses at the edge of the attachment and the edge of the pad. When computing the stresses at the edge of the attachment, program adds the pad thickness to the shell thickness.
Pad Thickness (Optional) - Enter the thickness of the pad.
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Vessel Leg Tab Specifies parameters for vessel legs. Number of Legs - Enter the number of legs attached to the vessel. This number must be greater than or equal to 3 and less than 16. CodeCalc will determine the effective number of legs for bending and shear of the vessel. Length of Legs - Enter the distance from the bottom leg support point to the attachment point on the vessel. This length term is used in determining the legs resistance to bending. Long legs are more likely to buckle than shorter legs. In order to eliminate torsional modes of vibration, legs in excess of about 10 feet should be crossbraced.
Effective Leg End Condition Factor K (used in Kl/r) - Enter in the value of K used as the effective end condition. This value usually ranges from .2 to 2.10. For design of pressure vessel legs a value of 1.0 is commonly used. If your design specs call out for a different value enter it here. End Condition
Theoretical K
Recommended K
Fixed - Fixed
.5
.65
Fixed - Pinned
.7
.80
Fixed - Trans
1.0
1.20
Pinned - Pinned
1.0
1.00
Fixed - Rotates
2.0
2.10
Pinned - Rotates
2.0
2.00
If this value is out of range, CodeCalc will use 1.0. AISC Member Designation (ie. L2X2X0.2500) - Enter the AISC shape name of the member used to construct the vessel. The program uses the name to look up various properties of the section from the AISC steel construction manual. to display the AISC Database dialog box. For more information, see AISC Database Click Dialog Box (on page 285). Orientation to the Vessel Axis - Each I-beam and channel has a strong and weak orientation. This means that these sections are more easily bent around one as opposed to the other. If the
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Legs and Lugs member is attached such that the tangent to the vessel is parallel to the beams strong axis, choose strong, otherwise choose weak. If the member is an angle and it is attached to with one leg welded to the vessel or one flat welded to the vessel, choose strong. If both legs are welded to the vessel choose diagonal. Leg Centerline Diameter (optional) - Enter the distance between the centerlines of two legs that are opposite to one another. If there are an odd number of legs (therefore no two are opposite), then enter the diameter of a circle drawn through the centerlines of the legs. If this field is left blank then program will add half the leg section length to the vessel outer diameter. This input is only used to compute the forces and moments at the vessel-leg junction, which are needed for performing local stress analysis (WRC-107). Are the Legs Cross Braced? - Indicates that the legs are cross braced. Cross bracing effectively stiffens the legs. Thus they will experience a minimum of bending stress. It is recommended that legs greater than 8 or 10 feet in length be cross braced. Are the Legs Pipe Legs - Indicates that the legs are pipe legs. Pipe Legs Inside Diameter - Enter the inside diameter for the pipe legs. You must account for any corrosion allowance to the inner or outer diameters when you enter this value. The inside diameter must be less than the outside diameter. Pipe Legs Outside Diameter - Enter the outside diameter for the pipe legs. You must account for any corrosion allowance to the inner or outer diameters when you enter this value. The inside diameter must be less than the outside diameter.
AISC Database Dialog Box Specifies parameters for selecting an AISC member from the database. Click + to expand the entries. Click - to collapse the entries
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Trunnion Tab Geometry
Trunnion Type - Indicates the type of trunnion to analyze. This input is required for performing shear and bending stress calculation, and the WRC 107 analysis. Trunnion Outside Diameter - Specifies the outer diameter of the trunnion. Trunnion Thickness - Specifies the thickness of the trunnion. Projection Length - Specifies the projection length of the trunnion. Bail/Sling Width - Specifies the bail or sling width of the trunnion. Reinforcement - Specifies the trunnion reinforcement. This input is required for performing the WRC 107 analysis. Pad Outside Diameter - Enter the outside diameter of the reinforcing pad along the surface of the vessel. The pad diameter is used to calculate the stresses at the edge of the reinforcing pad using WRC 107. Pad Thickness - Enter the thickness of the reinforcing pad. In the WRC 107 method the vessel thickness used is the thickness of the vessel plus the pad thickness. Ring Outside Diameter - Specifies the outside diameter of the ring. Ring Thickness - Specifies the thickness of the ring.
Lift Information and Loads on one Trunnion Lift Orientation (optional) - Enter the vessel lift orientation, for the lifting lug/trunnion analysis. This value is only used for information purpose.
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Legs and Lugs Axial Force - Enter the component of the force on the lifting lug/trunnion, along the axis of the vessel. Before the version 6.3 of CodeCalc and 4.2 of PVElite, this load was computed from the weight of the vessel. Now, you must enter the corresponding load depending upon the lift position and the lug/trunnion arrangement. CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 ( or more ) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift. The program multiplies this lifting load by the importance factor that you specify.
Normal Force - Enter the component of the force on the lifting lug/trunnion, perpendicular to the wall of the vessel. This load will cause an axial stress on a perpendicular lug and a bending stress on a flat lug. CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 ( or more ) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift. The program multiplies this lifting load by the importance factor that you specify. For the horizontal lift position, this load will include part of the weight of the vessel. Tangential Force - Enter the component of the force on the lifting lug/trunnion tangent to the wall of the vessel. This load will cause a major axis bending stress on a perpendicular lug and a minor axis bending stress on a flat lug.
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Legs and Lugs CodeCalc assumes that the magnitude of the applied loads is acting on one lug or one trunnion. Typically vessels are lifted with 2 ( or more ) lifting lugs/trunnion, thus the load is divided between them. An option is to analyze the lug/trunnion with the maximum load, acting on that lug/trunnion, during the whole lift. The program multiplies this lifting load by the importance factor that you specify. Impact Factor - When the vessel is lifted from the ground, it may be yanked suddenly. The impact factor takes this into account. This value typically ranges from 1.5 to 2.0, although values as high as 3.0 may be entered. The program multiplies the lifting loads by the impact factor.
WRC 107 Input Perform WRC-107 Analysis on Trunnion? - Indicates that WRC-107 analysis will be performed on the trunnion.
Output CodeCalc produces three basic types of results in the LEG & LUG module: Results for Legs, using the methods described by AISC Results for Lifting Lugs, using basic engineering principles Results for Support Lugs, using AISC methods, formulae from pressure vessel textbooks and other engineering reference texts. The input for this module includes some basic vessel parameters such as the vessel tangent-to-tangent length, the diameter and the height of the bottom tangent above grade. If you are performing a Leg or Support Lug calculation, the program follows these basic steps in order to determine the loads. For evaluation of wind loads: 1. Determine the elevation of the top and bottom seam of the vessel. 2. Determine the wind pressure at both elevations, and take the average. 3. Determine the effective diameter of the vessel and its area. 4. Compute the centroid of the vessel. 5. Resolve the wind pressure and the area at the centroid. For evaluation of seismic loads: 1. Determine the seismic zone factor from UBC table 23-I or use the one the user gave. 2. Multiply this value times the operating weight of the vessel. 3. Apply this load at the centroid of the vessel. If both types of loadings are considered, CodeCalc computes both and then choose the maximum of the two.
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Leg Results When a leg analysis is performed, CodeCalc reads entire data from the structural database (AISC89.BIN). The resulting leg loads are compared to the allowable leg compression loads as outlined in AISC paragraph 1.5.1.3. Either the Kl/r > Cc or Kl/r < Cc formula will be shown as appropriate. The combination of stresses due to bending and compression will be compared to the allowable per AISC 1.6.1. This is generally termed the AISC unity check. If the result is greater than 1.0, it implies that the member has failed.
Baseplate Results Baseplate analysis produces the following results: The thickness requirement is calculated using the 1.5 allowable plate bending stress and compared to the input thickness. The concrete bearing pressure is compared to the input allowable stress The anchor bolt size is analyzed at the bending level (D. Moss) and the overall vessel moment equilibrium (H. Bednar). In the absence of tension in the bolts, you should choose a practical bolt size.
Trunnion Results The ring outer diameter and thickness are not used in the calculations; they are used to display a picture only. There are four passing criteria used to calculate the trunnion design bending stress, shear stress, bearing stress and the Unity Check. The following allowables are used: Bending Stress: 0.66 *Sy*Occfac Shear Stress: 0.40 *Sy*Occfac Bearing Stress: 0.75 *Sy*Occfac WRC 107 Analysis- local stresses at 8 points are evaluated and compared with the allowable (1.5 * Sallow). For more information, see the WRC 107 module.
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SECTION 14
Pipes and Pads Home tab: Components > Add New Pipe/Pad Calculates the required wall thickness and area of replacement for ANSI B31.3 intersections. These area of replacement rules are based on the 1987 edition of ANSI B31.3 Chemical Plant and Petroleum Refinery Piping Code. Extruded outlet headers are also analyzed.
In This Section
Pipes and Pads Tab (Pipes and Pads) .......................................... 291 Output ............................................................................................ 300
Pipes and Pads Tab (Pipes and Pads) Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. Design Internal Pressure - Enter the design pressure of the ANSI B31.3 intersection. This should be the pressure at which the system operates continuously. Most of the internal computations for areas, wall thickness, and so on, involve the design pressure. Reinforcing Pad Present? - Check this box if the intersection being analyzed has a reinforcing pad. When this option is selected, the software will determine the area(s) available in the pad within the appropriate limits of reinforcement. In addition, the software will also report the required pad diameter based on the given pad thickness and the required pad thickness based on the given diameter. Reinforcing Pad Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Pad Diameter Along Vessel Surface - Enter the length of the reinforcing element along the longitudinal axis of the header.
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Pipes and Pads Pad Thickness - Enter the length of the reinforcing element along the longitudinal axis of the header. Is There an Extruding Outlet? - Check this box if the branch connection for this intersection is formed by the extrusion process. When this option is selected, the software prompts you to enter information required to determine the area in the extruded outlet. Thickness, Tx, of extruded outlet - The dimension TX of an extruded outlet header is the corroded finished thickness, which is measured at a height equal to the radius of curvature above the outside surface of the header. Height, Hx, of extruded outlet - Enter the height of the extruded outlet (HX), which is the dimension HX of an extruded header. This distance must be greater than or equal to the radius of curvature RX of the outlet. Inside Diameter, Dx, of extruded outlet - Enter the inside diameter of the extruded outlet (DX), which is measured at the level outside of the header. The software will automatically adjust the wall thickness of the outlet if the mill tolerance and/or the corrosion allowance is specified.
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Pipes and Pads Results of curvature, Rx, of extruded outlet - Enter the radius of curvature of the external contoured part of the extruded outlet (RX), which is measured in the plane containing the axes of both the header and the branch.
Figure 65: Pipe and Pad Module Geometry
Figure 66: Pipe and Pad Module Geometry
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Figure 67: Extruded Outlet
Branch Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Branch Material Type - Select the type of material used for the branch. Branch Dimension Basis - Select the branch dimension basis. If the actual outside diameter is known, select Actual (OD). If the nominal schedule is known, select Nominal. Pipe Actual Diameter - If you selected Actual (OD) in the Branch Dimension Basis list, enter the actual outside diameter of the pipe. If you selected Nominal in the list, enter the nominal outside diameter. For example, type 10 for a 10-inch pipe. Actual Thickness of Branch - If you specified Actual (OD) as the thickness basis, then enter the actual wall thickness of the pipe; otherwise, enter 0.0 for nominal basis. The software will reduce the wall thickness according to B31.3 if appropriate values are entered for mill tolerance or corrosion allowance.
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Pipes and Pads Nominal Thickness of Branch - Select the schedule for the branch or header wall only if you selected Nominal for the diameter and thickness basis. Otherwise, specify the Actual Thickness of Header. Mill Undertolerance, percent (ie. 12.5) - The mill undertolerance accounts for manufacturing deficiencies when pipe is produced. For example, if you enter 12.5, then the wall thickness of the pipe will be multiplied by (100 - 12.5)/100 or .875. This is essentially a reduction in wall thickness. Valid entries are between 0 and 99%. Branch Corrosion Allowance - Enter the estimated allowance for corrosion in this field. The difference of (wall thickness - (corrosion allowance + mill tolerance)) must be greater than 0. Basic Quality Factor for Longitudinal Joints - The basic quality factor is used in the wall thickness calculations for pipes under internal pressure only. These factors are listed in the ANSI B31.3 piping code Table A-1B. For seamless and fully radiographed pipe, this value is 1.0. For electric resistance welded and spot welded materials it is usually 0.85. Angle Between Branch and Header (usually 90) - Enter the angle between the centerline direction vector of the branch and header. Typically, this is 90-degrees. The piping codes do not allow "hillside" type arrangements. This angle is referred to as beta and is pictured in the user's guide. This is the smaller angle between axes. Does the Branch Penetrate a Header Weld? - Select this option if the branch pipe passes through a weld seam on the header pipe. Paragraph 304.3.3 in the ANSI piping code states that if the branch does not penetrate a header weld, the value of 1.0 for the joint efficiency is used in the appropriate wall thickness equation. However, if the branch does penetrate a header weld, the user-defined value of E is used in the thickness equation. Rate the Attached B16.5 Flange? - Opens the Flange Rating dialog box so that you can define the class and grade of the attached flange. The software uses the class and grade, along with the temperature, to rate the flange using the tables in ANSI B16.5. Class for Attached B16.5 Flange - Enter the class of the flange attached to the nozzle neck. You can choose from the following classes of flanges: CL 150 CL 300 CL 400 CL 60 CL 90 CL 1500 CL 2500 The Flange Rating dialog box displays only if you select Rate the attached B16.5 flange? Grade of Attached B16.5 Flange - Select the nozzle flange material grade (group). The available flange grades are listed in the following tables. There are certain advisories on the use of certain material grades. We recommend that you review the cautionary notes in the ANSI B16.5 code.
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Pipes and Pads Table 1A List of Material Specifications (ASME B16.5-2003) Material Group 1.1
1.2
Nominal Designation
Forgings
Castings
Plates
C-Si C-Mn-Si
A 105 A 350 Gr. LF2
A 216 Gr. WCB
C-Mn-Si-V 3½ Ni
A 350 Gr. LF 6 Cl.1 A 350 Gr. LF3
A 515 Gr. 70 A 516 Gr. 70 A 537 Cl. 1
C-Mn-Si C-Mn-Si-V 2½Ni 3½Ni
1.3
C-Si C-Mn-Si 2 ½Ni 3 ½Ni C-½Mo
A 352 Gr. LC2 A 352 Gr. LC3
A 203 Gr. B A 203 Gr. E
A 352 Gr. LCB
A 515 Gr. 65 A 516 Gr. 65 A 203 Gr. A A 203 Gr. D
A 217 Gr. WC1 A 352 Gr. LC1
1.4
C-Si C-Mn-Si
A 350 Gr. LF1 Cl. 1
1.5
C-1/2Mo
A 182 Gr. F1
1.7
½C-½Mo Ni-½Cr-½Mo ¾Ni-¾Cr-1Mo
A 182 Gr. F2
1.9
1¼Cr-½Mo 1¼Cr-½Mo-Si
A 182 Gr. F11 Cl.2
1.10
2¼Cr-1Mo
A 182 Gr. F22 Cl.3
1.11
Cr-½Mo
1.13
5Cr-½Mo
1.14
9Cr-1Mo
A 182 Gr. F9
A 217 Gr. C12
1.15
9Cr-1Mo-V
A 182 Gr. F91
A 217 Gr. C12A
A 387 Gr. 91 Cl.2
1.17
1Cr-½Mo 5Cr-½Mo
A 182 Gr. F12 Cl.2 A 182 Gr. F5
2.1
18Cr-8Ni
A 182 Gr. F304 A 182 Gr. F304H
A 351 Gr. CF3 A 351 Gr. CF8
A 240 Gr. 304 A 240 Gr. 304H
16Cr-12Ni-2Mo
A 182 Gr. F316 A 182 Gr. F316H A 182 Gr. F317
A 351 Gr. CF3M A 351 Gr. CF8M
2.2
18Cr-13Ni-3Mo 19Cr-10Ni-3Mo
296
A 350 Gr. LF 6 Cl.2
A 316 Gr. WCC A 352 Gr. LCC
A 515 Gr. 60 A 516 Gr. 60 A 204 Gr. A A 204 Gr. B A 217 Gr. WC4 A 217 Gr. WC5 A 217 Gr. WC6 A 217 Gr. WC9
A 387 Gr. 11 Cl.2 A 387 Gr. 22 Cl.2 A 204 Gr. C
A 182 Gr. F5a
A 217 Gr. C5
A 351 Gr. CG8M
A 240 Gr. 316 A 240 Gr. 316H A 240 Gr. 317
2.3
18Cr-8Ni 16Cr-12Ni-2Mo
A 182 Gr. F304L A 182 Gr. F316L
A 240 Gr. 304L A 240 Gr. 316L
2.4
18Cr-10Ni-Ti
A 182 Gr. F321 A 182 Gr. F321H
A 240 Gr. 321 A 240 Gr. 321H
2.5
18Cr-10Ni-Cb
A 182 Gr. F347 A 182 Gr. F347H A 182 Gr. F348 A 182 Gr. F348H
A 240 Gr. 347 A 240 Gr. 347H A 240 Gr. 348 A 240 Gr. 348H
2.6
23Cr-12Ni
A 240 Gr. 309H
CodeCalc User's Guide
Pipes and Pads 2.7
25Cr-20Ni
A 182 Gr. F310
2.8
20Cr-18Ni-6Mo 22Cr-5Ni-3Mo-N 25Cr-7Ni-4Mo-N 24Cr-10Ni-4Mo-V 25Cr-5Ni-2Mo-3Cu 25Cr-7Ni-3.5Mo-W-Cb 25Cr-7Ni-3.5Mo-N-Cu-W
A 182 Gr. F44 A 182 Gr. F51 A 182 Gr. F53
A 240 Gr. 310H A 351 Gr. CK3McuN A 351 Gr. CE8MN A 351 Gr. CD4Mcu A 351 Gr. CD3MWCuN
A 240 Gr. S31254 A 240 Gr. S31803 A 240 Gr. S32750
A 240 Gr. S32760
2.9
23Cr-12Ni 25Cr-20Ni
A 240 Gr. 309S A 240 Gr. 310S
2.10
25Cr-12Ni
A 351 Gr. CH8 A 351 Gr. CH20
2.11
18Cr-10Ni-Cb
A 351 Gr. CF8C
2.12
25Cr-20Ni
A 351 Gr. CK20
3.1
35Ni-35Fe-10Cr-Cb
B 462 Gr. N08020
B 463 Gr. N08020
3.2
99.0Ni
B 160 Gr. N02200
B 162 Gr. N02200
3.3
99.0Ni-Low C
B 160 Gr. N02201
B 162 Gr. N02201
3.4
67Ni-30Cu 67Ni-30Cu-S
B 564 Gr. N04400 B 164 Gr. N04405
B 127 Gr. N04400
3.5
72Ni-15Cr-8Fe
B 564 Gr. N06600
B 168 Gr. N06600
3.6
33Ni-42Fe-21Cr
B 564 Gr. N08800
B 409 Gr. N08800
3.7
65Ni-28Mo-2Fe B 462 Gr. N10665 64Ni-29.5Mo-2Cr-2Fe-Mn-W B 462 Gr. N10675
B 333 Gr. N10665 B 333 Gr. N10675
3.8
54Ni-16Mo-15Cr 60Ni-22Cr-9Mo-3.5Cb 62Ni-28Mo-5Fe 70Ni-16Mo-7Cr-5Fe 61Ni-16Mo-16Cr 42Ni-21.5Cr-3Mo-2.3Cu 55Ni-21Cr-13.5Mo 55Ni-23Cr-16Mo-1.6Cu
B 564 Gr. N10276 B 564 Gr. N06625 B 335 Gr. N10001 B 573 Gr. N10003 B 574 Gr. N06455 B 564 Gr. N08825 B 462 Gr. N06022 B 462 Gr. N06200
B 575 Gr. N10276 B 443 Gr. N06625 B 333 Gr. N10001 B 434 Gr. N10003 B 575 Gr. N06455 B 424 Gr. N08825 B 575 Gr. N06022 B 575 Gr. N06200
3.9
47Ni-22Cr-9Mo-I8Fe
B 572 Gr. N06002
B 435 Gr. N06002
3.10
25Ni-46Fe-21Cr-5Mo
B 672 Gr. N08700
B 599 Gr. N08700
3.11
44Fe-25Ni-21Cr-Mo
B 649 Gr. N08904
B 625 Gr. N08904
3.12
26Ni-43Fe-22Cr-5Mo 47Ni-22Cr-20Fe-7Mo 46Fe-24Ni-21Cr-6Mo-Cu-N
B 621 Gr. N08320 B 581 Gr. N06985 B 462 Gr. N08367
B 620 Gr. N08320 B 582 Gr. N06985 B 688 Gr. N08367
3.13
49Ni-25Cr-18Fe-6Mo Ni-Fe-Cr-Mo-Cu-Low C
B 581 Gr. N06975 B 462 Gr. N08031
B 582 Gr. N06975 B 625 Gr. N08031
3.14
47Ni-22Cr-19Fe-6Mo 40Ni-29Cr-15Fe-5Mo
B 581 Gr. N06007 B 462 Gr. N06030
B 582 Gr. N06007 B 582 Gr. N06030
3.15
33Ni-42Fe-21Cr
B 564 Gr. N08810
B 409 Gr. N08810
3.16
35Ni-19Cr-1¼Si
B 511 Gr. N08330
B 536 Gr. N08330
3.17
29Ni-20.5Cr-3.5Cu-2.5Mo
CodeCalc User's Guide
A 351 Gr. CN3MN
A 351 Gr. CN7M
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Pipes and Pads Table 1A List of Material Specification (ASME B16.5-1996) Material Group
Nominal Designation
Forgings
1.1
C-Si C-Mn-Si C-Mn-Si-V
A 216 Gr. WCB A 105 A 216 Gr. WCC A 350 Gr. LF2 A 350 Gr. LF 6 Cl.1
A 515 Gr. 70 A 516 Gr. 70 A 537 Cl. 1
1.2
C-Mn-Si C-Mn-Si-V 21/2Ni 31/2Ni
A 350 Gr. LF 6 Cl.2 A 352 Gr. LCC A 352 Gr. LC2 A 352 Gr. LC3 A 350 Gr. LF3
A 203 Gr. B A 203 Gr. E
1.3
C-Si C-Mn-Si 21/2Ni 31/2Ni
1.4
C-Si C-Mn-Si
A 350 Gr. LF1 Cl. 1
1.5
C-1/2Mo
A 182 Gr. F1
A 217 Gr. WC1 A 352 Gr. LC1
1.7
C-1/2Mo 1/2Cr-1/2Mo Ni-1/2Cr-1/2Mo 3/4Ni-3/4Cr-1Mo
A 182 Gr. F2
A 217 Gr. WC4 A 217 Gr. WC5
1.9
1Cr-1/2Mo 11/4Cr-1/2Mo 11/4Cr-1/2Mo-Si
A 182 Gr. F12 Cl.2 A 182 Gr. F11 Cl.2
A 217 Gr. WC6
A 387 Gr. 11 Cl.2
1.10
21/4Cr-1Mo
A 182 Gr. F22 Cl.3
A 217 Gr. WC9
A 387 Gr. 22 Cl.2
1.13
5Cr-1/2Mo
A 182 Gr. F5 A 182 Gr. F5a
A 217 Gr. C5
1.14
9Cr-1Mo
A 182 Gr. F9
A 217 Gr. C12
1.15
9Cr-1Mo-V
A 182 Gr. F91
A 217 Gr. C12A
A 387 Gr. 91 Cl.2
2.1
18Cr-8Ni
A 182 Gr. F304 A 182 Gr. F304H
A 351 Gr. CF3 A 351 Gr. CF8
A 240 Gr. 304 A 240 Gr. 304H
2.2
16Cr-12Ni-2Mo 18Cr-13Ni-3Mo 19Cr-10Ni-3Mo
A 182 Gr. F316 A 182 Gr. F316H
A 351 Gr. CF3M A 351 Gr. CF8M A 351 Gr. CG8M
A 240 Gr. 316 A 240 Gr. 316H A 240 Gr. 317
2.3
18Cr-8Ni 16Cr-12Ni-2Mo
A 182 Gr. F304L A 182 Gr. F316L
A 240 Gr. 304L A 240 Gr. 316L
2.4
18Cr-10Ni-Ti
A 182 Gr. F321 A 182 Gr. F321H
A 240 Gr. 321 A 240 Gr. 321H
2.5
18Cr-10Ni-Cb
A 182 Gr. F347 A 182 Gr. F347H A 182 Gr. F348 A 182 Gr. F348H
2.6
25Cr-12Ni
A 352 Gr. LCB
23Cr-12Ni
298
Castings
Plates
A 515 Gr. 65 A 516 Gr. 65 A 203 Gr. A A 203 Gr. D A 515 Gr. 60 A 516 Gr. 60 A 204 Gr. A A 204 Gr. B A 204 Gr. C
A 351 Gr. CF8C
A 240 Gr. 347 A 240 Gr. 347H A 240 Gr. 348 A 240 Gr. 348H
A 351 Gr. CH8 A 351 Gr. CH20
A 240 Gr. 309S A 240 Gr. 309H
2.7
25Cr-20Ni
A 182 Gr. F310
A 351 Gr. CK20
A 240 Gr. 310S A 240 Gr. 310H
2.8
20Cr-18Ni-6Mo 22Cr-5Ni-3Mo-N
A 182 Gr. F44 A 182 Gr. F51
A 351 Gr. CK3McuN A 351 Gr. CE8MN
A 240 Gr. S31254 A 240 Gr. S31803
CodeCalc User's Guide
Pipes and Pads 25Cr-7Ni-4Mo-N A 182 Gr. F53 24Cr-10Ni-4Mo-V A 182 Gr. F55 25Cr-5Ni-2Mo-3Cu 25Cr-7Ni-3.5Mo-W-Cb 25Cr-7Ni-3.5Mo-N-Cu-W
A 351 Gr. CD4Mcu A 240 Gr. S32750 A 351 Gr. CD3MWCuN A 240 Gr. S32760
3.1
35Ni-35Fe-20Cr-Cb
B 462 Gr. N08020
B 463 Gr. N08020
3.2
99.0Ni
B 160 Gr. N02200
B 162 Gr. N02200
3.3
99.0Ni-Low C
B 160 Gr. N02201
B 162 Gr. N02201
3.4
67Ni-30Cu 67Ni-30Cu-S
B 564 Gr. N04400 B 164 Gr. N04405
B 127 Gr. N04400
3.5
72Ni-15Cr-8Fe
B 564 Gr. N06600
B 168 Gr. N06600
3.6
33Ni-42Fe-21Cr
B 564 Gr. N08800
B 409 Gr. N08800
3.7
65Ni-28Mo-2Fe
B 335 Gr. N10665
B 333 Gr. N10665
3.8
54Ni-16Mo-15Cr 60Ni-22Cr-9Mo-3.5Cb 62Ni-28Mo-5Fe 70Ni-16Mo-7Cr-5Fe 61Ni-16Mo-16Cr 42Ni-21.5Cr-3Mo-2.3Cu
B 564 Gr. N10276 B 564 Gr. N06625 B 335 Gr. N10001 B 573 Gr. N10003 B 574 Gr. N06455 B 564 Gr. N08825
B 575 Gr. N10276 B 443 Gr. N06625 B 333 Gr. N10001 B 434 Gr. N10003 B 575 Gr. N06455 B 424 Gr. N08825
Header Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Header Material Type - Select the type of material for the header. Header Dimension Basis - Enter the header dimension basis. If the actual outside diameter is known, then select Actual (OD). If the nominal schedule of the header is known, select Nominal. Header Nominal Diameter - If you selected Actual (OD) in the Header Dimension Basis list, then enter the actual outside diameter of the pipe. If you selected Nominal in the list, enter the nominal outside diameter of the branch pipe. For example, enter 10 for a 10-inch pipe. Actual Thickness of Header - If you specified Actual (OD) as the thickness basis, then enter the actual wall thickness of the pipe; otherwise, enter 0.0 for nominal basis. The software will reduce the wall thickness according to B31.3 if appropriate values are entered for mill tolerance or corrosion allowance.
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Pipes and Pads Nominal Thickness of Header - Select the schedule for the branch or header wall only if you selected Nominal for the diameter and thickness basis. Otherwise, specify the Actual Thickness of Header. Mill Undertolerance, percent (ie. 12.5) - The mill undertolerance accounts for manufacturing deficiencies when pipe is produced. For example, if you enter 12.5, then the wall thickness of the pipe will be multiplied by (100 - 12.5)/100 or .875. This is essentially a reduction in wall thickness. Valid entries are between 0 and 99%. Header Corrosion Allowance - Enter the estimated allowance for corrosion in this field. The difference of (wall thickness - (corrosion allowance + mill tolerance)) must be greater than 0. Basic Quality Factor for Longitudinal Joints - The basic quality factor is used in the wall thickness calculations for pipes under internal pressure only. These factors are listed in the ANSI B31.3 piping code Table A-1B. For seamless and fully radiographed pipe, this value is 1.0. For electric resistance welded and spot welded materials it is usually 0.85.
Output The software will generate output for maximum allowable working pressure, new and old as well as the corroded condition. Hydrotest pressure is calculated as the maximum allowable working pressure at the design condition times 1.5 the ratio of the allowable stress at ambient temperature to the allowable stress at the design temperature. The replaced area can only be within a certain zone. No credit will be given for reinforcement that lies outside of the zone. These zones are different for extruded outlets. If a reinforcing element is used, the software will compute the required diameter for the given thickness and the required thickness for the given diameter. If a pad is used in conjunction with an extruded outlet header, consult the piping code for details on this design. If the calculated diameter falls outside the limit of reinforcement, the software displays a message such as EXCEEDS D2 or EXCEEDS L4. The MAWP for the given geometry is an estimate because of a slight non-linearity in the required thickness calculation. To verify the MAWP plug the value back into the analysis as the design pressure and check to see if the area required is equal to the area available.
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SECTION 15
WRC 107/537 FEA Home tab: Components > Add New WRC 107 Calculates stresses on the nozzle/shell junction of a vessel when a nozzle or a rectangular attachment is loaded, using one of the following methods: Calculations and tables based on Welding Research Council bulletin number 107, Local Stresses in Spherical and Cylindrical Shells due to External Loadings, August 1965, and revision 1979, based on the prior work of P.P. Bijlaard. A typical case analyzes the vessel stresses on a nozzle due to external piping loads. These loads are obtained from a piping flexibility analysis.
In 2010 WRC bulletin 537 was released. The results of the local stress calculation of this bulletin are effectively identical to that of WRC bulletin 107. Bulletin 537 simply provides equations in place of the dimensionless curves found in bulletin 107. Please review the Forward in bulletin 537 for more information. Finite element analysis (FEA). CodeCalc provides an interface for NozzlePro, a separately purchased product available from Paulin Research Group http://www.paulin.com. FEA is appropriate when the applicability and accuracy of WRC 107 are in question or a particular design is out of the scope of the bulletin. Examples include large nozzles, hillside nozzles, and lateral nozzles. FEA is then the best method to get accurate results.
After purchasing and installing NozzlePro, you must configure it to work with CodeCalc. On the Tools tab, select Configuration. On the Miscellaneous tab, browse to or type the installation path in Nozzle Pro Installation Folder. CodeCalc will now automatically run NozzlePro and present the results within CodeCalc. WRC 107/FEA also includes a stress summation capability. The software calculates overall stress intensities on a vessel/nozzle intersection in accordance with ASME Section VIII Division 2. Local vessel stresses for sustained, expansion, and occasional loads, along with pressure stresses, are transformed into code-defined stress components. The results, in the form of Pm, Pl, Q, and their appropriate combinations, can be compared with Section VIII Div. 2 allowable values.
In This Section
Design Tab..................................................................................... 302 Vessel Tab ..................................................................................... 304 Loads Tab ...................................................................................... 306 WRC 107 Options .......................................................................... 315 Results (WRC 107/537/FEA) ......................................................... 318 Examples ....................................................................................... 324
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WRC 107/537 FEA
Design Tab Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. This number can be up to 5 digits in length. Description - Enter an alpha-numeric description for the nozzle or attachment. The description can be up to 15 characters long. The description is used in results output and in any error displays. Analysis Type - Select the type of nozzle-vessel junction analysis: WRC 107/537 or FEA. To use the FEA option and perform a finite element analysis, you must separately purchase NozPro from Paulin Research Group http://www.paulin.com. Design Temperature - Enter the operating temperature of the vessel. The temperature is used to determine the allowable stress of the material from the material database. If the temperature is changed, the allowable stress of the material at operating temperature changes accordingly. Attachment Type - Select the type of attachment. Select Round for a typical pipe nozzle. Select Square for an attachment such as square vessel support lug. Select Rectangle for an attachment such as rectangular vessel support lug. See the WRC 107 bulletin for examples. Each selection opens a dialog box specific to the attachment type. When FEA is selected for Analysis Type, only Round is available. Diameter Basis - Select the type of diameter to use for the nozzle. Select ID for the inside diameter. Select OD for the outside diameter. Diameter - Enter the diameter of the nozzle, in the displayed units. The diameter should be consistent with the selection in Diameter Basis for Nozzle. Nozzle Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Full Length in Circumferential Direction, C11 - If the attachment is square or rectangular instead of a nozzle, enter C11. IN WRC 107, C11 is defined as one-half of the full length of the attachment in the circumferential direction of the vessel. Full Length in Longitudinal Direction, C22 - If the attachment is square or rectangular instead of a nozzle, enter C22. IN WRC 107, C22 is defined as one-half of the full length of the attachment in the longitudinal direction of the vessel. Fill Type - Select Hollow for a hollow attachment and select Solid for a solid attachment. Round-hollow attachments are converted to round-solid attachments for the cylinder-to-cylinder analysis. Round-hollow attachments are analyzed on spherical vessels. Rectangular attachments on spherical shells cannot be analyzed using this method.
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WRC 107/537 FEA This value is only available when WRC 107/537 is selected as the value for Analysis Type. Wall Thickness - Enter the thickness of the nozzle wall at the shell-to-nozzle junction, in the displayed units. Include any allowances for mill tolerance. For example, for a 12.5% mill tolerance, multiply the nozzle wall thickness by 0.875 and enter that value. WRC 107/537 analysis uses the wall thickness. Corrosion Allowance - Enter the corrosion allowance for the nozzle. This value typically ranges from 0 to 1/4" depending on the service and design specifications. Reinforcing Pad - Select Re-Pad when the nozzle has a pad. Select None if there is no pad. For FEA only, select Hub when the nozzle has a hub reinforcement. For WRC 107/537, the software performs two separate analyses: Using the nozzle OD and the vessel wall thickness plus the reinforcing pad thickness Taking the pad into account by making the nozzle OD equal to the reinforcing pad diameter and assuming a solid attachment. For FEA, the software performs analyses at critical locations such as the nozzle-shell junction and the edge of the pad. Thickness (Reinforcing Pad) - Enter the thickness of the reinforcing pad. For WRC 107/537 analysis, the vessel thickness includes the pad thickness. For FEA, the reinforcing pad is directly modeled. Reinforcing Pad Diameter - Enter the reinforcing pad diameter along the surface of the vessel. For WRC 107/537 analysis, a solid attachment model is used and the pad diameter is used to calculate the stresses at the edge of the reinforcing pad. For FEA, the reinforcing pad is directly modeled. Full Length of Pad in Circumferential Direction, C11P - If the attachment is square or rectangular instead of a nozzle, enter C11P. IN WRC 107, C11 is defined as one-half of the full length of the reinforcing pad in the circumferential direction of the vessel. Full Length of Pad in Longitudinal Direction, C22P - If the attachment is square or rectangular instead of a nozzle, enter C22. IN WRC 107, C22 is defined as one-half of the full length of the reinforcing pad in the longitudinal direction of the vessel. Hub Thickness - Enter the thickness of the hub.
Hub Height - Enter the height of the hub. Bevel Height - Enter the bevel height of the hub.
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WRC 107/537 FEA Insert or Abutting Nozzle? - Select Insert if the hole in the vessel is bigger than the nozzle OD and the nozzle is welded into the hole. Select Abutting if the nozzle is welded to the outside of the vessel wall. This value is only available when FEA is selected for Analysis Type. Nozzle Outside Projection - Enter the projection length of the nozzle from the vessel wall to the nozzle flange. Nozzle Inside Projection - Enter the projection length of the nozzle into the vessel, measured along the centerline of the nozzle. Thickness of Nozzle Insert (if different) - Enter the thickness of the internally projected part of the nozzle, if it is different from the nozzle thickness. Weld Leg Size for Fillet between Nozzle and Shell/Pad - Enter the fillet leg size of the weld. This field is optional. Nozzle Fatigue Curve - Select the fatigue curve to use based on the type of material. Fatigue curves are listed in ASME Section VIII, Division 2, Appendix 5. Select one of the following: S No.
Description
Low Carbon Steels 1
UTS < 130 ksi
Low Alloy Steels
To 700º F
2
High Tensile Steels 3
Martensitic stainless steels to 700º F
Austenetic Steels
4
To 800º F
70Cu-30Ni Alloys
5
Wrought 70 Copper, 30 Nickel
Ni-Cr-Mo-Fe Alloys 6
Nickel-Chromium-Moly-Iron Alloys to 800º F
This value is only available when FEA is selected for Analysis Type. . Select the shell you want Merge Shell/Head - Click to bring in data from Shells and Heads to use, and the appropriate data will be brought in from that shell for use in the analysis. Import Nozzle Data from PV Elite - Click to import nozzle data from a PVElite .pvi file.
Vessel Tab Vessel Type - Select the type of vessel. When WRC 107/537 is selected for Analysis Type on the Vessel tab, select Cylindrical or Spherical. When FEA is selected for Analysis Type, select Cylindrical, Hemispherical, Elliptical, Torispherical, Conical, or Flat Head. Attached Shell Length - Enter the length of the shell attached to the head. Set this value based on the proximity of the nozzle to the edge of the head, and the concern for any stress discontinuity in this area. This value is optional. Attached Shell Thickness - Enter the thickness of the shell attached to the head. Set this value based on the proximity of the nozzle to the edge of the head, and the concern for any stress discontinuity in this area. If left blank, this entry defaults to the thickness of the head. This value is optional. Design Length of Section - Enter the total length of the cylinder or a conical geometry. Aspect Ratio for Elliptical Heads - Enter the aspect ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Length of Straight Flange - Enter the length of the straight flange portion for conical or torispherical heads.
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WRC 107/537 FEA Inside Crown Radius - Enter the crown radius L for a torispherical head as defined in ASME Section VIII Div. 1. For more information see Appendix 1-4 in the ASME code. This dimension is usually referred to as DR in many head catalogs. Even though the head catalogs list these heads as being OD heads, the crown radius is given on the inside diameter basis. For example, DR and IKR point to the inside of the head in the illustration. Inside Knuckle Radius - Enter the knuckle radius R for a torispherical head as defined in ASME Section VIII Div. 1. For more information see Appendix 1-4 in the ASME code. This dimension is usually referred to as IKR in many head catalogs. Even though the head catalogs list these heads as being OD heads, the crown radius is given on the inside diameter basis. For example, DR and IKR point to the inside of the head in the illustration. Length of Straight Flange - Enter the length of the straight flange portion for conical or torispherical heads. Small End Diameter - Enter the diameter for the small end of the cone. Is there a knuckle? - Select if the cone has a knuckle. Knuckle Radius at Small End - Enter the knuckle radius at the small end of the cone. The direction of a conical head or shell is from the large end to the small end. The large end is the bottom of the cone and the small end is the top. Knuckle Radius at Large End - Enter the knuckle radius at the large end of the cone. The direction of a conical head or shell is from the large end to the small end. The large end is the bottom of the cone and the small end is the top. Diameter Basis For The Vessel - Select the type of diameter to use for the pressure vessel. Select ID for the inside diameter and OD for the outside diameter. The software uses Diameter Basis for Vessel, Vessel Wall Thickness, and Vessel Corrosion Allowance to determine the mean radius. Diameter of Vessel - Enter the diameter of the pressure vessel, in the displayed units. The diameter should be consistent with the selection in Diameter Basis for Vessel. Vessel Wall Thickness - Enter the thickness of the pressure vessel wall, in the displayed units. This thickness is measured at the intersection of the nozzle and the vessel.
You can type the wall thickness as an equation to account for mill tolerance. For example, if the mill tolerance is 12.5%, type: * 0.875 The software modifies this value if a value for Vessel Corrosion Allowance is defined.
Vessel Corrosion Allowance - Enter the corrosion allowance. The software adjusts the actual thickness and the inside diameter for the corrosion allowance you enter. Some common corrosion allowances are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material.
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WRC 107/537 FEA 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. For more information on material, see Material Database Dialog Box (on page 385) and Material Properties Dialog Box (on page 422). Nozzle Fatigue Curve - Select the fatigue curve to use based on the type of material. Fatigue curves are listed in ASME Section VIII, Division 2, Appendix 5. Select one of the following:
S No.
Description
Low Carbon Steels 1
UTS < 130 ksi
Low Alloy Steels
To 700º F
2
High Tensile Steels 3
Martensitic stainless steels to 700º F
Austenetic Steels
4
To 800º F
70Cu-30Ni Alloys
5
Wrought 70 Copper, 30 Nickel
Ni-Cr-Mo-Fe Alloys 6
Nickel-Chromium-Moly-Iron Alloys to 800º F
This value is only available when FEA is selected for Analysis Type on the Design Tab (on page 302).
Loads Tab Convention System - Select WRC 107 to define local forces and moments according to WRC 107 conventions. Select Global to define local forces and moments in global coordinates. The selected convention is applied to the vessel, the nozzle, and the loads. For both conventions, enter values for Direction Cosines, Sustained Loads, Expansion Loads, and Occasional Loads. The software compares stresses intensities to allowable stresses based on the value for Vessel Material selected on the Vessel tab. When you switch convention systems, the software converts loads from one system to the other. WRC 107/537 Load Conventions (on page 314) Global Load and Direction Conventions (on page 315) Direction Cosines - Enter the centerline direction cosines. Enter values for Vessel (VX, VY, and VZ) and Attachment (NX, NY, and NZ). For WRC 107 analysis, the software uses the direction vectors to transfer the global forces and moments for each load case from piping analysis software such as CAESAR II into the traditional WRC 107 sign/load convention. For FEA, these direction cosines are used to determine the angle between the nozzle/attachment and the vessel. The direction for a conical vessel is from the big end to small end. For WRC 107 analysis, the centerlines of the vessel and nozzle must be perpendicular to each other. The direction vectors of the vessel and the nozzle centerline must not be collinear. The following global convention system is used for a cylindrical vessel:
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WRC 107/537 FEA The vessel direction is +Y direction The nozzle direction is +X direction (towards the vessel) Direction cosines of the vessel are: VX - 0 VY - 1 VZ - 0 Direction cosines of the vessel are: NX - 1 NY - 0 NZ - 0 The following global convention system is used for a spherical vessel:
The direction of a spherical vessel is from points B to A
The software uses these direction vectors to transfer the global forces and moments from the global convention into the traditional WRC107 convention. Direction cosines are only available when Global is selected as the convention system. For more information, see Convention System. Loads - Enter the forces and moments acting on the nozzle or attachment. The loads are obtained from the restraint summary of CAESAR II output and/or other calculations. A stress summation is performed and stress intensities are checked based on the different load cases. The type of loads and the available load sets depend on: The Convention System selection (WRC 107 or Global). The Analysis Type selection on the Design tab (WRC 107 or FEA).
Load Sets When WRC 107 is selected for Analysis Type, you can enter values in the following load sets: Sustained Loads - (SUS) Primary loads, typically weight + pressure + forces. Expansion Loads - (EXP) Secondary thermal expansion loads. Occasional Loads - (OCC) Irregularly occurring loads such as wind loads, seismic loads, and water hammer. When FEA is selected for Analysis Type, you can enter values in the following load sets: Sustained Loads - Primary loads, typically weight + pressure + forces. Operating Loads - Loads that occur during operation of the nozzle or attachment. Occasional Loads - Irregularly occurring loads such as wind loads, seismic loads, and water hammer.
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WRC 107/537 FEA The software plots one set of loads at a time and only that set can have values. For example, to calculate Expansion Loads, values for Sustained Loads and Occasional Loads must be cleared.
Types of Loads When WRC 107 is selected for Convention System, the following forces and moments are entered: Radial Load P Longitudinal Shear VL Circumferential Shear VC Torsional Moment MT Circumferential Moment MC Longitudinal Moment ML When Global is selected for Convention System, forces and moments are entered as X, Y, and Z vector components with respect to the global coordinate system: Global Force Fx, Global Force Fy, Global Force Fz, Global Moment Mx, Global Moment My, and Global Moment Mz. Radial Load P - Enter the radial load P on the nozzle or attachment. Positive load tries to "push" the nozzle while a negative load tries to "pull" the nozzle. The software does not account for the effect of pressure thrust when loads are entered in the WRC convention, so add the appropriate portion of thrust load with the radial load. Use the conventions below.
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WRC 107/537 FEA Longitudinal Shear VL - Enter the longitudinal shear load VL. If the vessel is spherical then enter the shear load V1 from B to A. Use the conventions below.
Circumferential Shear VC - Enter the circumferential shear load VC. If the vessel is spherical then enter the shear load V2 from D to C. Use the conventions below.
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WRC 107/537 FEA Torsional Moment MT - Enter the torsional moment MT. Use the conventions below.
Circumferential Moment MC - Enter the circumferential moment MC. If the vessel is spherical then enter the moment M1 about the B-axis. Use the conventions below.
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WRC 107/537 FEA Longitudinal Moment ML - Enter the longitudinal moment ML. If the vessel is spherical then enter the moment M2 about the C-axis. Use the conventions below.
Internal Pressure - When WRC 107/537 is selected for Analysis Type on the WRC 107 tab, enter the system internal design pressure (P). WRC 107/537 only analyzes internal pressure and the value must be positive. The pressure stress equations used are: Longitudinal Stress = Pressure * ri2 /( ro2 - ri2) Hoop Stress = 2.0 * Longitudinal Stress
For the spherical case, the membrane stress due to internal pressure uses the Lamé equation to calculate the stress at both the upper and lower surfaces of the vessel at the edge of the attachment. When FEA is selected for Analysis Type on the WRC 107 tab, enter the design pressure for the vessel and the nozzle. Internal pressure is positive and external pressure is negative. Occasional Pressure (Pvar) - Enter the difference between the peak pressure of the system and Internal Pressure (the system design pressure). The value must be positive. Pvar is added to the system design pressure to calculate the primary membrane stress due to occasional loads. This value is only available when WRC 107/537 is selected for Analysis Type on the WRC 107 tab. Include Pressure Thrust - Select to include the pressure thrust force (P*A) in the nozzle radial load. Pressure thrust is added to Internal Pressure and Occ.Pressure Diff. (Pvar).
This value is only available when WRC 107/537 is selected for Analysis Type on the WRC 107 tab.
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WRC 107/537 FEA For more information on pressure thrust, see the July 2001 COADE Newsletter http://www.coade.com/newsletters/jul01.pdf. Override Vessel-Nozzle Angle? - Select and enter an angle to override the calculated angle.
The calculated angle is the vector product between the direction cosine of the vessel and the nozzle. Vessel-Nozzle Angle - Click to enter nozzle orientation values. This value is only available when FEA is selected for Analysis Type on the WRC 107 tab. Nozzle Orientation Reference Vector - Enter the nozzle orientation reference vector, by entering values for X Direction Cosine (NRX), Y Direction Cosine (NRY), and Z Direction Cosine (NRZ). The vector defines the zero-degree reference axis where the orientation of the nozzle is measured, indicating where the nozzle is located around the vessel. You must also enter the angular displacement of the nozzle from this reference vector in Nozzle Orientation Angle for the Reference Vector. These values are optional. For example, the nozzle shown below is located along the X-axis. It can be represented by a nozzle orientation reference vector along the X-axis and a nozzle orientation angle of 0º.
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WRC 107/537 FEA When the nozzle is located along the Z-axis, it can represented by a nozzle orientation reference vector along the X-axis and a nozzle orientation angle of 90º.
Nozzle Orientation Angle for the Reference Vector - Enter the angular displacement of the nozzle from the Nozzle Orientation Reference Vector. This value is optional. For example, if the nozzle orientation reference vector is along the X-axis and the nozzle orientation angle is zero, then the nozzle is located along the x-axis.
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WRC 107/537 FEA Nozzle Offset from the Vessel Centerline - Enter the offset distance from shell/head centerline to the nozzle centerline. Nozzle Distance from Top End of the Vessel - Enter the distance from the positive end of the vessel to the point where the nozzle or branch centerline intersects the vessel centerline.
WRC 107/537 Load Conventions The WRC 107/537 convention system has the benefit of being independent of the orientation of the vessel. All loads and moments are defined locally with respect to the vessel and the nozzle. The following WRC 107 convention system is used for a cylindrical vessel:
P - Radial load VC - Circumferential shear load VL - Longitudinal shear load MC - Circumferential moment ML - Longitudinal moment MT - Torsional moment
The following WRC 107 convention system is used for a spherical vessel:
P - Radial load V1 - Shear load from points B to A V2 - Shear load from points D to C M1 - Moment from points A to B M2 - Moment from points D to C MT - Torsional moment
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Global Load and Direction Conventions The global convention system has the benefit of using the global coordinate system also used by other analyses, such as pipe stress analysis. As a result, nozzle or attachment loads from another analysis can be used directly in the WRC 107/537 or FEA analysis. The following global convention system is used for a cylindrical vessel: The vessel direction is +Y direction The nozzle direction is +X direction (towards the vessel) Direction cosines of the vessel are: VX - 0 VY - 1 VZ - 0 Direction cosines of the vessel are: NX - 1 NY - 0 NZ - 0 The following global convention system is used for a spherical vessel:
The direction of a spherical vessel is from points B to A
The software uses these direction vectors to transfer the global forces and moments from the global convention into the traditional WRC107 convention.
WRC 107 Options WRC 107 Version - Select a version of the WRC 107/537 bulletin. Select August 1965, March 1979, or March 1979 Use B1 and B2. March 1979 Use B1 and B2 is likely to be the most accurate option. It typically produces slightly higher stresses than the other versions. These stresses more closely match theoretical results. The stress computation method was also adjusted to compute B1 and B2 maximum stresses that do not lie on the stress points A, B, C or D. This is referred to as calculation of the off-angle maximums. Would you like to have interactive control? - Select to have interactive control. In many instances, the geometric parameter Beta, which is computed for cylindrical shell geometry, exceeds the parameter Gamma for certain WRC 107/537 curves. If this option is not selected, then the software uses the last point on the curve that is available and completes the analysis. If
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WRC 107/537 FEA this option is selected, then the software pauses and ask you to enter what a value of the stress parameter from the WRC 107/537 curves. In most cases, this option is not selected. Include WRC 107 SIF (Kn,Kb) - Select to include the WRC 107 Appendix B stress concentration factors (Kn and Kb) in a fatigue analysis. This option should only be used if you are performing a fatigue analysis. Check ASME VIII Div.2 paragraph AD-160 to see if the fatigue effect needs to be considered. Kn and Kb are used for estimating the peak stress intensity due to external loads. Peak stress intensity due to internal pressure is included in the analysis by selecting Include Pressure Stress Indices per Div. 2?. For normal (elastic) analysis, do not select this option or Include Pressure Stress Indices per Div. 2?. The software does not perform the complete fatigue analysis of Section VIII Div.2 Appendix 4 and 5 rules. Instead, the value of peak stress intensity is reported for fatigue effect comparison. For more information, see WRC-107 Elastic Analysis v/s Fatigue Analysis in the June 2000 COADE newsletter http://www.coade.com/newsletters/jun00.pdf. Fillet Radius Between Vessel and Nozzle - Enter the fillet radius between the nozzle and the vessel shell. The software uses this value to calculate the stress concentration factors Kn and Kb according to Appendix B of the WRC 107 bulletin. A value of 0 sets Kn and Kb to 1.0. Fillet Radius Between Vessel and Pad - Enter the fillet radius between the pad and the vessel shell. The software uses this value to calculate the stress concentration factors Kn and Kb for the vessel/pad intersection, according to Appendix B of the WRC 107 bulletin. A value of 0 sets Kn and Kb to 1.0. Include Pressure Stress Indices per Div. 2? - Select to include the ASME Sec. VIII Div. 2 Table AD-560.7 pressure stress indices in a fatigue analysis. This option should only be used if you are performing a fatigue analysis. Check ASME VIII Div.2 paragraph AD-160 to see if the fatigue effect needs to be considered. The pressure stress indices are used for estimating the peak stress intensity due to internal pressure.
Peak stress intensity due to external loads is included in the analysis by selecting Include WRC 107 SIF (Kn, Kb)?. For normal (elastic) analysis, do not select this option or Include WRC 107 SIF (Kn, Kb)?. The software does not perform the complete fatigue analysis of Section VIII Div.2 Appendix 4 and 5 rules. Instead, the value of peak stress intensity is reported for fatigue effect comparison. For more information, see the June 2000 COADE newsletter http://www.coade.com/newsletters/jun00.pdf. Compute pressure stress per WRC 368 (no ext loads)? - Select to compute pressure stresses in the shell and nozzle according to WRC 368. WRC 368 provides a method for calculating stresses in a cylinder-to-cylinder intersection (such as cylinder-to-nozzle) due to internal pressure and pressure thrust loading.
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Using WRC 368 with WRC 107/297 is not accurate for calculating the combined stress from pressure and external loads. So, this option is only available when the attachment type is round and when no external loads are specified. For more information on WRC 368 and pressure thrust, see Modeling of Internal Pressure and Thrust Loads on Nozzles Using WRC-368 in the July 2001 COADE Newsletter http://www.coade.com/newsletters/jul01.pdf.
CodeCalc User's Guide
WRC 107/537 FEA
FEA Options Specify File Name for FEA - Enter text to use as the prefix for FEA analysis file names. The filename can up to seven characters long without quotes and spaces. Specify FEA Mesh Density - Select the type of mesh density. Select Crude to produce a coarse mesh that solves quickly. Select Fine and enter a value for the mesh density multiplier. The typical value for the multiplier is between 1 and 2. A finer mesh has more accurate results but takes longer to solve. Select Crude and Preview the finite element mesh? to check the initial mesh. Specify S.C.F. for Vessel - Enter the notch effect multiplication factor for computing peak stresses on the vessel. This is a type of stress concentration factor, defined in the ASME Section VIII, Division 2 Appendix 4. A typical value is 1.35. This is an optional value and is only used in the FEA fatigue failure stress case. Specify S.C.F. for Nozzle - Enter the notch effect multiplication factor for computing peak stresses on the nozzle. This is a type of stress concentration factor, defined in the ASME Section VIII, Division 2 Appendix 4. A typical value is 1.35. This is an optional value and is only used in the FEA fatigue failure stress case. Number of Operating Cycles - Enter a value for the number of operating load cycles in order to select the allowable fatigue stress from S-N curves. If 0 or no value is entered, the software defaults to 7000 cycles. This is an optional value. For more information on operating loads, see Load Sets. Number of Occasional Cycles - Enter a value for the range of occasional load cycles, in order to perform a fatigue analysis. If 0 is entered, the occasional load is treated like a static load. This is an optional value. For more information on occasional loads, see Load Sets. Do not cut hole in header for branch? - Select if there is no opening in the vessel due to the nozzle. For example, there is no opening in the vessel for a support trunnion, but an injector pipe will have an opening. Consider thermal strains? - Select to consider thermal strains. Enter values for Vessel Inside Temperature, Vessel Outside Temperature, Nozzle Inside Temperature, and Nozzle Outside Temperature. These values are used to calculate thermal expansion. Run analysis in silent mode? - Select to run the analysis in silent mode. When the software runs in silent mode, status windows from Nozzle Pro are not displayed. Use this option with caution because the status windows display error information. Preview the finite element mesh? - Select to preview the finite element mesh. When the software runs the analysis, the finite element mesh is shown.
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Results (WRC 107/537/FEA) WRC 107 Stress Summations ASME Section VIII, Division 2 code provides or a procedure to analyze the local stresses in vessels and nozzles (Appendix 4-1, Mandatory Design Based on Stress Analysis). Only the elastic analysis approach is discussed here. You should always refer to the applicable code if any of the limits described in this section are approached; if any unusual material, weld, or stress situation exists; or there are non-linear concerns such as operation of the material in the creep range. The first step in the procedure is to determine if the elastic approach is satisfactory. Section AD-160 contains the exact method and states that if all of the following conditions are met, then fatigue analysis need not be done: The expected design number of full-range pressure cycles does not exceed the number of allowed cycles corresponding to a Sa value of 3Sm (4Sm for non-integral attachments) on the material fatigue curve. The Sm is the allowable stress intensity for the material at the operating temperature. The expected design range of pressure cycles other than startup or shutdown must be less than 1/3 (1/4 for non-integral attachments) the design pressure times (Sa/Sm), where Sa is the value obtained on the material fatigue curve for the specified number of significant pressure fluctuations. The vessel does not experience localized high stress due to heating. The full range of stress intensities due to mechanical loads (including piping reactions) does not exceed Sa from the fatigue curve for the expected number of load fluctuations. Once you decide that an elastic analysis is satisfactory, either a simplified approach—WRC 107 Stress Calculations (on page 321)—or a comprehensive approach—Finite Element Analysis (FEA) (on page 323)—may be taken to the vessel stress evaluation. ASME Section VIII Division 2 - Elastic Analysis of Nozzle (on page 318)
ASME Section VIII Division 2 - Elastic Analysis of Nozzle In order to address local allowable stresses, the endurance curve for the material of construction and complete design pressure/temperature loading information should be available. If any of the elastic limits are approached, or if there is anything out of the ordinary about the nozzle/vessel connection design, the code should be carefully consulted before performing the local stress analysis. The material Sm table and the endurance curve for carbon steels are given in this section for illustration. Only values taken directly from the code should be used in design. There are essentially three criteria that must be satisfied before the stresses in the vessel wall due to nozzle loads can be considered within the allowables. These three criteria can be summarized as: Pm < kSmh Pm + Pl + Pb< 1.5kSmh Pm + Pl + Pb + Q < 3Smavg
Where Pm, Pl, Pb, and Q are the general primary membrane stress, the local primary membrane stress, the local primary bending stress, and the total secondary stresses (membrane plus bending), respectively; and K, Smh, and Smavg are the occasional stress factor, the hot material allowable stress intensity, and the average material stress intensity (Smh + Smc)/2. Due to the stress classification defined by Section VIII, Division 2 in the vicinity of nozzles, as given in Table 4-120.1, the bending stress terms caused by any external load moments or
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WRC 107/537 FEA internal pressure in the vessel wall near a nozzle or other opening, should be classified as Q, or the secondary stresses, regardless of whether they were caused by sustained or expansion loads. This causes Pb to disappear, and leads to a much more detailed classification: Pm - General primary membrane stress (primarily due to internal pressure) Pl - Local primary membrane stress, which may include: Membrane stress due to internal pressure Local membrane stress due to applied sustained forces and moments Q - Secondary stresses, which may include: Bending stress due to internal pressure Bending stress due to applied sustained forces and moments Membrane stress due to applied expansion forces Bending stress due to applied expansion forces and moments Membrane tress due to applied expansion moments Each of the stress terms defined in the above classifications contains three parts: two stress components in normal directions and one shear stress component. To combine these stresses, the following rules apply: 1. Compute the normal and shear components for each of the three stress types, i.e. Pm, Pl, and Q. 2. Compute the stress intensity due to the Pm and compare it against kSmh. 3. Add the individual normal and shear stress components due to Pm and Pl; compute the resultant stress intensity and compare its value against 1.5kSmh. 4. Add the individual normal and shear stress components due to Pm, Pl, and Q, compute the resultant stress intensity, and compare its value to against 3Smavg. 5. If there is an occasional load as well as a sustained load, these types may be repeated using a k value of 1.2. These criteria can be readily found from Figure 4-130.1 of Appendix 4 of ASME Section VIII, Division 2 and the surrounding text. Note that the primary bending stress term, Pb, is not applicable to the shell stress evaluation, and therefore disappears from the Section VIII, Division 2 requirements. Under the same analogy, the peak stress limit may also be written as: P l + Pb + Q + F < S a
The above equation need not be satisfied, provided the elastic limit criteria of AD-160 is met based on the statement explicitly given in Section 5-100, which is cited below: "If the specified operation of the vessel meets all of the conditions of AD-160, no analysis for cyclic operation is required and it may be assumed that the peak stress limit discussed in 4-135 has been satisfied by compliance with the applicable requirements for materials, design, fabrication, testing and inspection of this division."
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WRC 107/537 FEA Example: Fatigue Curve (For Values of Sa)
The equations used in CodeCalc to qualify the various stress components can be summarized as follows: Pm(SUS) < Smh Pm(SUS + OCC) < 1.2Smh Pm(SUS) + Pl(SUS) < 1.5Smh Pm(SUS + OCC) + Pl(SUS + OCC) < 1.5(1.2)Smh Pm(SUS + OCC) + Pl(SUS + OCC) + Q(SUS + EXP + OCC) < 1.5(Smc + Smh)
If some of the conditions of in ASME VIII Div.2, AD-160 are not satisfied, you probably need to perform the formal fatigue analysis. Peak stresses are required to be calculated or estimated. You may consider using AD-560, Alternative Rules for Nozzle Design instead of Article 4-6, Stresses in Openings for Fatigue Evaluation to calculate the peak pressure stress for the opening. If all conditions of AD-560.1 through AD-560.6 are satisfied, the stress indices given in Table AD-560.7 may be used. If you click the corresponding box, the software uses these pressure stress indices to modify the primary stress due to internal pressure (hoop and longitudinal stresses). For external loads, the highest peak stress is usually localized in fillets and transitions. If you use WRC107 stress concentration factors (Kn, Kb), the fillet radius between the vessel and nozzle is required. (If a reinforcing pad is used, you can input the pad fillet radius.) The software makes a rough approximation and use WRC 107 Appendix-B equations (3) and (4) to estimate Kn and Kb. The tension and bending stresses are thus modified using Kn and Kb respectively. The software calculates the local stresses for four pairs of points (upper and lower) at the intersection. You should not direct the program to perform the stress summations. Instead, determine which stresses should be added based on locations in order to obtain the peak stress level, and then use Appendix-4 and 5 rules and fatigue curves depending on operation cycles.
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WRC 107/537 FEA Based on comparisons with finite element analysis, it is known that the top tip of the fillet weld on the nozzle usually experiences the highest peak stress due to external loads. It is conservative to add all the peak stresses after including both pressure stress indices and concentration factors. Note that the stress summation may ONLY be used to check stress intensities, not stress levels. You need the peak stress level to perform fatigue analysis. The current stress summation routine does not compare stress level with fatigue allowables according to Appendix 5. However, you may find the stress summation results useful to compare the combined effect due to the stress concentration factor and pressure stress indices. For more information on fatigue analysis, see WRC-107 Elastic Analysis v/s Fatigue Analysis in the June 2000 COADE newsletter http://www.coade.com/newsletters/jun00.pdf.
WRC 107 Stress Calculations The software calculates stress intensities according to WRC 107 and includes the effects of longitudinal and hoop stresses due to internal pressure. If the geometry includes a reinforcing pad, CodeCalc performs two analyzes on the geometry. The first analysis calculates stresses at the edge of the nozzle. The second stress analysis is at the edge of the reinforcing pad. CodeCalc uses the Lamé equation to determine the exact hoop stress at the upper and lower surface of the cylinder around the edge of the attachment. The hoop stress equations, as well as the longitudinal stress equation are as follows:
For spherical shells the program uses the following equation:
For each run performed, a table of dimensionless stress factors for each loading is displayed for review. Any table figure followed by an exclamation point (!) means that the curve figure for that loading has been exceeded.
Why are the stresses at Edge of the Pad the same as at Edge of the Nozzle? Because the stress is a direct product of the stress factor, the stresses calculated at the edge of the pad may be same as those at the edge of the nozzle if the curve parameter for that type of stress has been exceeded.
What are the Allowable Stresses? The stress intensities calculated should typically be between 1.5 and 3.0 times the hot allowable stress for the vessel material at operating temperature. If the results are less than 1.5 Sa then the configuration and loading are acceptable. If the load is self-relieving — that is, if it relaxes or disappears after only a small rotation or translation of the attachment — the allowable stress intensity increases to 3.0 Sa. Since many geometries do not fall within the acceptable range of WRC 107, it may be necessary to use a more sophisticated tool to solve the problems where the diameter of the vessel is very large in comparison with the nozzle, or where the thickness of the
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WRC 107/537 FEA vessel or nozzle is small. An example of a more sophisticated tool would be Finite Element Analysis (FEA) (on page 323).
Figure C - WRC 107 Module Geometry for a Sphere
Figure D - WRC 107 Axis Convention for a Cylinder
Spherical Shells To Define WRC Axes:
P-axis: Along the nozzle centerline and positive entering the vessel. M1-axis: Perpendicular to the nozzle centerline along convenient global axis. M2-axis: Cross the P-axis into the M1 axis and the result is the M2-axis.
To Define WRC Stress Points:
u: Upper, means stress on outside of vessel wall at junction. l: Lower, means stress on inside of vessel at junction. A: Position on vessel at junction, along negative M1 axis. B: Position on vessel at junction, along positive M2 axis. C: Position on vessel at junction, along positive M2 axis. D: Position on vessel at junction, along negative M2 axis.
Cylindrical Shells To Define WRC Axes:
P-axis: Along the nozzle centerline and positive entering the vessel. MC-axis: Along the vessel centerline and positive to correspond with any parallel global axis. M2-axis: Cross the P-axis with the MC axis and the result is the ML-axis.
To Define WRC Stress Points:
u: Upper, means stress on outside of vessel wall at junction. l: Lower, means stress on inside of vessel at junction. A: Position on vessel at junction, along negative MC axis. B: Position on vessel at junction, along positive MC axis. C: Position on vessel at junction, along positive ML axis. D: Position on vessel at junction, along negative ML axis.
Shear axis VC is parallel, and in the same direction as the bending axis ML. Shear axis VL is parallel, and in the opposite direction as the bending axis MC.
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Finite Element Analysis (FEA) Using the interface within CodeCalc to Paulin Research Group's NozzlePro program, you can perform FEA and WRC 107 within the same module. FEA can model more types of vessel and nozzle geometries. This module uses the ASME Section VIII Div. 1 allowable stress values, which may be conservative in some cases. You can switch to Div. 2 values. FEA generates graphical results showing various ASME stress states. Important results and a sample printout are below. The ASME overstressed areas are reported. ASME Overstressed Areas Pad Edge Weld for Nozzle 1 Pl 1.5(k)Smh Primary Membrane Load Case 2 20,116 18,000 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2 111%
1. The next report, the Highest Primary Stress Report, outlines the stresses at critical location like the nozzle-shell junction and the edge of the pad. 2. The Highest Secondary and Fatigue Stress Reports are also provided. 3. Next, the program lists nozzle stress intensification factors for use in a beam type pipe stress analysis program such as CAESAR II. 4. NozzlePro then calculates the maximum individual allowable loads and simultaneously acting allowable loads. Both primary and secondary loads are reported. Maximum SECONDARY Load Type Individual (Range): Occurring
Conservative Simultaneous Occurring
Realistic Simultaneous Occurring
Axial Force (lb.)
398030.
120631.
180946.
Inplane Moment (in. lb.)
5306513.
1137199.
2412363.
Outplane Moment (in. lb.)
3358105.
719650.
1526608.
Torsional Moment (in. lb.) Pressure (psi)
2343568. 344.
710264.
1065396.
111.
111.
PRIMARY Load Type (Range):
Maximum Individual Occurring
Axial Force (lb.)
618455.
178300.
267450.
Inplane Moment (in. lb.)
5998639.
1222872.
2594104.
Outplane Moment (in. lb.)
5458219.
1182725.
2508939.
Torsional Moment (in. lb.)
2938301.
847110.
Pressure (psi)
422.
Conservative Simultaneous Occurring
111.
Realistic Simultaneous Occurring
1270665. 111.
Conservative simultaneous loads will produce stresses that are approximately 60-to-70% of the allowable. Realistic allowable simultaneous loads are the maximum loads that can be applied simultaneously, producing stresses that are closer to 100% of the allowable. Maximum
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WRC 107/537 FEA individual occurring primary pressure can be taken as a finite element calculation of the MAWP for the nozzle. Nozzle-shell junction flexibilities are also available. These flexibilities are used to accurately model the flexibility of the junction and can be included in the pipe stress software used to model the piping system attaching to the nozzle. You have a choice of performing either a WRC 107 or a finite element analysis from within the same module, without redundant input. As with any finite element program users should visually check the finite element mesh for errors and make sure the FEA results make sense from stress analysis perspective. Address technical queries regarding FEA results to Paulin Research Group http://www.paulin.com.
Examples Examples illustrating these principles are located in the CodeCalc\Examples directory.
Figure F - Vessel and Nozzle Direction Cosines
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WRC 107/537 FEA After confirming that the geometry guidelines according to WRC 107 are met, the actual preparation of the WRC 107 calculation input can now begin. One of the most important steps in the WRC 107 procedure is to identify the correlation between the stress output global coordinates and the WRC 107 local axes. The software performs this conversion automatically. You will, however, have to identify the vectors defining the vessel as well as the nozzle centerline. The following figure illustrates the definition of the direction vectors of the vessel and the nozzle:
Figure G - Converting Forces/Moments in CAESAR II Global Coordinates to WRC 107 Local Axes In order to define a vessel direction vector, you must first designate the output data points (A to D) as defined by the WRC 107 bulletin. The line between data points B and A defines the vessel centerline, except for nozzles on heads, where the vessel centerline will have to be defined along a direction which is perpendicular to that of the nozzle. In the vessel/nozzle configuration shown, because point A is assigned to the bottom of the nozzle, the vessel direction vector can be written as (0.0, -1.0, 0.0), while the nozzle direction vector is (1.0, 0.0, 0.0). The nozzle direction vector is always defined as the vector pointing from the vessel nozzle connection to the centerline of vessel. For different load cases (SUS, EXP, OCC), the restraint loads (forces and moments) can be obtained from typical piping stress analysis program like CAESAR II. These loads reflect the action of the piping on the vessel. The following data would then be entered into the WRC 107 program. You can use either the WRC-107 or global convention. The program will supply a pass/fail status at the end of the report. While on the input screen you can also toggle from one convention to another and the program will transform the loads automatically between the two conventions. Summary of Restraint Loads on the Vessel Load
X lb
CodeCalc User's Guide
Y lb
Z lb
MX ft. lb
MY ft. lb
MZ ft. lb
325
WRC 107/537 FEA Sustained -26
-1389
32
-65
127
4235
Expansion 8573
23715
-5866
31659
-5414
-525
Force VC(+Z)
Momen Moment Moment t T(-X) MC (+Y) ML(+Z)
WRC 107 Local Components Load
326
ForceP(+ Force X) VL(-Y)
Sustained -26
-1389
32
-65
127
4235
Expansion 8573
23715
-5866
31659
-5414
-52583
CodeCalc User's Guide
SECTION 16
Base Rings Home tab: Components > Add New Base Ring Performs thickness calculations and design for annular plate baserings, top rings, bolting, and gussets. These calculations are performed using industry standard calculation techniques. Thickness of a Basering under Compression - The equation for the thickness of the basering is the equation for a simple cantilever beam. The beam is assumed to be supported at the skirt, and loaded with a uniform load caused by the compression of the concrete due to the combined weight of the vessel and bending moment on the down-wind / down-earthquake side of the vessel. Thickness of a cantilever, t:
Where fc = Bearing stress on the concrete l = Cantilever length of basering s = Allowable bending stress of basering (typically 1.5 times the code allowable) There are two commonly accepted methods of determining the stress from the vessel and base-ring acting on the concrete. The simplified method calculates the compressive stress on the concrete assuming that the neutral axis for the vessel is at the centerline. Stress acting on the concrete, fc:
Where: W = Weight of the vessel together with the basering M = Maximum bending moment on vessel A = Cross-sectional area of basering on foundation c = Distance from the center of the basering to the outer edge of the basering I = Moment of inertia of the basering on the foundation However, when a steel skirt and basering are supported on a concrete foundation, the behavior of the foundation is similar to that of a reinforced concrete beam. If there is a net bending moment on the foundation, then the force upward on the bolts must be balanced by the force downward on the concrete. Because these two materials have different elastic moduli, and because the strain in the concrete cross section must be equal to the strain in the base ring at any specific location, the neutral axis of the combined bolt/concrete cross section will be in the direction of the concrete. Several authors, including Jawad and Farr (Structural Analysis and Design of Process Equipment, pg 428 - 433) and Megyesy (Pressure Vessel Handbook, pg 70 -
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Base Rings 73), have analyzed this phenomenon. The software uses the formulation of Singh and Soler (Mechanical Design of Heat Exchangers and Pressure Vessel Components, pg 957 - 959). This formulation seems to be the most readily adaptable to computerization, as there are no tabulated constants. Singh and Soler provide the following description of their method: In this case, the neutral axis is parallel to the Y-axis. The location of the neutral axis is identified by the angle alpha. The object is to determine the peak concrete pressure (p) and the angle alpha. For narrow base plate rings, an approximate solution may be constructed using numerical iteration. It is assumed that the concrete annulus under the base plate may be treated as a thin ring of mean diameter c. Assuming that the foundation is linearly elastic and the base plate is relatively rigid, Brownell and Young have developed an approximate solution which can be cast in a form suitable for numerical solution. Let the total tensile stress area of all foundation bolts be A. Within the limits of accuracy sought, it is permissible to replace the bolts with a thin shell of thickness t and mean diameter equal to the bolt circle diameter c, such that: Thickness, t:
Where: A = Total cross-sectional area of all foundation bolts P = Peak concrete pressure l = Width of basering c = Thin ring diameter We assume that the discrete tensile bolt loads, acting around the ring, are replaced by a line load, varying in intensity with the distance from the neutral plane. Let n be the ratio of Young's moduli of the bolt material to that of the concrete; n normally varies between 10 and 15. Assuming that the concrete can take only compression (non-adhesive surface) and that the bolts are effective only in tension (untapped holes in the base plate), an analysis, similar to that given above, yields the following results:
Where: n = Ratio of elastic modulus of the bolt, Eb, to that of the concrete, Ec:
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Base Rings t3 = Width of the basering, similar to the cantilever length, l, in Jawad and Farr's thickness equation previously mentioned c = Bolt circle diameter r1 - r4 = Four constants based on the neutral axis angle and defined in Singh and Soler's equations 20.3.12 through 20.3.17, not reproduced here. These equations give the required seven non-linear equations to solve for seven unknowns, namely p, c, α, and the ri (i = 1 - 4) parameters. The iterative solution starts with assumed values of s and p, so and po, taken from an approximate analysis performed first. Then α is determined using the above equation. Knowing α the dimensionless parameters r1, r2, r3, and r4 are computed. This enables computation of corrected values of p and s, named po' and so'). The next iteration is started with s1 and p1 where we choose:
This process is continued until the errors ei and Ei at the iteration stage are within specified tolerances --ei = Ei = 0.005 is a practical value, Where:
After the new values of bolt stress and bearing pressure are calculated, the thickness of the base ring is calculated again using the same formula given above for the approximate method. Thickness of Basering under Tension - On the tensile side, if there is no top ring but there are gussets, then there is a discrepancy on how to do the analysis. For example, while Megyesy uses Table F (Pressure Vessel Handbook, pg 78) to calculate an equivalent bending moment, Dennis R. Moss uses the same approach but does not give a table (Pressure Vessel Design Manual, pg 126-129), and Jawad & Farr use a 'yield-line' theory (Structural Analysis and Design of Process Equipment, pg 435-436). Since the Jawad and Farr equation for thickness, t, is both accepted and explicit, the program uses their equation 12.13: Thickness, t:
Where:
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Base Rings Bolt Load, Pt:
sy = Yield strength of the bolt a = Distance between gussets b = Width of base plate that is outside of skirt l = Distance from skirt to bolt area d = Diameter of bolt hole Thickness of Top Ring under Tension - If there is a top ring or plate, its thickness is calculated using a simple beam formula. Taking the plate to be a beam supported between two gussets with a point load in the middle equal to the maximum bolt load, we derive the following equation: Thickness, t:
Where: Allowable stress, s:
Bending moment, M:
Where: Cg = Center of gravity, depending on the geometry of the plate Bolt Load, Pt:
Section Modulus, Z:
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Width of Section, Wt:
Required Thickness of Gussets in Tension - If there are gussets, they must be analyzed for both tension and compression. The tensile stress, T, is the force divided by the area, where the force is taken to be the allowable bolt stress times the bolt area, and the area of the gusset is the thickness of the gusset, tgusset, times one half the width of the gusset, W gusset (because gussets normally taper):
Where:
Required Thickness of Gussets in Compression - In compression (as a column) we must iteratively calculate the required thickness. Taking the actual thickness as the starting point, we perform the calculation in AISC 1.5.1.3. The radius of gyration for the gusset is taken as 0.289 t per Megyesy's Pressure Vessel Design Handbook, page 404. The actual compression is calculated as described above, and then compared to the allowed compression per AISC. The thickness is then modified and another calculation performed until the actual and allowed compressions are within one half of one percent of one another. Basering Design - When you request a basering design, the software performs the following additional calculations to determine the design geometry: Selection of Number of Bolts This selection is made on the basis of Megyesy's table in Pressure Vessel Handbook (Table C, page 67). Above the diameter shown, the selection is made to keep the anchor bolt spacing at about 24 inches. Calculation of Load per Bolt This calculation of load, Pb, per bolt:
Where:
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Base Rings
W = Weight of vessel N = Number of bolts R = Radius of bolt area M = Bending moment Calculation of Required Area for Each Bolt This is the load per bolt divided by the allowable stress:
Selection of the Bolt Size The software has a table of bolt areas and selects the smallest bolt with area greater than the area calculated above. Selection of Preliminary Basering Geometry - The table of bolt areas also contains the required clearances in order to successfully tighten the selected bolt (wrench clearances and edge clearances). The software selects a preliminary basering geometry based on these clearances. Values selected at this point are the bolt circle, base ring outside diameter, and base ring inside diameter. Analysis of Preliminary Basering Geometry - Using the methods described previously for the analysis section, the software determines the approximate compressive stress in the concrete for the preliminary geometry. Selection of Final Basering Geometry - If the compressive stress calculated above is acceptable then the preliminary geometry becomes the final geometry. If not, then the bolt circle and base ring diameters are scaled up to the point where the compressive stresses are acceptable. These become the final base ring geometry values. Analysis of Basering Thicknesses - The analysis then continues through the thickness calculation described above, determining required thicknesses for the basering, top ring, and gussets.
In This Section
Base Ring (1) Tab (Base Rings) .................................................... 333 Base Ring (2) Tab (Base Rings) .................................................... 334 Miscellaneous Tab (Base Rings) ................................................... 336 Results (Base Rings) ..................................................................... 339
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Base Ring (1) Tab (Base Rings) Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. in CodeCalc can either analyze existing base Analyze or Design Basering? - Base Rings rings or design new ones. You can choose either Analyze for existing or Design for new baserings. If you choose Design mode, the software may change the following items: Number of Bolts Size of Bolts Bolt Circle Diameter Outside Diameter of the Base ring Inside Diameter of the Base ring Temperature of Basering (needed if not ambient) - Normally baserings operate at temperatures which are near ambient. If the base ring is at a higher temperature, enter it here; otherwise, leave the default temperature. Thickness of Basering - Enter the actual thickness of basering. Any allowances for corrosion or mill tolerance should be subtracted from this value. The software will compute the required basering thickness using the simplified method and the neutral axis shift method. The user-specified thickness value will be used only for comparison. Basering Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Inside Diameter of Basering - Enter the inside diameter of the basering. This value must be greater than 0 and less than the bolt circle diameter and the base ring OD. If you have specified that the software is to design the base ring, the software may change this value. A good approximation for the base ring ID should be entered when using either the Analyze or Design option. Outside Diameter of Basering - Enter the outside diameter of the base ring. This value must be greater than the base ring ID and the bolt circle diameter. When in Design mode, the software may change this value.
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Base Ring (2) Tab (Base Rings) Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Diameter of Bolt Circle - Enter the diameter of the bolt circle of the flange. This is dimension C in the ASME Code.
Figure 68: Flange Diagram
Thread Series - The following bolt thread series tables are available: TEMA Bolt Table UNC Bolt Table User-specified root area of a single bolt TEMA Metric Bolt Table British, BS 3643 Metric Bolt Table
334
Irrespective of the table used, the values are converted back to user selected units. TEMA threads are National Coarse series below 1-inch and 8 pitch thread series for 1-inch and above bolt nominal diameter. The UNC threads available are the standard threads.
CodeCalc User's Guide
Base Rings Nominal Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the software range from 0.5 to 4.0 inches. This value is used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field. Also, enter the root area of one bolt in the Root Area cell. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt here. Number of Bolts - Enter the number of bolts to use in the flange analysis. The number of bolts is almost always a multiple of four. Skirt Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Skirt Thickness - Enter the thickness of the skirt here. This entry must be greater than 0. The software will automatically compute the required skirt thickness for both combinations of bending and axial stress. The software uses the ASME code compression allowable B for axial stresses. Skirt Temperature - If the skirt is at an elevated temperature, enter it here. Usually, skirts are at ambient temperature. Outside Diameter of Skirt at Base - Enter the skirt OD at the junction of the skirt and base ring. This value should be greater than the base ring ID and less than the base ring bolt circle. Skirt Diameter at Bottom Head - Enter the diameter of the skirt at the bottom head of the vessel. Not all skirts are cylindrical. Some skirts are cone shaped and as such have different diameters at the top and bottom. Joint Eff. for Skirt Weld at Bottom Head - Enter the joint efficiency for the weld that joins the skirt to the bottom head. This value depends on the weld detail used. Typical values range between 0.49 and 1.0.
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Miscellaneous Tab (Base Rings) Nominal Compressive Stress of Concrete - Enter the Nominal Compressive stress of the Concrete to which the base ring is bolted. This value is f'c in Jawad and Farr or FPC in Meygesy. A typical entry is 3000 psi. Water Content, US Gallons fc, 28 Day Ultimate Compressive Strength (psi) per 94-lb Sack of Cement 7.5
2000
6.75
2500
6
3000
5
3750
Thickness of Top Ring or Plate (if any) - If your base ring design incorporates a top ring, enter its thickness here. If a thickness greater than 0.0 is entered, the software will compute the required thickness of the top plate. If no top ring thickness is entered, the software will not perform top ring thickness calculations. Radial Width of the Top Ring or Plate (if any) - Enter the radial width of the top ring or plate, if any. This is simply the half of (top ring OD - top ring ID). If you enter a value for Thickness of Top Ring or Plate (if any), then you must also enter a value for this option, and it must be positive. Top Ring/Plate Type per Moss - Enter the type of top ring or plate as per Moss (Type 3 = Cap Plate, 4-Continuous Ring). For more information, refer to Dennis Moss Pressure Vessel Design Manual page 129. If you specify type 3 or 4, the software will calculate as per page 130. External Corrosion Allowance - Enter the corrosion allowance that would be applied to the skirt, base plate, gussets and top ring. The external corrosion allowance will simply be added to the required thickness of these components. Dead Weight of Vessel - Enter the weight of the vessel with all peripheral equipment, such as ladders, cages, catwalks, packing, and so on. The working fluid of the vessel should not be included here. This entry is optional and can be 0. Operating Weight of Vessel - Enter the operating weight of the vessel here. This includes all contents and associated hardware. This value must be greater than 0. Test Weight of Vessel - Enter the test weight of the vessel here. This weight will include the fluid used for the hydrotest of the vessel. This entry is optional and can be 0. Operating Weight of Vessel - Enter the total moment exerted on the skirt by the wind, reboilers, attached piping, and so on, when the vessel is operating. This value must be greater than 0. Test Weight of Vessel - Enter the test moment on the basering. The entry for the test moment is optional and can be 0. Operating Moment of Basering - Enter the total moment exerted on the skirt by the wind, reboilers, attached piping, and so on, when the vessel is operating. This value must be greater than 0. Test Moment on Basering - Enter the test moment on the basering. The entry for the test moment is optional and can be 0. Are Gussets to be used? - Check this option if your basering design includes the use of gusset plates otherwise, leave this option unselected. After you select Are Gussets to be used? the software displays addtional parameters for the gussets.
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Base Rings Gusset Plate Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Thickness of Gusset Plates - Enter the thickness of the gusset plates to be used for this base ring. Any allowances for corrosion should be considered when making this entry. Temperature for Gussets (if not ambient) - Enter the temperature for the gusset plates. Usually, the gussets will operate at ambient temperature. If the temperature is above ambient, enter it here. Height of Gussets - Enter the gusset dimension from the base ring to the top of the gusset plate. The forces in the skirt are transmitted to the anchor bolts through the gussets. Distance from Bolts to Gussets - Enter the distance from a bolt to the nearest gusset. Normally, each bolt will have two gussets. This distance would be 1/2 of the spacing between the gusset plates. Average Width of the Gussets - Enter the average width of the gusset plates. Number of Gussets per Bolt - Enter the number of gussets per bolt. Usually, each bolt will have two gusset plates associated with it. For base rings that have a large number of bolts, this may not always be the case. In these occasions, each bolt may have a single gusset plate associated with it. Elastic Module for Gusset Plates - Enter the elastic modulus for the gusset plates. This value is used to determine the allowable stress for plates in compression according to AISC. This is a required value. For most common steels, this value is 29E6 psi. Are Stress Multipliers to be used? - Select this option if you want to increase the allowable stress the program uses for the skirt design. Factor for the Skirt Allowable at the Skirt Top - This factor is multiplied by the skirt operating allowable wherever it is used. For example, the skirt allowable stress at the top would be equal to stress multiplier X joint efficient X skirt operating allowable. If you do not wish to use this value, enter a 1.00 for this value. This multiplier is usually between 1 and 2. Skirt Comp. Allowable Mult. for (B) at Base (OPE) - Enter the factor to be multiplied plied by the Code compression allowable B for the operating case. The software will look at the minimum of this factor times its allowable and the skirt yield stress times its allowable multiplier. This minimum value will then be used as a comparison to the actual compressive stress in the skirt. Skirt Comp. Allowable Mult. for (B) at Base (TEST) - Enter the factor to be multiplied by the Code compression allowable B for the test case. CodeCalc will look at the minimum of this factor times its allowable times 1.5 and the skirt yield stress times its allowable multiplier. This minimum value will then be used, as a comparison to the actual compressive stress in the skirt.
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Base Rings Skirt Comp. Allowable Mult. for (Sy) at Base (OPE) - CodeCalc will multiply the skirt yield stress by this factor. The minimum of this result and the basic hot allowable stress times its factor will be the skirt operating allowable stress. This minimum value will then be used, as a comparison to the actual compressive stress in the skirt. Skirt Comp. Allowable Mult. for (Sy) at Base (TEST) - CodeCalc will multiply the skirt yield stress by this factor. The minimum of this result and the basic hot allowable stress times its factor will be the skirt test allowable stress. This minimum value will then be used as a comparison to the actual compressive stress in the skirt. Add a Tailing Lug - Select this option to perform the tailing lug analysis. The design is based on a lift position where bending does not occur on the tailing lug. The main considerations for the design are the section modulus, shear, and bearing stress at the pinhole and the weld strength. The location of the center of the pinhole will be assumed radially at the edge of the outer most of the top ring or the base ring, whichever is larger. In the absence of the top ring/plate the height of the tailing lug is required. The tailing lug is assumed to be the same material as the gusset or base ring. Note that all input fields pertain to one tail lug. Tail Lug Type - Select the type of tailing lug (Single or Dual) to be used. Tailing Lug Offset from Centerline - Enter the offset dimension (OS) for the dual tailing lug design only. Thickness - Enter the thickness of the tailing lug. Pin Hole Diameter - Enter the pin hole diameter. The center of the pin hole will be placed radially in-line with the larger of the outer most edge of the top ring or the base ring (OD). Weld Size Diameter - Enter the leg weld size. Load on Tailing Lug - Enter the load on the tailing lug.
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Base Rings Lug Height (only if no Top Ring) - Enter the tailing lug height measured form the top of the base ring. If you have a top ring, this value is usually the distance to the top ring.
Results (Base Rings) The tailing lug design consists of a three-part analysis: The base ring assembly ( base ring, skirt and top ring), The strength of weld The tailing lug itself It is assumed that bending does not occur in the tailing lug. In the absence of the top ring only the base ring and the decay length (e) are considered for the section modulus calculation. The table below lists the allowable stresses used to check the design strength. Stress Type
Allowable Value
Shear at Pin Hole
0.4 Sy
Bearing Stress
0.75 Sy
Weld Stress
0.49 Sallow
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SECTION 17
Thin Joints Home tab: Components > Add New Thin Joint Performs elastic analysis for the stresses due to internal and external pressures, and closing or opening of a metal bellows expansion joint typically used in piping systems and heat exchangers. The maximum combined stress is used to calculate the cycle life of the joint, which is based on the appropriate formula in the ASME Code, Section VIII, Division 1, Appendix 26 2007 Edition. The MAWP/MAPnc will also be computed for the bellows. Thin Joints enables engineers and designers to evaluate or design metal bellows expansion joints. Because the module uses ASME Code procedures for evaluating these joints, the calculations are acceptable to fabricators, engineering contractors, and petrochemical companies. Thus a consistent design basis and a simple way to perform the calculations will be established, and individual engineers will be effective in evaluating these critical components. Thin Joints calculates the required thickness and elastic stresses using formulas in ASME Section VIII Code, Division 1, Appendix 26. These formulas take into account both internal and external pressures, and axial joint movement. The appendix covers both reinforced and un-reinforced expansion joints for U-shaped and toroidal types with multiple convolutions and up to a 0.2 inch nominal thickness. Each curve in Appendix 26 was digitized. The program picks points off of the curves and interpolates for the results used in the stress calculations. These parameters are displayed as part of the output. If the selected joint is reinforced or un-reinforced, the software perform the various stress and cycle life computations for that joint type. Thus, there will be no extraneous output for a joint type that is not of interest. In addition, for reinforced expansion joints, the stresses in the reinforcing element and any bolted fastener, which may be holding the ring together, are calculated as well.
In This Section
Expansion Joint Tab (Thin Joints) ................................................. 341 Bellows Tab (Thin Joints) .............................................................. 346
Expansion Joint Tab (Thin Joints) Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. Design Cycle Life, Number of Cycles - Enter the number of cycles for which the expansion joint is to be designed. This value is to be compared to the total number of cycles that this design will be capable of handling. Design Internal Temperatures - Enter the design temperature of the expansion joint. During normal operation, expansion joints typically run cooler than the piping/pressure vessel. Determine that temperature and enter it here.
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Thin Joints Design Internal Pressure - Displays the internal pressure to be exerted on the expansion joint. This analysis is limited to internal pressure only. External pressure is not considered. Design External Temperature - The software automatically updates materials properties for external pressure calculations when you change the design temperature. The design external pressure at this temperature is a completely different design case than the internal pressure case. Therefore, this temperature may be different than the temperature for internal pressure. Many external pressure charts have both lower and upper limits on temperature. If your design temperature is below the lower limit, use the lower limit as your entry. If your temperature is above the upper limit, the component may not be designed for vacuum conditions. Design External Pressure - Enter the design pressure for external pressure analysis. This should be a positive value, such as 14.7 psia. If you enter a zero, the software will not perform external pressure calculations. Value
Result
0.00
No External Calculation
14.7
Full Vacuum Calculation
Design Length of Section - Enter the cumulative design length of the bellow section. For the U-shaped type bellows, the bellow design length can be determined by multiplying the total number of convolution (N) and convolution pitch (q). The design length will also be used to perform the external pressure analysis.
Thin Joint Type - Select the type of thin joint. You can choose: U-Shaped
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Toroidal
If you select Toroidal, the software opens the Toroidal Thin Joint Additional Information dialog box in which you can enter information about the toroidal thin joint. Mean Diameter, Dm - Enter the mean diameter (Dm) of toroidal bellows convolution:
Distance Between Attachment Weld, Lw - Enter the distance between toroidal bellows attachment welds (Lw). Convolution Mean Radius - Enter the mean radius of toroidal bellows convolution (r) as depicted in the toroidal bellows. Reinforcement/Collar Information - Select this option to define ring and collar information. Reinforcement Ring Present? - Select this option to define reinforcing ring information. This option is available only if you select U-shaped thin joint type. Ring Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. This option is available only if you select Reinforcing Ring Present?.
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Thin Joints Cross Sectional Diameter, Dr - Enter the ring cross sectional diameter (Dr). This option is available only if you select Reinforcing Ring Present?.
Elastic Modulus at Design Temperature, Er (optional) - Enter the modulus of elasticity of reinforcing ring member material at design temperature. This option is available only if you select Reinforcing Ring Present? Elastic Modulus at Ambient Temperature, Era (opitonal) - Enter the modulus of elasticity for the bellows material at the bellows ambient temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING table C-6. This option is available only if you select Reinforcing Ring Present? Weld Joint Efficiency, Cwr - Enter the longitudinal weld joint efficiency for reinforcing ring (Cwr) (see UW-12). This option is available only if you select Reinforcing Ring Present?. Fastener Bolt Present? - Enables the entries for the bolt information section of the Reinforcing Data dialog box. This option is available only if you select U-shaped thin joint type. Bolt Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Effective Length, Lf - Enter the effective length of one reinforcing fastener (Lf) that is being stressed. This is typically the distance from the center of the nut to the center of the head on the bolt. This option is available only if you select Fastener Bolt Present?. Cross Sectional Area, Af - Enter the cross-sectional metal area of one reinforcing fastener (Af) that retains the ring. Elastic Modulus at Design Temperature, Ef (optional) - Enter the modulus of elasticity for the fastener material (Ef) at the bellows design temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING table C-6.
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Thin Joints Elastic Modulus at Design Temperature, Efa (optional) - Enter the modulus of elasticity (Efa) for the collar material at the bellows design temperature. This is an optional field and is available only if you select Fastener Bolt Present?. Collar Present? - Select this option to define collar information. This option is available for either type of thin joint. Collar Material Name - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. This option is available only if you select Collar Present?. Cross Sectional Thickness, tc - Enter the collar cross sectional thickness (tc). This option is available only if you select Collar Present?. Cross Sectional Length, Lc - Enter the collar cross sectional length (Lc). For the toroidal bellows, Lc is determined by dividing the collar cross section area with the collar thickness. This option is available only if you select Collar Present?. Elastic Modulus at Design Temperature, Ec (optional) - Enter the modulus of elasticity (Ec) for the collar material at the bellows design temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING table C-6. This option is available only if you select Collar Present?. Elastic Modulus at Design Temperature, Eca (optional) - Enter the modulus of elasticity (Eca) for the collar material at the bellows design temperature. This is an optional field and is available only if you select Collar Present?. Weld Joint Efficiency, Cwc - Enter the longitudinal weld joint efficiency for tangent collar (Cwc) (see UW-12). This option is available only if you select Collar Present?.
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Bellows Tab (Thin Joints) Poisson's Ration, vb - Displays Poisson's ratio for the bellow material (vb). Inside Diameter of Bellows, Db - Enter the inside diameter of the bellows (Db). This value will normally be equal to the pipe or vessel inside diameter. Some geometries are larger in diameter than the attached cylinder. Thus, the bellows ID will be larger than the vessel/pipe ID. Dim.
Description
Af
Cross sectional metal area of one reinforcing fastener.
Db
Inside diameter of bellows convolution.
Dm
Mean diameter of bellows convolution.
Dr
Cross sectional diameter of the reinforcing ring.
Lc
Bellows collar length. For the toroidal bellows, Lc is determined by dividing the collar cross section area with the collar thickness.
Lf
Effective length of one reinforcing fastener.
Lt
End tangent length.
Lw
Distance between toroidal bellows attachment welds.
q
Convolution pitch.
r
Mean radius of toroidal bellows convolution.
t
Bellow nominal thickness of one ply.
tc
Collar thickness.
w
Convolution height.
Sketch
Convolution Depth, w - Enter the distance from the top of the convolution to the trough of the convolution. This is referred as the variable w in the ASME Code.
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Thin Joints Convolution Pitch, q - The convolution pitch is the distance between the tops of successive bellows convolutions. This is referred to as q in the ASME Code. Expansion Joint Opening Per Convolution, deltaq - Deltaq is the total equivalent axial displacement range per convolution. For example, for a total design movement of 1 inch with an expansion joint that had 8 convolutions, this would result in deltaq = 1/8 = 0.125 in/conv. Number of Convolution, N - Enter the total number of convolutions. Nominal Thickness of One Ply, t - Enter the nominal thickness (t) of the plate that the expansion joint is to be made of before it is pressed or formed. Expansion joints are typically thin compared to the matching pipe. Number of Piles, n - Enter the total number of piles used to form the bellows thickness. End Tangent Length, Lt - Displays the end tangent length described as Lt. The Lt variable is required only for the U-Shaped bellows analysis. Fatigue Strength Reduction Factor, Kg - Enter the fatigue strength reduction factor (Kg) per the ASME code Appendix 26. This factor accounts for geometrical stress concentration factors due to thickness variations; weld geometries, surface notches or environmental conditions. The range of factor Kg is between 1 and 4, with its minimum value for smooth geometrical shapes and its maximum for 90 degree welded corners and fillet welds. Fatigue strength reduction factors can be determined from theoretical, experimental, or photo elastic studies. Material Condition - Select the method of which the U-shaped bellow is being made. This selection will be used to determine the multiplier Kf for the combined meridional membrane and bending stress allowables. Material Condition
Kf
Annealed
1.5
Formed
3.0
Elastic Modulus at Design Temperature - Enter the modulus of elasticity for the bellows material at the bellows operating temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING table C-6. Elastic Modulus at Ambient Temperature - Enter the modulus of elasticity for the bellows material at the bellows ambient temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING table C-6.
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SECTION 18
Thick Joints Home tab: Components > Add New Thick Joint Applies to fixed tubesheet exchangers, which require flexible elements to reduce shell and tube longitudinal stresses, tubesheet thickness, or tube-to-tubesheet joint loads. Light gauge bellows type expansion joints within the scope of the Standards of the Expansion Joint Manufacturers Association (EJMA) are not included within the purview of this paragraph. The analysis contained within these paragraphs is based upon the equivalent geometry used in Expansion Joints for Heat Exchangers by S. Kopp and M.F. Sayre; however, the formulas have been derived based upon the use of plate and shell theory. Flanged-only and flanged-and-flued types of expansion joints can be analyzed with this method. (TEMA 8th Edition, Paragraph RCB-8, page 61). The formulas contained in the module are applicable based on the following assumptions: Applied loadings are axial. Torsional loads are negligible. Flexible elements are sufficiently thick to avoid instability. Flexible elements are axisymmetric. All dimensions are in inches. and all forces are in force-pounds. Per TEMA Eighth Edition, Paragraph RCB-8.1, page 61, other systems of units may be used for input and output since the program converts these to inches and pounds for its internal calculations. The sequence of calculations used by the software is: 1. Select a geometry for the flexible element per RCB-8.21 (user-defined). 2. Determine the effective geometry constants per RCB-8.22. 3. Calculate the flexibility factors per RCB-8.3. 4. Calculate the flexible element geometry factors per RCB-8.4. 5. Calculate the overall shell spring rate with all contributions from flexible shell elements per RCB-8.5. 6. Calculate FAX for each condition as shown in Table RCB-8.6. This requires that you run the CodeCalc Tubesheet module to determine the differential expansion and shell side and tube side equivalent pressures. 7. Calculate the flexible element stresses per RCB-8.7 8. Compare the flexible element stresses to the appropriate allowable stresses per the Code for the load conditions as noted in step 6. 9. Modify the geometry and rerun the program if necessary. More than one analysis may be needed to evaluate the hydrotest and uncorroded conditions. Thick expansion joints can also be designed in the Tubesheet module. This integration allows CodeCalc to automatically transfer the needed information between the tubesheet and the expansion joint calculation. Figure Thick Joint Module Geometry shows the geometry for the Thick Joints module. (TEMA Figure RCB-8.21 and RCB-8.22). Both the input geometry and the equivalent geometry used for
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Thick Joints the analysis are shown. The discussion of input data below uses the nomenclature shown on this figure. The stresses computed from the TEMA standard are compared to their respective allowables, as per APP-5 in ASME code Sec. VIII Div. 1. The cycle life is also computed to address the fatigue consideration.
Figure 69: Thick Joint Module Geometry
Figure 70: Flanged Only Expansion Joint
In This Section
Expansion Joint Tab (Thick Joints) ................................................ 351 Shell Tab (Thick Joints) ................................................................. 352 Miscellaneous Tab (Thick Joints) .................................................. 353 Results (Thick Joints) .................................................................... 356
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Thick Joints
Expansion Joint Tab (Thick Joints) Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. Design Temperature - Enter the temperature associated with the internal design pressure. The software will automatically update materials properties for built-in materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Expansion Joint Inside Diameter - Enter the inside diameter of the expansion joint bellows. Note that this is not the diameter at the shell, but the inside diameter at the outside of the bellows. This value is shown ID in the following illustration. Expansion Joint Outside Diameter - Enter the outside diameter of the expansion joint bellows. This value is shown as OD in the following illustration. This is not the diameter at the shell, but the outside diameter at the outside of the bellows. Expansion Joint Flange Wall Thickness - Enter the minimum thickness of the flange or web of the expansion joint, after forming. This will usually be somewhat thinner than the unformed metal. This value is shown as te in the following illustration. Expansion Joint Corrosion Allowance - Enter the corrosion allowance for the expansion joint. This value will be subtracted from the minimum thickness of the flange or web for the joint. Expansion Joint Inside Knuckle Offset - Enter the knuckle radius for an expansion joint with an inside knuckle. Enter zero for an expansion joint with a sharp inside corner. This value is shown ra on the following illustration. Expansion Joint Outside Knuckle Radius - Enter the knuckle radius for an expansion joint with an outside knuckle. Enter zero for an expansion joint with a sharp outside corner (flanged only). This value is shown as rb in the following illustration.
Figure 71: Thick Joint Module Geometry
Expansion Joint Outside Knuckle Offset - Enter the distance from the outer cylinder to the beginning of the knuckle for an expansion joint with an inside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. This value is shown as fb in the following illustration.
In both cases this distance is frequently zero. An expansion joint with a outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint.
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Thick Joints Expansion Joint Outside Knuckle Radius - Enter the knuckle radius for an expansion joint with an outside knuckle. Enter zero for an expansion joint with a sharp outside corner (flanged only). This value is shown as rb in the following illustration. Number of Flexible Shell Elements (1 Convolution = 2 Fse) - Enter the number of flexible shell elements in the flanged/flued expansion joint, as shown in the following illustration:
Shell Tab (Thick Joints) Shell Inside Diameter - Enter the inside diameter of the shell at the point where the expansion joint is attached. This value is shown as G in the illustration. Shell Wall Thickness - Enter the actual wall thickness of the shell at the point where the expansion joint is attached. This value is shown as ts in RCB-8-21 and in the illustration. Shell Cylinder Length - Enter the length of the shell cylinder to the nearest body flange or head. This value is shown as li in the illustration. Per TEMA Paragraph RCB 8-21, lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length. Shell Corrosion Allowance - Enter the corrosion allowance for the shell wall. Some common corrosion allowances are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4" Shell Material - Specify the material name as it appears in the material specification of the appropriate code.
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Thick Joints 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Mean Metal Temperature for Shell and Expansion Joint - Enter the shell mean metal temperature along its length. This value will be used to look up the Young's modulus of the shell, expansion joint and the outer cylinder, if present. As per TEMA technical inquiry #156 (8th edition), the mean metal temperature should be used to look up these Young's modulus values.
Miscellaneous Tab (Thick Joints) Is there an outer cylinder? - Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolute. It may also be true when there is a relatively long cylindrical portion between two half convolutes, as in the case of certain inlet nozzle geometries for heat exchangers. Outer Cylindrical Element Thickness - Enter the actual wall thickness of the outer cylindrical element at the point where the expansion joint is attached. Outer Cylindrical Element Corrosion Allowance - Enter the corrosion allowance for the outer cylindrical element.
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Thick Joints Outer Cylindrical Element Length (Lo) - Enter the length of the outer cylinder to the nearest body flange or head, or to the centerline of the convolute. This value is shown as lo in the following illustration:
Figure 72: Thick Joint Module Geometry
Per TEMA Paragraph RCB 8-21, lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, because the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length. Outer Cylindrical Element Material - Specify the material name as it appears in the material specification of the appropriate code.
to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Shellside Design Pressure - You do not need to run the CodeCalc Tubesheet module program to get this value. It is simply the design pressure for the shell. Tubeside Design Pressure - You do not need to run the CodeCalc Tubesheet module program to get this value. It is simply the design pressure for the channel. Shellside Prime Design Pressure (from Tubesheet) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis. Shellside Prime Design Pressure (from Tubesheet) (corr) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis.
As of CodeCalc version 6.3 and PV Elite version 4.1, the TEMA tubesheet module calcuates the shellside prime design pressure, in both corroded and un-corroded conditions.
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Thick Joints Tubeside Prime Design Pressure (from Tubesheet) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis. Tubeside Prime Design Pressure (from Tubesheet) (corr) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis. Differential Expansion Pressure (from Tubesheet) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis of fixed tubesheet exchangers. Differential Expansion Pressure (from Tubesheet) (corr) - You need to run the CodeCalc Tubesheet module program to get this value. It is listed in the output from the TEMA tubesheet analysis of fixed tubesheet exchangers. Desired Cycle Life, Cycles - Enter the number of desired pressure cycles for this exchanger. This will be compared with the actual computed cycle life of the expansion joint. Differential Expansion? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout. Shellside Pressure? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout. Tubeside Pressure? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout. Shellside + Tubeside Pressure? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout. Shellside + Differential Expansion? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout. Tubeside + Differential Expansion? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Shellside + Tubeside + Differential Expansion? - Check this field if you want to run an analysis for this case. We recommend that you analyze all the cases at first, but you may want to eliminate some cases that are not controlling from the final printout.
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Results (Thick Joints) The three most significant results for the THICK JOINT analysis are the spring constant for the joint, the stresses in the joint, and the cycle life for the joint. These are discussed below.
Spring Constant The software does not calculate the deflection of the joint. Instead it calculates the spring constant for the joint, which can be used in the TUBESHEET module or elsewhere to determine the effect of the joint on the heat exchanger design.
Stresses The software calculates the combined meridional bending and membrane stresses in the expansion joint and the attached cylinders. According to ASME, Section VIII, Division 1, Appendix 5, this stress should be limited to KS, where K is 1.5 for flat sections (the annular ring or cylinders) and 3.0 for curved areas of the inner and outer torus (or sharp corners). S is the basic allowable stress for the expansion joint material at operating temperature. Note, however, that this stress limit applies only to the stresses due to pressure - stresses due to deflection are limited by fatigue considerations rather than stress allowables. Thus the software only prints the allowable membrane plus bending stress for the case of shellside pressure.
Cycle Life The cycle life of the joint is analyzed using the rules in the ASME Code, Section VIII, Division 1, Appendix CC. For Series 3xx stainless steels, nickel-chromium iron alloys, nickel-iron chromium alloys and nickel-copper alloys, the equation for cycle life is as follows: N < [(2.2)/(( 14.2*Kg*Sn)/Eb - 0.03 )]^2.17 For carbon and low alloy steels, Series 4xx stainless steels, and high alloy steels, the equation for cycle life is: N < [(2.0)/(( 15*Kg*Sn)/Eb - 0.011 )]^2.17 Where: Kg = The fatigue strength reduction factor which accounts for the geometrical stress concentration factors due to local thickness variations, weld geometries, and other surface conditions. The range of Kg is 1.0 Add New WRC 297 Calculates local stresses on: Cylinder to cylinder attachments according to Welding Research Council bulletin number 297 or PD 5500, Annex G. Cylinder on sphere attachments according to PD 5500 Annex G. Solid attachments on either a cylinder or a sphere, according to PD 5500 Annex G. WRC 297/Annex G calculates stress intensities in the nozzle and vessel wall at the junction of the intersection on the upper and lower surface at eight different points. Typically, stress intensities can be compared with the yield stress of the material at operating temperature. However, you should read the WRC 297 bulletin carefully for further clarification and evaluation of stress results. Because this method produces extensive output, it may be useful to produce only a summary of results. On the Tools tab, select Configuration, then click Summary on the Miscellaneous tab. This option affects all generated reports in the file.
In This Section
WRC 297 Tab ................................................................................ 367 Vessel Tab ..................................................................................... 369 Nozzle / Attachment Tab ............................................................... 370 Loads Tab ...................................................................................... 372
WRC 297 Tab Item Number - Enter the ID number of the item. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for the item. This entry is optional but strongly encouraged for organizational and support purposes. PD5500 Annex G? - Select to perform analysis according to British Standard Published Document 5500 Annex G instead of Welding Research Council Bulletin 297. The software computes stresses in cylindrical or spherical vessels with or without reinforcing pads. Only round hollow nozzle geometries are computed. When PD5500 Annex G? is selected or cleared, the program automatically converts loads into the coordinate systems used by each method. With PD5500 Annex G? selected, you can modify values such as: Stress concentration factor at the attachment edge Stress concentration factor at the pad edge Nozzle projection Factor for Membrane + Bending (Attachment Edge) - Enter the allowable stress intensity factor for combined membrane and bending stress at the attachment edge. This factor is multiplied by the allowable stress f to obtain maximum allowable stress for the membrane stress
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WRC 297/Annex G plus bending stress. These stresses are in rows 27, 28 and 29 in the printout samples in PD 5500 Annex G. At the attachment edge (nozzle neck), this factor normally has a maximum value of 2.25. Print the Membrane Stress? - Select to compute membrane stress at the attachment edge and enter the allowable stress intensity factor for it. Also enter a value for Factor for Membrane. The example in Annex W does not compute the membrane stress at the attachment edge. You must check the membrane stress before entering a value for Vessel Wall Thickness. According to Annex G, the membrane stress at the attachment edge contains intensified stresses due to the presence of the hole. Factor for Membrane (Attachment Edge) - Enter the allowable stress intensity factor for the membrane at the attachment edge. This factor is multiplied by the allowable stress f to obtain maximum allowable stress for the membrane. These stresses are in rows 32, 33 and 34 in the printout samples in PD 5500 Annex W. At the attachment edge, this factor normally has a value higher than Factor for Membrane (Pad Edge).
This value is only available when Print the Membrane Stress? is selected. The example in Annex W does not compute the membrane stress at the attachment edge. You must check the membrane stress before entering a value for Vessel Wall Thickness. According to Annex G, the membrane stress at the attachment edge contains intensified stresses due to the presence of the hole. Factor for Membrane (Pad Edge) - Enter the allowable stress intensity factor for the membrane at the pad edge. This factor is multiplied by the allowable stress f to obtain maximum allowable stress for the membrane. These stresses are in rows 32, 33 and 34 in the printout samples in PD 5500 Annex W. At the edge of the reinforcement pad, this factor normally has a maximum value of 1.2.
The example in Annex W does not compute the membrane stress at the attachment edge. You must check the membrane stress before entering a value for Vessel Wall Thickness. According to Annex G, the membrane stress at the attachment edge contains intensified stresses due to the presence of the hole. If you would like to check the membrane stress at the attachment edge, see Print the Membrane Stress? and Factor for Membrane (Attachment Edge). Factor for Membrane + Bending (Pad Edge) - Enter the allowable stress intensity factor for combined membrane and bending stress at the pad edge. This factor is multiplied by the allowable stress f to obtain an maximum allowable stress for the membrane stress plus bending stress. These stresses are in rows 27, 28 and 29 in the printout samples in PD 5500 Annex G. At the edge of the pad, this factor is normally 2.0. Nozzle Inside Projection - If the nozzle has a projection inside of the vessel, enter that length. This value is used to determine the pressure stress intensification factor from the Cers/eps graphs in Section 3 of the BS-5500 Code. All of the curves for protruding and flush nozzles are included for analysis. The software uses the smaller of the inside projection and the thickness limit with no pad to calculate the area available in the inward nozzle. You can safely enter a large number such as six or twelve inches if the nozzle continues into the vessel a long distance. Stiffened Length of Vessel Section - Enter the length of the vessel on which the nozzle lies. For vessels without stiffeners or cones, use the entire vessel length including the heads. This
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WRC 297/Annex G value is used along with Offset from Left Tangent Line to compute the equivalent length for off-center loading. Offset from Left Tangent Line - Enter in the distance between the centerline of the nozzles and the left tangent line or appropriate line of support. This value is used in conjunction with Stiffened Length of Vessel Section to compute the equivalent length for off-center loading. Is this Attachment on a Sphere? - Select if the nozzle is located within the spherical portion of an elliptical or torispherical head or is in a spherical head. The software accesses the Annex G curves used to calculate factors for nozzles connected to spheres. If you enter this data manually, enter the spherical diameter. This is especially important for nozzles located in elliptical heads. Design Temperature - Enter the operating temperature of the vessel. The temperature is used to determine the allowable stress of the material from the material database. If the temperature is changed, the allowable stress of the material at operating temperature changes accordingly. Design Pressure - Enter the design pressure of the pressure vessel, in the displayed units. Use a design pressure applicable to the following pressure stress equations: Longitudinal Stress = Pressure * Inside Radius2/(Outside Radius2 - Inside Radius2) Hoop Stress = 2.0 * Longitudinal Stress
The design pressure is used to calculate membrane stresses on the nozzle and vessel wall and axial pressure thrust. For a spherical vessel, the same longitudinal stress equation is used for membrane stress due to internal pressure.
Vessel Tab Specifies pressure vessel parameters for WRC 297 analysis. Vessel Diameter Basis - Select the type of diameter to use for the pressure vessel. Select ID for the inside diameter and OD for the outside diameter. The software uses Diameter Basis for Vessel, Vessel Wall Thickness, and Vessel Corrosion Allowance to determine the mean radius. Vessel Diameter - Enter the diameter of the pressure vessel, in the displayed units. The diameter should be consistent with the selection in Diameter Basis for Vessel. Wall Thickness - Enter the thickness of the pressure vessel wall, in the displayed units. This thickness is measured at the intersection of the nozzle and the vessel. You can type the wall thickness as an equation to account for mill tolerance. For example, if the mill tolerance is 12.5%, type: * 0.875 The software modifies this value if a value for Vessel Corrosion Allowance is defined. Corrosion Allowance - Enter the corrosion allowance. The software adjusts the actual thickness and the inside diameter for the corrosion allowance you enter. Some common corrosion allowances are: 0.0625 - 1/16" 0.1250 - 1/8" 0.2500 - 1/4"
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WRC 297/Annex G Vessel Material - Specify the material name as it appears in the material specification of the appropriate code. 1. Click to open the Material Database Dialog Box (on page 385). The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. For more information on vessel material, see Material Database Dialog Box (on page 385) and Material Properties Dialog Box (on page 422). Stress Concentration Factor for Vessel - Enter a value, typically between 1 and 3, for stress concentration due to weld quality and dimensions in the immediate vicinity of the weld. The stress concentration factor: Accounts for peak stresses - local stress risers in the immediate vicinity of vessel welds due to factors such as sharp corners and lack of fillet weld radii. Peak stresses are considered in fatigue analysis. Applies to the stress calculations in the vessel and the nozzle on both the inside and the outside of the vessel. Is used in pressure stress calculations in the vessel on both the inside and outside of the vessel.
This value is only available for ASME material when PD5500 Annex G? is not selected. . Select the shell you want Merge Shell/Head - Click to bring in data from Shells and Heads to use, and the appropriate data will be brought in from that shell for use in the analysis. Import Nozzle Data - Click to import nozzle data from a PVElite .pvi file.
Nozzle / Attachment Tab Specifies nozzle or other attachment parameters for WRC 297 analysis. Attachment Type - Select the type of attachment. For WRC 297 analysis, Round is the only option. For PD5500 Annex G analysis, select Round, Square, or Rectangular. Nozzle Diameter Basis - Select the type of diameter to use for the nozzle. Select ID for the inside diameter. Select OD for the outside diameter. Nozzle Diameter - Enter the diameter of the nozzle, in the displayed units. The diameter should be consistent with the selection in Diameter Basis for Nozzle. Wall Thickness - Enter the thickness of the nozzle wall at the shell-to-nozzle junction, in the displayed units. Include any allowances for mill tolerance. For example, for a 12.5% mill tolerance, multiply the nozzle wall thickness by 0.875 and enter that value. Corrosion Allowance - Enter the corrosion allowance for the nozzle. This value typically ranges from 0 to 1/4" depending on the service and design specifications.
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WRC 297/Annex G Stress Concentration Factor - Enter a value, typically between 1 and 3, for stress concentration due to weld quality and dimensions in the immediate vicinity of the weld. The stress concentration factor: Accounts for peak stresses - local stress risers in the immediate vicinity of vessel welds due to factors such as sharp corners and lack of fillet weld radii. Peak stresses are considered in fatigue analysis. Applies to the stress calculations in the vessel and the nozzle on both the inside and the outside of the vessel. Is not used in pressure stress calculations. This value is only available for ASME material when PD5500 Annex G? on the Vessel tab is not selected. Attachment Cuts a Hole in Shell - Select if the attachment makes a hole in the pressure vessel. The software then applies a stress concentration factor. Not all attachments cut a hole. For example, a nozzle cuts a hole, but a trunnion does not. This value is only used for ASME analysis, when PD5500 Annex G is not selected on the Vessel tab. Full Length in Longitudinal Direction 2*Cx - If the attachment is square or rectangular instead of a nozzle, enter Cx, the full length of the attachment in the longitudinal direction of the vessel. At the junction of the attachment with the vessel, the attachment is converted to an equivalent round attachment with the following outside radius: ro = Sqrt(Cx * Cy) This value is only used when PD5500 Annex G is selected on the Vessel tab. Full Length in Circumferential Direction 2*Cy - If the attachment is square or rectangular instead of a nozzle, enter Cy, the full length of the attachment in the circumferential direction of the vessel. At the junction of the attachment with the vessel, the attachment is converted to an equivalent round attachment with the following outside radius: ro = Sqrt(Cx * Cy)
This value is only used when PD5500 Annex G is selected on the Vessel tab. Reinforcing Pad? - Select when the nozzle has a pad. The software performs stress calculations at the edge of the pad. Thickness - Enter the thickness of the reinforcing pad. WRC 297 does not directly analyze the reinforcing pad. Instead, the vessel thickness includes the pad thickness. This is analyzed in a consistent manner with the WRC 107 pad method. Diameter - Enter the reinforcing pad diameter along the surface of the vessel. This value is used when the software calculates stresses at the edge of the reinforcing pad. Full Length in Circumferential Direction 2*Cyp - If the attachment is square or rectangular instead of a nozzle, enter Cyp, the full width of the square or rectangular reinforcing pad in the circumferential direction of the vessel. At the junction of the attachment with the vessel, the pad is converted to an equivalent round pad with the following outside radius: ro = Sqrt(Cxp * Cyp) This value is only used when PD5500 Annex G is selected on the Vessel tab. Full Length in Longitudinal Direction 2*Cxp - If the attachment is square or rectangular instead of a nozzle, enter Cxp, the full length of the square or rectangular reinforcing pad in the longitudinal direction of the vessel. At the junction of the attachment with the vessel, the pad is converted to an equivalent round pad with the following outside radius: ro = Sqrt(Cxp * Cyp) This value is only used when PD5500 Annex G is selected on the Vessel tab.
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WRC 297/Annex G
Loads Tab Specifies load parameters for WRC 297 analysis. Radial Load "P" - Enter the axial load P that is trying to push the nozzle into the vessel or pull the nozzle out of the vessel. Enter this value according to the WRC 107 and BS 5500 conventions below. In WRC 107, positive loads try to "push" the nozzle while negative loads try to "pull" the nozzle. In BS 5500, positive loads try to "pull" the nozzle while negative loads try to "push" the nozzle. Axial force does not include the effect of pressure thrust. For more information, see Add Axial Pressure Thrust?. Circumferential Shear "VC" - Enter the circumferential shear load VC (for WRC 107) or FC (for BS 5500). Enter this value according to the WRC 107 and BS 5500 conventions below. Longitudinal Shear "VL" - Enter the longitudinal shear load VL (for WRC 107) or FL (for BS 5500). Enter this value according to the WRC 107 and BS 5500 conventions below. Torsional Moment (MT) - Enter the torsional moment MT. Enter this value according to the WRC 107 and BS 5500 conventions below. Circumferential Moment (MC) - Enter the circumferential moment MC or M1. Enter this value according to the WRC 107 and BS 5500 conventions below. Longitudinal Moment (ML) - Enter the longitudinal moment ML or M2. Enter this value according to the WRC 107 and BS 5500 conventions below. Include Pressure Thrust? - Select to add the force due to pressure times internal pipe area to the Axial Force "P".
This option is only available for ASME material when PD5500 Annex G? on the Vessel tab is not selected. A negative axial pressure thrust is subtracted from P. For more information on pressure thrust, see the July 2001 COADE Newsletter http://www.coade.com/newsletters/jul01.pdf. Use Pressure Stress Indices (Div. 2 AD 560.7)? - Select to multiply the nominal pressure stress by the stress indices of paragraph AD 560.7 of ASME Code Section VIII, Division 2. This calculates the surface stress intensity.
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This option is only available for ASME material when PD5500 Annex G? on the Vessel tab is not selected. These indices are not used in the calculation of the pressure stress on the nozzle. The software multiplies the pressure stress on the nozzle by a factor of 1.2.
CodeCalc User's Guide
WRC 297/Annex G Enter the axial load P that is trying to push the nozzle into the vessel or pull the nozzle out of the vessel. Enter this value according to the WRC 107 and BS 5500 conventions below.
In WRC 107, positive loads try to "push" the nozzle while negative loads try to "pull" the nozzle. In BS 5500, positive loads try to "pull" the nozzle while negative loads try to "push" the nozzle. Axial force does not include the effect of pressure thrust. For more information, see Add Axial Pressure Thrust?.
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WRC 297/Annex G
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SECTION 22
Appendix Y Flanges Home tab: Components > Add New Appendix Y Flange Performs stress evaluations of Class 1, category 1, 2, or 3 flanges that form identical flange pairs. This module conforms to the latest version of the ASME Code Section VIII Division 1 Appendix Y, 2007 Edition. The analysis of an Appendix Y flange is similar in many ways to the Appendix 2 evaluation. However, these flanges have metal-to-metal contact outside the bolt circle, unlike the types evaluated in Appendix 2. These flanges typically have a soft, self-sealing o-ring gasket that sits in the recess of one of the flange faces. The loads on the flanges are generated in a very similar manner to those in Appendix 2. The actual stress evaluation, however, is different. This software evaluates flanges with or without hubs. A category 1 flange is an integral flange. The integral type must have the hub information specified. A category 2 flange is a loose type flange with a hub where the hub strengthens the assembly. A category 3 flange is a loose type flange where no credit is taken for the strengthening effect of the hub. Based on user input (especially flange type and hub information), the category is automatically determined.
Gasket and Gasket Factors One critical value the software computes is the diameter of the load reaction. This value is termed G and is a function of where the gasket sits on the flange face. The value of G is typically the average of the gasket inner and outer diameters. For these types of flanges, the gasket ID is usually equal to the flange face ID and the gasket OD is usually equal to the flange face OD. Two other important factors are m and Y. The value of m is the leak pressure ratio, and the value of Y is the gasket design seating stress. This Appendix presumes these gaskets to be self-sealing (see the definition of Hg in the Code). Thus, the m and Y factors should both be 0.0. If any other value is entered, the user-defined values are echoed but the software uses values of 0.0 for both.
In This Section
Flange Tab ..................................................................................... 376 Hubs/Bolts Tab .............................................................................. 378 Gasket Tab .................................................................................... 380
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Appendix Y Flanges
Flange Tab Item Number - Enter an ID number for the item. This can be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description - Enter an alpha-numeric description for this item. This entry is optional, but strongly encouraged for organizational and support purposes. Type of Flange - Select the type of flange: Integral or Loose. Integral flanges generally have hubs and act as an integral component with the shell to which there are attached. Loose flanges typically do not have hubs and are attached by fillet welds. This module computes Class 1, Category 1, 2, or 3 flanges. Design Pressure - Enter the specified design pressure (P). Design Temperature - Enter the design temperature for the flange. This value will be used to look up the allowable stresses for the material at design temperature. Flange Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list. The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material. Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials. Flange Thickness - Enter the flange thickness. The flange thickness is shown in the diagram below.
Figure 75: Flange Diagram
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Appendix Y Flanges Corrosion Allowance - Enter the specified corrosion allowance. Values, such as the flange ID and hub thicknesses, will be corroded according to the flange type. Note, however, that for either type of flange (loose or integral), the flange thickness, T, will not be corroded since the contained fluid is not exposed to the flange thickness. Flange Inside Diameter - Enter the inside diameter of the flange. This is dimension B in the following illustration, which extends to the equivalent left side of the flange, not shown:
Figure 76: Flange Diagram
Flange Outside Diameter - Enter the outside diameter of the flange. This is dimension A in the ASME Code.
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Appendix Y Flanges
Hubs/Bolts Tab Gasket Outer Diameter - Enter the outer diameter of the gasket. The software uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Inner Diameter - Enter the inner diameter of the gasket. The software uses the maximum of the flange face ID and the gasket ID to calculate the inner contact point of the gasket. Hub Thickness - Small End - Enter the thickness of the small end of the hub. This value is referred to as G0 in the ASME code. The corrosion allowance will be subtracted from this value (for integral types only). For weld neck flange types, this is the thickness of the shell at the end of the flange. For slip on flange geometries, this is the thickness of the hub at the small end. For flange geometries without hubs, this thickness may be entered as zero.
Figure 77: Flange Diagram
Hub Thickness - Large End - Enter the thickness of the large end of the hub. This value is referred to as G1 in the ASME code. The corrosion allowance will be subtracted from this value (for integral types). It is permissible for the hub thickness at the large end to equal the hub thickness at the small end. For flange geometries without hubs, this thickness may be entered as zero. Hub Length - Enter the hub length. This value is refered to as H in the ASME code. For flange geometries without hubs, this length may be entered as zero. When analyzing an optional type flange that is welded at the hub end, the hub length should be the leg of the weld, and the thickness at the large end should include the thickness of the weld. Bolt Material - Specify the material name as it appears in the material specification of the appropriate code. to open the Material Database Dialog Box (on page 385). 1. Click The software displays the Material Database dialog box, which displays read-only information about the selected material. 2. Select the material that you want to use from the list.
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Appendix Y Flanges The software displays the material properties. 3. Click Select to use the material, or click Back to select a different material.
Alternatively, you can type the material name as it appears in the material specification. If you type in the name, the software retrieves the first material it finds in the material database with a matching name. To modify material properties, go to the Tools tab and select Edit/Add Materials.
Diameter of Bolt Circle - Enter the diameter of the bolt circle of the flange. This is dimension C in the ASME Code.
Figure 78: Flange Diagram
Nominal Bolt Diameter - Enter the nominal bolt diameter. The tables of bolt diameter included in the software range from 0.5 to 4.0 inches. This value is used to determine the bolt space correction factor. If you have bolts that are larger or smaller than this value, enter the nominal size in this field. Also, enter the root area of one bolt in the Root Area cell. Bolt Root Area - If your bolted geometry uses bolts that are not the standard TEMA or UNC types, you must enter the root area of a single bolt in this field. This option is used only if bolt root area is greater than 0.0. Number of Bolts - Enter the number of bolts to be used in the flange analysis. The number of bolts is almost always a multiple of four.
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Appendix Y Flanges
Gasket Tab
Facing Column
Gasket Factor m
Gasket Material
Seating Stress y, psi (MPa)
Gasket Factor - The values of m and y shown in the following table are listed in ASME Section VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y, please contact your gasket manufacturer.
0.00
0
II
Below 75A Shore Durometer
0.50
0
II
75A Shore Durometer or higher
1.00
200 (1.4)
II
1/8 inch thick
2.00
1600 (11)
II
1/16 inch thick
2.75
3700 (26)
II
1/32 inch thick
3.50
6500 (45)
II
Elastomer with cotton fabric insertion
1.25
400 (2.8)
II
3 ply
2.25
2200 (15)
II
2 ply
2.50
2900 (20)
II
1 ply
2.75
3700 (26)
II
Vegetable Fiber
1.75
1100 (7.6)
II
Carbon Steel
2.50
10000 (69)
II
Stainless Steel, Monel, and nickel-base alloys
3.00
10000 (69)
II
Soft aluminum
2.50
2900 (20)
II
Soft copper or brass
2.75
3700 (26)
II
Iron or soft steel
3.00
4500 (31)
II
Monel or 4-6% Chrome
3.25
5500 (38)
II
Stainless - steels and nickel-base alloys
3.50
6500 (45)
II
2.75
3700 (26)
II
Self energizing types (O rings, elastomer, other gasket types considered as self-sealing) Elastomers without fabric or high percent of mineral fiber
Mineral fiber with suitable binder for operating conditions
Elastomer with mineral fiber fabric insertion (with or without wire reinforcment)
Spiral-wound metal, mineral fiber filled
Corrugated metal, mineral fiber inserted or Corrugated metal, jacketed, mineral fiber filled
Corrugated metal, not filled Soft aluminum
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Facing Column
Seating Stress y, psi (MPa)
Gasket Material
Gasket Factor m
Appendix Y Flanges
Soft copper or brass
3.00
4500 (31)
II
Iron or soft steel
3.25
5500 (38)
II
Monel or 4-6% Chrome
3.50
6500 (45)
II
Stainless steel
3.75
7600 (52)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel
3.50
8000 (55)
II
4-6% chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
3.75
9000 (62)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel or 4-6% Chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
4.25
10100 (70)
II
Soft aluminum
4.00
8800 (61)
I
Soft copper or brass
4.75
13000 (90)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steels and nickel-base alloys
6.50
26000 (180)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steel
6.50
26000 (180)
I
Flat metal, jacketed, mineral fiber filled
Grooved metal
Solid flat metal
Ring Joint
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Appendix Y Flanges
Facing Column
Gasket Factor m
Gasket Material
Seating Stress y, psi (MPa)
Gasket Design and Seating Stress - The values of m and y shown in the following table are listed in ASME Section VIII Div. 1 code in App. 2. As stated in the code, these are only suggested values. For more accurate values of m and y, please contact your gasket manufacturer.
0.00
0
II
Below 75A Shore Durometer
0.50
0
II
75A Shore Durometer or higher
1.00
200 (1.4)
II
1/8 inch thick
2.00
1600 (11)
II
1/16 inch thick
2.75
3700 (26)
II
1/32 inch thick
3.50
6500 (45)
II
Elastomer with cotton fabric insertion
1.25
400 (2.8)
II
3 ply
2.25
2200 (15)
II
2 ply
2.50
2900 (20)
II
1 ply
2.75
3700 (26)
II
Vegetable Fiber
1.75
1100 (7.6)
II
Carbon Steel
2.50
10000 (69)
II
Stainless Steel, Monel, and nickel-base alloys
3.00
10000 (69)
II
Soft aluminum
2.50
2900 (20)
II
Soft copper or brass
2.75
3700 (26)
II
Iron or soft steel
3.00
4500 (31)
II
Monel or 4-6% Chrome
3.25
5500 (38)
II
Stainless - steels and nickel-base alloys
3.50
6500 (45)
II
Soft aluminum
2.75
3700 (26)
II
Soft copper or brass
3.00
4500 (31)
II
Self energizing types (O rings, elastomer, other gasket types considered as self-sealing) Elastomers without fabric or high percent of mineral fiber
Mineral fiber with suitable binder for operating conditions
Elastomer with mineral fiber fabric insertion (with or without wire reinforcment)
Spiral-wound metal, mineral fiber filled
Corrugated metal, mineral fiber inserted or Corrugated metal, jacketed, mineral fiber filled
Corrugated metal, not filled
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Facing Column
Seating Stress y, psi (MPa)
Gasket Material
Gasket Factor m
Appendix Y Flanges
Iron or soft steel
3.25
5500 (38)
II
Monel or 4-6% Chrome
3.50
6500 (45)
II
Stainless steel
3.75
7600 (52)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel
3.50
8000 (55)
II
4-6% chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
3.75
9000 (62)
II
Soft aluminum
3.25
5500 (38)
II
Soft copper or brass
3.50
6500 (45)
II
Iron or soft steel
3.75
7600 (52)
II
Monel or 4-6% Chrome
3.75
9000 (62)
II
Stainless steels and nickel-base alloys
4.25
10100 (70)
II
Soft aluminum
4.00
8800 (61)
I
Soft copper or brass
4.75
13000 (90)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steels and nickel-base alloys
6.50
26000 (180)
I
Iron or soft steel
5.50
18000 (124)
I
Monel or 4-6% chrome
6.00
21800 (150)
I
Stainless steel
6.50
26000 (180)
I
Flat metal, jacketed, mineral fiber filled
Grooved metal
Solid flat metal
Ring Joint
Is There a Partition Gasket? - If your exchanger geometry has a pass partition gasket, then check this field. The software opens the Partition Gasket dialog box so that you can define the overall length and width of the gasket. Length of Partition Gasket - This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. Width of Partition Gasket - Enter the width of the pass partition gasket. Using these properties and the known width, the software computes the effective seating width and the gasket loads contributed by the partition gasket. Specify External Loads? - In order to compute the equivalent pressure, the external loads acting on the flange must be specified, if applicable. Normally, there would be no external loads for these types of flanges. When you check this field, the software displays a pop-up form in
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Appendix Y Flanges which you enter this loading data. Loading data of this nature typically comes from a stress analysis program, such as CAESAR II. Node Number - Enter the node number of this flange. This entry represents the node point in a stress analysis model from which the loads are obtained. Node Number is an optional entry. Axial Force - Enter the magnitude of the external axial force which acts on this flange. Bending Moment - Enter the magnitude of the external bending moment which acts on this flange.
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SECTION 23
Material Dialog Boxes The Material Database and Material Properties dialog boxes are available in many commands throughout the software. Material Database Dialog Box (on page 385) Material Properties Dialog Box (on page 422)
Material Database Dialog Box Displays materials and material properties. Select the needed material. To modify material properties, go to the Tools tab and select Edit/Add Materials. Below are examples of standard ASME material names. Plates and Bolting
SA-516 55 SA-516 60 SA-516 65 SA-516 70 SA-193 B7 SA-182-F1 SA-182 F1 SA-182 F11 SA-182 F12 SA-182 F22 SA-105 SA-36 SA-106 B
Stainless Steels SA-240 304 SA-240 304L SA-240 316 SA-240 316L SA-193 B8 Aluminum
SB-209 SB-234 Titanium
SB-265 1 SB-265 26H Nickel
SB-409 SB-424
If you used old CodeCalc material names in previous CodeCalc versions, see the CodeCalc appendix for comparisons with ASME code names. Material Search String - Enter part of the material name to search against. Find Next Match - Click to go to the next matching material name available. UNS # Search String - Enter part of the UNS # to search against. Select Material - Click to use the selected material.
Cancel - Exit the dialog box without selecting a material.Material Database Notes These notes are valid for the 2010 edition of ASME Section II Part D. If using an older database, these notes may not be correct or meaningful as they are periodically changed by ASME. Division 1 Material Notes for Table 1A (Ferrous Materials) - Customary (a)
The following abbreviations are used: Applic., Applicability; Cond., Condition; Desig., Designation; Smls., Seamless; and Wld., Welded.
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Material Dialog Boxes
386
(b)
The stress values in this Table may be interpolated to determine values for intermediate temperatures.
(c)
For Section VIII applications, stress values in restricted shear such as dowel bolts or similar construction in which the shearing member is so restricted that the section under consideration would fail without reduction of area shall be 0.80 times the value in the above table.
(d)
For Section VIII applications, stress values in bearing shall be 1.60 times the values in the above Table.
(e)
Stress values for –20 to 100F are applicable for colder temperatures when toughness requirements of Section III or Section VIII are met.
(f)
An alternative typeface is used for stress values obtained from time dependent properties (see notes T1 - T10 )
(h)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
G1
To these stress values a casting quality factor as specified in PG-25 of Section I or UG-24 of Section VIII, Division 1 shall be applied.
G2
These stress values include a joint efficiency factor of 0.60.
G3
These stress values include a joint efficiency factor of 0.85.
G4
For Section I applications, these stresses apply when used for boiler, water wall, superheater, and economizer tubes that are enclosed within a setting. A joint efficiency factor of 0.85 is included in values above 850F.
G5
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66 2/3 % but do not exceed 90% of the yield strength at temperature. Use of these stresses may results in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors which, when applied to the yield strength values shown in table Y-1, will give allowable stress values that will result in lower values of permanent strain.
G6
Creep-fatigue, thermal ratcheting, and environmental effects are increasingly signiificant failure modes at temperatures in excess of 1500F and shall be considered in the design.
G7
Deleted
G8
Deleted
G9
For Section III applications, the stress-rupture test is not required for design temperatures 800F and below.
G10
Upon prolonged exposure to temperatures above 800F, the carbide phase of carbon steel may be converted to graphite.
G11
Upon prolonged exposure to temperatures above 875F, the carbide phase of carbon–molybdenum steel may be converted to graphite.
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Material Dialog Boxes G12
At temperatures above 1000F, these stress values apply only when the carbon is 0.04% or higher on heat analysis.
G13
These stress values at 1050F and above shall be used only when the grain size is ASTM No. 6 or coarser.
G14
These stress values shall be used when the grain size is not determined or is determined to be finer than ASTM No. 6.
G15
For Section I applications, use is limited to stays as defined in PG-13 except as permitted by PG-11.
G16
For Section III Class 3 applications, these S values do not include a casting quality factor. Statically and centrifugally cast products meeting the requirements of NC-2570 shall receive a casting quality factor of 1.00.
G17
For Section III Class 3 applications, statically and centrifugally cast products meeting the requirements of NC-2571(a) and (b), and cast pipe fittings, pumps, and valves with inlet piping connections of 2 in. nominal pipe size and less, shall receive a casting quality factor of 1.00. Other casting quality factors shall be in accordance with the following: a. for visual examination, 0.80; b. for magnetic particle examination 0.85; c. for liquid penetrant examination, 0.85; d. for radiography, 1.00; e. for ultrasonic examination, 1.00; and f. for magnetic particle or liquid penetrant plus ultrasonic examination or radiography, 1.00.
G18
See Table Y-1 for yield strength values as a function of thickness over this range. Allowable stresses are independent of yield strength in this thickness range.
G19
Although external pressure chart title is listed for SA-537, use Class 1 curves for this specification.
G20
Although external pressure chart title is listed for SA-537, use Class 2 curves for this specification.
G21
For external pressure chart listing, use Class 1 curve.
G22
For Section I applications, use of external pressure charts for material in the form of barstock is permitted for stiffening rings only.
G23
For temperatures above the maximum temperature shown on the external pressure chart for this material, Fig. CS-2 may be used for the design using this material.
G24
A factor of 0.85 has been applied in arriving at the maximum allowable stress values in tension for this material. Divide tabulated values by 0.85 for maximum allowable longitudinal tensile stress.
G25
For Section III applications, for both Class 2 and Class 3, the completed vessel after final heat treatment shall be examined by the ultrasonic method in accordance with NB-2542 except that angle beam examination in both the circumferential and the axial directions.
G26
Material that conforms to Class 10, 11, or 12 is not permitted.
G27
Material that conforms to Class 11 or 12 is not permitted.
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Material Dialog Boxes
388
G28
Supplementary Requirement S15 of SA-781, Alternate Tension Test Coupons and Specimen Locations for Castings, is mandatory.
G29
For Section III applications, impact testing in accordance with the requirements of NC-2300 is required for Class 2 components and in accordance with ND-2300 for Class 3 components.
G30
For Section VIII applications, these stress values are based on expected minimum values of 45,000 psi tensile strength and yield strength of 20,000 psi resulting from loss of strength due to thermal treatment required for the glass coating operation. UG-85 does not apply.
G31
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints where freedom from leakage over a long period of time without retightening is required, lower stress values may be necessary as determined from the flexibility of the flange and bolts and corresponding relaxation properties.
G32
This steel may be expected to develop embrittlement after service at moderately elevated temperature; see Appendix 6. For P-No. 10H Gr. 1 materials, exposure to temperatures in the range of 1100F to 1700ºF for relatively short periods of time may result in severe loss of ductility due to sigma formation; see 6-340 and 6-360.
G33
These stresses are based on weld metal properties.
G34
For Section I, use is limited to PEB-5.3. See PG-5.5 for cautionary note.
H1
For temperatures above 1000F, these stress values may be used only if the material is solution treated by heating to the minimum temperature specified in the material specification, but not lower than 1900F, and quenching in water or rapidly cooling by other means.
H2
For temperatures above 1000F, these stress values may be used only if the material is heat treated by heating to a minimum temperature of 2000F, and quenching in water or rapidly cooling by other means.
H3
DELETED
H4
DELETED
H5
For Section III applications, if heat treatment is performed after forming or fabrication, it shall be performed at 1500–1850F for a period of time not to exceed 10 min at temperature, followed by rapid cooling. For Section VIII applications involving consideration of heat treatment after forming or welding, see table UHA-32 for P-No. 10K, group No.1 materials.
H6
Material shall be solution annealed at 2010F to 2140F, followed by a rapid cooling in water or air.
S1
For Section I applications, stress values at temperatures of 850F and above are permissible but, except for tubular products 3 in. O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S2
For Section I applications, stress values at temperatures of 900F and above are permissible but, except for tubular products 3 in. O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
CodeCalc User's Guide
Material Dialog Boxes S3
For Section I applications, stress values at temperatures of 1000F and above are permissible but, except for tubular products 3 in. O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S4
For Section I applications, stress values at temperatures of 1150F and above are permissible but, except for tubular products 3 in. O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S5
Material that conforms to Class 10, 11, or 12 is not permitted when the nominal thickness of the material exceeds 3/4 in.
S6
Material that conforms to Class 10, 11, or 12 is not permitted when the nominal thickness of the material exceeds 1-1/4 in.
S7
The maximum thickness of unheat-treated forgings shall not exceed 3-3/4 in. The maximum thickness as-heat-treated may be 4 in.
S8
The maximum section thickness shall not exceed 3 in. for double-normalized-and-tempered forgings, or 5 in. for quenched-and-tempered forgings.
S9
Both NPS 8 and larger, and schedule 140 and heavier.
S10
The maximum pipe size shall be NPS 4 (Dn 100) and the maximum thickness in any pipe size shall be Schedule 80.
T1
Allowable stresses for temperatures of 700ºF and above are values obtained from time-dependent properties.
T2
Allowable stresses for temperatures of 750ºF and above are values obtained from time-dependent properties.
T3
Allowable stresses for temperatures of 850ºF and above are values obtained from time-dependent properties.
T4
Allowable stresses for temperatures of 900ºF and above are values obtained from time-dependent properties.
T5
Allowable stresses for temperatures of 950ºF and above are values obtained from time-dependent properties.
T6
Allowable stresses for temperatures of 1000ºF and above are values obtained from time-dependent properties.
T7
Allowable stresses for temperatures of 1050ºF and above are values obtained from time-dependent properties.
T8
Allowable stresses for temperatures of 1100ºF and above are values obtained from time-dependent properties.
T9
Allowable stresses for temperatures of 1150ºF and above are values obtained from time-dependent properties.
T10
Allowable stresses for temperatures of 800ºF and above are values obtained from time-dependent properties.
W1
Not for welded construction.
W2
Not for welded construction in Section III.
W3
Welded.
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Material Dialog Boxes
390
W4
Nonwelded, or welded if the tensile strength of the Section IX reduced section tension test is not less than 100 ksi.
W5
Welded, with the tensile strength of the Section IX reduced tension test less than 100 ksi but not less than 95 ksi.
W6
This material may be welded by the resistance technique.
W7
In welded construction for temperatures above 850ºF, the weld metal has a carbon content of greater than 0.05%.
W8
Welding and oxygen or other thermal cutting processes are not permitted when carbon content exceeds 0.35% by heat analysis.
W9
For Section I applications, for pressure retaining welds in 2-1/4Cr–1Mo materials, other than circumferential butt welds less than or equal to 3-1/2 in. in outside diameter, when the design metal temperatures exceed 850F, the weld metal shall have a carbon content greater than 0.05%.
W10
For Section III applications, material that conforms to Class 10, 13, 20, 23, 30, 33, 40, 43, 50, or 53 is not permitted for Class 2 and Class 3 construction when a weld efficiency factor of 1.00 is used in accordance with Note W12.
W11
For Section VIII applications, Section IX, QW-250 Variables QW-404.12, QW-406.3, QW-407.2, and QW-409.1 shall also apply to this material. These variables shall be applied in accordance with the rules for welding of Part UF.
W12
These S values do not include a longitudinal weld efficiency factor. For Section III applications, for materials welded without filler metal, ultrasonic examination, radiographic examination, or eddy current examination, in accordance with NC-2550, shall provide a longitudinal weld efficiency factor of 1.0. Other long. weld efficiency factors shall be in accordance with the following: a. for single butt weld, with filler metal, 0.80; b. for single or double butt weld, without filler metal, 0.85; c. for double butt weld, with filler metal, 0.90; d. for single or double butt weld, with radiography, 1.00.
W13
For Section I applications, electric resistance and autogenous welded tubing may be used with these stresses, provided the following additional restrictions and requirements are met: a. The tubing shall be used for boiler, waterwall, superheater, and economizer tubes that are enclosed within the setting. b. The maximum outside diameter shell be 3.5 in. c. The weld seam of each tube shall be subjected to an angle beam ultrasonic inspection per SA-450. d. A complete volumetric inspection of the entire length of each tube shall be performed in accordance with SA-450. e. Material test reports shall be supplied.
W14
These S values do not include a weld factor. For Section VIII Division 1 applications using welds made without filler metal, the tabulated tensile strength values should be multiplied by 0.85. For welds made with filler metal, check UW-12 of Section VIII Division 1.
CodeCalc User's Guide
Material Dialog Boxes W15
The Nondestructive Electric Test requirements of SA-53 Type E pipe are required for all sizes. The pipe sahll be additionally marked "NDE" and so noted on the material certification.
Division 1 Material Notes for Table 1A (Ferrous Materials) - Metric (a)
The following abbreviations are used: Norm. rld., Normalized rolled; Smls., Seamless; Sol. ann., Solution annealed; and Wld., Welded.
(b)
The stress values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures are rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated.
(c)
For Section VIII and XII applications, stress values in restricted shear, such as dowel bolts or similar construction in which the shearing member is so restricted that the section under consideration would fail without reduction of area, shall be 0.80 times the values in Division 1 Material Notes for Table 1A (Ferrous Materials) Customary.
(d)
For Section VIII and XII applications, stress values in bearing shall be 1.60 times the values in Division 1 Material Notes for Table 1A (Ferrous Materials) - Customary.
(e)
Stress values for -30ºC to 40ºC are applicable for colder temperatures when the toughness requirements of Section III, VIII, or XII are met.
(f)
An alternative typeface is used for stress values obtained from time-dependent properties (see Notes T1 through T10).
(g)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SA-516/SA-516M), the values listed in this Table are applicable to either the customary U.S. version of the material specification or the SI units version of the material specification. For example, the values listed for SA-516 Grade 70 are used when SA-516M Grade 485 is used in construction.
(h)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
G1
To these stress values a casting quality factor as specified in PG-25 of Section I; UG-24 of Section VIII, Division 1; or TM-190 of Section XII is applied.
G2
These stress values include a joint efficiency factor of 0.60.
G3
These stress values include a joint efficiency factor of 0.85.
G4
For Section I applications, these stresses apply when used for boiler, water wall, superheater, and economizer tubes that are enclosed within a setting. A joint efficiency factor of 0.85 is included in values above 450ºC.
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Material Dialog Boxes
392
G5
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66 2/3 % but do not exceed 90% of the yield strength at temperature. Use of these stresses may results in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors which, when applied to the yield strength values shown in Table Y-1, will give allowable stress values that will result in lower values of permanent strain.
G6
Creep-fatigue, thermal ratcheting, and environmental effects are increasingly significant failure modes at temperatures in excess of 825ºC and are considered in the design.
G9
For Section III applications, the use of these materials shall be limited to materials for tanks covered in Subsections NC and ND, component supports, and for nonpressure-retaining attachments (NC/ND-2190).
G10
Upon prolonged exposure to temperatures above 425ºC, the carbide phase of carbon steel may be converted to graphite. See Appendix A, A-240.
G11
Upon prolonged exposure to temperatures above 475ºC, the carbide phase of carbon–molybdenum steel may be converted to graphite. See Appendix A, A-240.
G12
At temperatures above 550ºC, these stress values apply only when the carbon is 0.04% or higher on heat analysis.
G13
These stress values at 575ºC and above shall be used only when the grain size is ASTM No. 6 or coarser.
G14
These stress values shall be used when the grain size is not determined or is determined to be finer than ASTM No. 6.
G15
For Section I applications, use is limited to stays as defined in PG-13 except as permitted by PG-11.
G16
For Section III Class 3 applications, these S values do not include a casting quality factor. Statically and centrifugally cast products meeting the requirements of NC-2570 shall receive a casting quality factor of 1.00.
G17
For Section III Class 3 applications, statically and centrifugally cast products meeting the requirements of NC-2571(a) and (b), and cast pipe fittings, pumps, and valves with inlet piping connections of 2 in. nominal pipe size and less, shall receive a casting quality factor of 1.00. Other casting quality factors shall be in accordance with the following For visual examination, 0.80. For magnetic particle examination 0.85. For liquid penetrant examination, 0.85. For radiography, 1.00. For ultrasonic examination, 1.00. For magnetic particle or liquid penetrant plus ultrasonic examination or radiography, 1.00.
G18
See Table Y-1 for yield strength values as a function of thickness over this range. Allowable stresses are independent of yield strength in this thickness range.
CodeCalc User's Guide
Material Dialog Boxes G22
For Section I applications, use of external pressure charts for material in the form of bar stock is permitted for stiffening rings only.
G23
For temperatures above the maximum temperature shown on the external pressure chart for this material, Fig. CS-2 may be used for the design using this material.
G24
A factor of 0.85 has been applied in arriving at the maximum allowable stress values in tension for this material. Divide tabulated values by 0.85 for maximum allowable longitudinal tensile stress.
G25
For Section III applications, for both Class 2 and Class 3, the completed vessel after final heat treatment is examined by the ultrasonic method in accordance with NB-2542 except that angle beam examination in both the circumferential and the axial directions may be performed in lieu of the straight beam examination in the axial direction. The tensile strength does not exceed 860 MPa.
G26
Material that conforms to Class 10, 11, or 12 is not permitted.
G27
Material that conforms to Class 11 or 12 is not permitted.
G28
Supplementary Requirement S15 of SA-781, Alternate Mechanical Test Coupons and Specimen Locations for Castings, is mandatory.
G29
For Section III applications, impact testing in accordance with the requirements of NC-2300 is required for Class 2 components and in accordance with ND-2300 for Class 3 components.
G30
For Section VIII applications, these stress values are based on expected minimum values of 310 MPa tensile strength and yield strength of 140 MPa resulting from loss of strength due to thermal treatment required for the glass coating operation. UG-85 does not apply.
G31
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints where freedom from leakage over a long period of time without retightening is required, lower stress values may be necessary as determined from the flexibility of the flange and bolts and corresponding relaxation properties.
G32
This steel may be expected to develop embrittlement after service at moderately elevated temperature. See Appendix A, A-340 and A-360.
G33
These stresses are based on weld metal properties.
G34
For Section I, use is limited to PEB-5.3. See PG-5.5 for cautionary note.
H1
For temperatures above 550ºC, these stress values may be used only if the material is solution treated by heating to the minimum temperature specified in the material specification, but not lower than 1040ºC, and quenching in water or rapidly cooling by other means.
H2
For temperatures above 550ºC, these stress values may be used only if the material is heat treated by heating to a minimum temperature of 1095ºC, and quenching in water or rapidly cooling by other means.
H5
For Section III applications, if heat treatment is performed after forming or fabrication, it shall be performed at 825ºC–1000ºC for a period of time not to exceed 10 min at temperature, followed by rapid cooling.
CodeCalc User's Guide
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Material Dialog Boxes
394
S1
For Section I applications, stress values at temperatures of 450ºC and above are permissible but, except for tubular products 75 mm O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S2
For Section I applications, stress values at temperatures of 475ºC and above are permissible but, except for tubular products 75 mm O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S3
For Section I applications, stress values at temperatures of 550ºC and above are permissible but, except for tubular products 75 mm O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S4
For Section I applications, stress values at temperatures of 625ºC and above are permissible but, except for tubular products 75 mm O.D. or less enclosed within the boiler setting, use of these materials at these temperatures is not current practice.
S5
Material that conforms to Class 10, 11, or 12 is not permitted when the nominal thickness of the material exceeds19 mm.
S6
Material that conforms to Class 10, 11, or 12 is not permitted when the nominal thickness of the material exceeds 32 mm.
S7
The maximum thickness of unheat-treated forgings does exceed 95 mm. The maximum thickness as-heat-treated may be 100 mm.
S8
The maximum section thickness does exceed 75 mm for double-normalized-and-tempered forgings, or 125 mm for quenched-and-tempered forgings.
S9
Both NPS 8 and larger, and schedule 140 and heavier.
S10
The maximum pipe size is NPS 4 (DN 100) and the maximum thickness in any pipe size is Schedule 80.
T1
Allowable stresses for temperatures of 370ºC and above are values obtained from time-dependent properties.
T2
Allowable stresses for temperatures of 400ºC and above are values obtained from time-dependent properties.
T3
Allowable stresses for temperatures of 455ºC and above are values obtained from time-dependent properties.
T4
Allowable stresses for temperatures of 480ºC and above are values obtained from time-dependent properties.
T5
Allowable stresses for temperatures of 510ºC and above are values obtained from time-dependent properties.
T6
Allowable stresses for temperatures of 540ºC and above are values obtained from time-dependent properties.
T7
Allowable stresses for temperatures of 565ºC and above are values obtained from time-dependent properties.
T8
Allowable stresses for temperatures of 595ºC and above are values obtained from time-dependent properties.
T9
Allowable stresses for temperatures of 620ºC and above are values obtained from time-dependent properties.
CodeCalc User's Guide
Material Dialog Boxes T10
Allowable stresses for temperatures of 425ºC and above are values obtained from time-dependent properties.
W1
Not for welded construction.
W2
Not for welded construction in Section III.
W3
Welded.
W4
Nonwelded, or welded if the tensile strength of the Section IX reduced section tension test is not less than 690 MPa.
W5
Welded, with the tensile strength of the Section IX reduced tension test less than 690 MPa but not less than 655 MPa.
W6
This material may be welded by the resistance technique.
W7
In welded construction for temperatures above 450ºC, the weld metal has a carbon content of greater than 0.05%.
W8
Welding and oxygen or other thermal cutting processes are not permitted when carbon content exceeds 0.35% by heat analysis.
W9
For Section I applications, for pressure retaining welds in 2¼Cr–1Mo materials, other than circumferential butt welds less than or equal to 89 mm in outside diameter, when the design metal temperatures exceed 450ºC, the weld metal has a carbon content greater than 0.05%.
W10
For Section III applications, material that conforms to Class 10, 13, 20, 23, 30, 33, 40, 43, 50, or 53 is not permitted for Class 2 and Class 3 construction when a weld efficiency factor of 1.00 is used in accordance with Note W12.
W11
For Section VIII applications, Section IX, QW-250 Variables QW-404.12, QW-406.3, QW-407.2, and QW-409.1 shall also apply to this material. These variables shall be applied in accordance with the rules for welding of Part UF.
W12
These S values do not include a longitudinal weld efficiency factor. For Section III applications, for materials welded without filler metal, ultrasonic examination, radiographic examination, or eddy current examination, in accordance with NC-2550, shall provide a longitudinal weld efficiency factor of 1.0. Other long. weld efficiency factors shall be in accordance with the following:
For single butt weld, with filler metal, 0.80. For single or double butt weld, without filler metal, 0.85. For double butt weld, with filler metal, 0.90. For single or double butt weld, with radiography, 1.00.
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Material Dialog Boxes W13
For Section I applications, electric resistance and autogenous welded tubing may be used with these stresses, provided the following additional restrictions and requirements are met:
The tubing is used for boiler, waterwall, superheater, and economizer tubes that are enclosed within the setting. The maximum outside diameter is 89 mm. The weld seam of each tube is subjected to an angle beam ultrasonic inspection per SA-450. A complete volumetric inspection of the entire length of each tube is performed in accordance with SA-450. Material test reports are supplied.
W14
These S values do not include a weld factor. For Section VIII, Division 1 and Section XII applications using welds made without filler metal, the tabulated tensile strength values should be multiplied by 0.85. For welds made with filler metal, consult UW-12 of Section VIII, Division 1, or TW-130.4 for Section XII, as applicable.
W15
The Nondestructive Electric Test requirements of SA-53 Type E pipe are required for all sizes. The pipe shall be additionally marked "NDE" and so noted on the material certification.
Division 1 Material Notes for Table 1B (Non-Ferrous Materials) - Customary
396
(a)
The following abbreviations are used: ann., annealed; Applic., Applicability; Cond., Condition; cond., condenser; Desig., Designation; exch., exchanger; extr., extruded; fin., finished; fr., from; rel., relieved; rld., rolled; Smls., Seamless; Sol., Solution; treat., treated; and Wld., Welded.
(b)
The stress values in this Table may be interpolated to determine values for intermediate temperatures.
(c)
For Section VIII applications, stress values in restricted shear, such as dowel bolts, rivets, or similar construction in which the shearing is so restricted that the section under consideration would fail without reduction of areas, shall be 0.80 times the values in this table.
(d)
For Section VIII applications, stress values in bearing shall be 1.60 times the values in this Table.
(e)
An alternative typeface is used for stress values obtained from time-dependent properties (see Notes T1-T18).
(f)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SB-407/SB-407M), the values listed in this Table shall be applicable to either the customary U.S. version of the material specification or the SI units version of the material specification.
(g)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
G1
For steam at 250 psi (406F), the values given for 400F may be used.
CodeCalc User's Guide
Material Dialog Boxes G2
At temperatures over 1000F, these stress values apply only when the carbon is 0.04% or higher.
G3
In the absence of evidence that the casting is of high quality throughout, values not in excess of 80% of those given in the Table shall be used. This is not intended to apply to valves and fittings made to recognized standards.
G4
Creep-fatigue, thermal ratcheting, and environmental effects are increasingly significant failure modes at temperatures in excess of 1500F and shall be considered in the design.
G5
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66 2/3 % but do not exceed 90% of the yield strength at temperature. Use of these stresses may results in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors which, when applied to the yield strength values shown in table Y-1, will give allowable stress values that will result in lower values of permanent strain.
G6
Maximum temperature for external pressure not to exceed 350F.
G7
Use 350F curve for all temperature values below 350F.
G8
The stresses for this material are based on 120 ksi minimum tensile strength because of weld metal strength limitations.
G9
Use Fig. NFC-6 up to and including 300F. Use the 600F curve of Fig. NFC-3 above 300F up to and including 400F. Maximum temperature for external pressure not to exceed 400F.
G10
Maximum temperature for external pressure not to exceed 450F.
G11
Referenced external pressure chart is applicable up to 700F.
G12
Referenced external pressure chart is applicable up to 800F.
G13
For Section VIII applications, use of external pressure charts for material in the form of bar stock is permitted for stiffening rings only.
G14
A factor of 0.85 has been applied in arriving at the maximum allowable stress values in tension for this material. Divide tabulated values by 0.85 for maximum allowable longitudinal tensile stress.
G15
To these stress values a quality factor as specified in Section III, ND-3115 or UG-24 of Section VIII, Division 1 shall be applied for castings. This is not intended to apply to valves and fittings made to recognized standards.
G16
Allowable stress values shown are 90% of those for the corresponding core material.
G17
Copper-silicon alloys are not always suitable when exposed to certain media and high temperatures, particularly steam above 212F. The user should ensure that the alloy selected is satisfactory for the service for which it is to be used.
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Material Dialog Boxes
398
G18
Because of the occasionally contingent danger from the failure of pressure vessels by stress corrosion cracking, the following is pertinent. These materials are suitable for engineering use under a wide variety of ordinary corrosive conditions with no particular hazard in respect to stress corrosion.
G19
Few alloys are completely immune to stress corrosion cracking in all combinations of stress and corrosive environments and the supplier of the material should be consulted. Reference may also be made to the following sources: (1) Stress Corrosion Cracking Control Measures B.F. Brown, U.S. National Bureau of Standards (1977), available from NACE, Texas; (2) The Stress Corrosion of Metals, H.L. Logan, John Wiley and Sons, New York, 1966.
G20
For plate only.
G21
The maximum operating temperature is arbitrarily set at 500F because harder temper adversely affects design stress in the creep rupture temperature range.
G22
The minimum tensile strength of reduced tension specimens in accordance with QW-462.1 of Section IX shall not be less than 110,000 psi.
G23
This alloy is subject to severe loss of impact strength at room temperature after exposure in the range of 1000F to 1400F.
G24
For stress relieved tempers (T351, T3510, T3511, T451, T4510, T4511, T651, T6510, T6511), stress values for materials in the basic temper shall be used.
G25
The tension test specimen from plate 0.500 in. and thicker is machined from the core and does not include the cladding alloy; therefore, the allowable stress values for thickness less than 0.500 in. shall be used.
G26
The tension test specimen from plate 0.500 in. and thicker is machined from the core and does not include the cladding alloy; therefore, the allowable stress values shown are 90% of those for the core material of the same thickness.
G27
Alloy N06022 in the solution annealed condition is subject to severe loss of impact strength at room temperatures after exposure in the range of 1000F to 1250F.
G28
For external pressure design, the maximum design temperature is limited to 1000F.
G29 (METRIC Database)
The maximum allowable stress values for greater than 900C are 9.7 MPa (927C), 7.6 MPs (954C), and 5.0 MPa (982C).
G30 (METRIC Database)
The maximum allowable stress values for greater than 900C are 5.0 MPa (925C), 4.0 MPa (950C), 3.2 MPa (975C), and 2.6 MPa (1000C). The maximum use temperature is 982C; the value listed at 1000C is provided for interpolation purposes only.
G31 (METRIC Database)
The maximum allowable stress values for greater than 900C are 7.8 MPa (925C), 5.2 MPa (950C), 3.5 MPa (975C), and 2.4 MPa (1000C). The maximum use temperature is 982C; the value listed at 1000C is provided for interpolation purposes only.
CodeCalc User's Guide
Material Dialog Boxes G32 (METRIC Database)
The maximum allowable stress values for greater than 900C are 6.6 MPa (925C), 4.4 MPa (950C), 2.9 MPa (975C), and 2.0 MPa (1000C). The maximum use temperature is 982C; the value listed at 1000C is provided for interpolation purposes only.
H1
For temperatures above 1000F, these stress values may be used only if the material is annealed at a minimum temperature of 1900F and has a carbon content of 0.04% or higher.
H2
For temperatures above 1000F, these stress values may be used only if the material is heat treated by heating it to a minimum temperature of 1900F and quenching in water or rapidly cooling by other means.
H3
For Section I applications, cold drawn pipe or tube shall be annealed at 1900F minimum.
H4
The material shall be given a 1725F to 1825F stabilizing heat treatment.
T1
Allowable stresses for temperatures of 250F and above are values obtained from time-dependent properties.
T2
Allowable stresses for temperatures of 300F and above are values obtained from time dependent properties.
T3
Allowable stresses for temperatures of 350F and above are values obtained from time dependent properties.
T4
Allowable stresses for temperatures of 400F and above are values obtained from time dependent properties.
T5
Allowable stresses for temperatures of 500F and above are values obtained from time dependent properties.
T6
Allowable stresses for temperatures of 550F and above are values obtained from time dependent properties.
T7
Allowable stresses for temperatures of 600F and above are values obtained from time dependent properties.
T8
Allowable stresses for temperatures of 750F and above are values obtained from time dependent properties.
T9
Allowable stresses for temperatures of 800F and above are values obtained from time dependent properties.
T10
Allowable stresses for temperatures of 850F and above are values obtained from time dependent properties.
T11
Allowable stresses for temperatures of 900F and above are values obtained from time dependent properties.
T12
Allowable stresses for temperatures of 950F and above are values obtained from time dependent properties.
T13
Allowable stresses for temperatures of 1000F and above are values obtained from time dependent properties.
T14
Allowable stresses for temperatures of 1050F and above are values obtained from time dependent properties.
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Material Dialog Boxes
400
T15
Allowable stresses for temperatures of 1100F and above are values obtained from time dependent properties.
T16
Allowable stresses for temperatures of 1150F and above are values obtained from time dependent properties.
T17
Allowable stresses for temperatures of 1200F and above are values obtained from time dependent properties.
T18
Allowable stresses for temperatures of 1250F and above are values obtained from time dependent properties.
T19
Allowable stresses for temperatures of 450F and above are values obtained from time dependent properties.
W1
No welding or brazing permitted.
W2
For Section VIII applications, UNF-56(d) shall apply for welded constructions.
W3
For welded and brazed constructions, stress values for O (annealed) temper material shall be used.
W4
The stress values given for this material are not applicable when either welding or thermal cutting is employed.
W5
These S values do not include a longitudinal weld efficiency factor. For Section III applications, for materials welded without filler metal, ultrasonic examination, radiographic examination, or eddy current examination, in accordance with NC 2550, shall provide a longitudinal weld efficiency factor of 1.0. Other long. weld efficiency factors shall be in accordance with the following: a. for single butt weld, with filler metal, 0.80; b. for single or double butt weld, without filler metal, 0.85; c. for double butt weld, with filler metal, 0.90; d. for single or double butt weld, with radiography, 1.00.
W6
Filler metal shall not be used in the manufacture of welded pipe or tubing.
W7
Strength of reduced-section tensile specimen required to qualify welding procedures. See QW-150, Section IX.
W8
After welding, heat treat at 1150-1200F, hold 1-1/2 hr at temperature for the first inch of cross-section thickness and 1/2 hr for each additional inch, and air cool. For castings used in pumps, valves, and fittings 2 in. nominal pipe size and less, PWHT is not required for socket welds and attachment welds when the castings have been temper annealed at 1150 to 1200F prior to welding.
W9
If welded or brazed, the allowable stress values for the annealed condition shall be used and the minimum tensile strength of the reduced tension specimen in accordance with QW-462.1 of Section IX shall not be less than 30.0 ksi.
W10
When nonferrous materials conforming to specifications in Section II, Part B are used in welded or brazed construction, the maximum allowable working stresses shall not exceed the values given herein for annealed material at the metal temperature shown.
W11
These maximum allowable stress values are to be used in welded or brazed constructions.
CodeCalc User's Guide
Material Dialog Boxes W12
These S values do not include a weld factor. For Section VIII, Division 1 applications using welds made without filler metal, the tabulated tensile stress values shall be multiplied by 0.85. For welds made with filler metal, consult UW-12 of Section VIII, Division 1.
W13
For service at 1200F or higher, the deposited weld metal shall be of the same nominal chemistry as the base metal.
W14
No welding permitted.
W15
For Section VIII applications, no welding is permitted.
W16
Use NFA-12 when welded with 5356 or 5556 filler metal, all thickness, or 4043 or 5554 filler metal, thickness 3/8 in.
Division 1 Material Notes for Table 1B (Non-Ferrous Materials) - Metric (a)
The following abbreviations are used: ann., annealed; cond., condenser; exch., exchanger; extr., extruded; fin., finished; fr., from; rel., relieved; rld., rolled; Smls., Seamless; Sol., Solution; treat., treated; and Wld., Welded.
(b)
The stress values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures are rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated.
(c)
For Section VIII and XII applications, stress values in restricted shear, such as dowel bolts, rivets, or similar construction in which the shearing is so restricted that the section under consideration would fail without reduction of areas, are 0.80 times the values in this Table.
(d)
For Section VIII applications, stress values in bearing are 1.60 times the values in this Table.
(e)
An alternative typeface is used for stress values obtained from time-dependent properties (see Notes T1-T18).
(f)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SB-407/SB-407M), the values listed in this Table are applicable to either the customary U.S. version of the material specification or the SI units version of the material specification. For example, the values listed for SB-407 Grade N08800 are used when SB-407M Grade N08800 is used in construction.
(g)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
G1
For steam at 1700 kPa (208ºC), the values given for 200ºC may be used.
G2
At temperatures over 550ºC, these stress values apply only when the carbon is 0.04% or higher.
G3
In the absence of evidence that the casting is of high quality throughout, values not in excess of 80% of those given in the Table are used. This is not intended to apply to valves and fittings made to recognized standards.
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Material Dialog Boxes
402
G4
Creep-fatigue, thermal ratcheting, and environmental effects are increasingly significant failure modes at temperatures in excess of 825ºC and are considered in the design.
G5
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66 2/3% but do not exceed 90% of the yield strength at temperature. Use of these stresses may results in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors which, when applied to the yield strength values shown in Table Y-1, will give allowable stress values that will result in lower values of permanent strain.
G6
Maximum temperature for external pressure not to exceed 175ºC.
G7
Use 350ºF curve for all temperature values below 175ºC.
G8
The stresses for this material are based on 828 MPa minimum tensile strength because of weld metal strength limitations.
G9
Use Fig. NFC-6 up to and including 150ºC. Use the 325ºC curve of Fig. NFC-3 above 150ºC up to and including 200ºC. Maximum temperature for external pressure not to exceed 200ºC.
G10
Maximum temperature for external pressure does not exceed 225ºC.
G11
Referenced external pressure chart is applicable up to 375ºC.
G12
Referenced external pressure chart is applicable up to 425ºC.
G13
For Section VIII and XII applications, use of external pressure charts for material in the form of bar stock is permitted for stiffening rings only.
G14
For Section VIII applications, a factor of 0.85 has been applied in arriving at the maximum allowable stress values in tension for this material. Divide tabulated values by 0.85 for maximum allowable longitudinal tensile stress.
G15
To these stress values a quality factor as specified in ND-3115 of Section III; UG-24 of Section VIII, Division 1; or TM-190 of Section XII shall be applied for castings. This is not intended to apply to valves and fittings made to recognized standards.
G16
Allowable stress values shown are 90% of those for the corresponding core material.
G17
Copper-silicon alloys are not always suitable when exposed to certain media and high temperatures, particularly steam above 100ºC. The user should ensure that the alloy selected is satisfactory for the service for which it is to be used.
G18
Because of the occasionally contingent danger from the failure of pressure vessels by stress corrosion cracking, the following is pertinent. These materials are suitable for engineering use under a wide variety of ordinary corrosive conditions with no particular hazard in respect to stress corrosion.
CodeCalc User's Guide
Material Dialog Boxes G19
Few alloys are completely immune to stress corrosion cracking in all combinations of stress and corrosive environments and the supplier of the material should be consulted. Reference may also be made to the following sources:
Stress Corrosion Cracking Control Measures B.F. Brown, U.S. National Bureau of Standards (1977), available from NACE, Texas The Stress Corrosion of Metals, H.L. Logan, John Wiley and Sons, New York, 1966.
G20
For plate only.
G21
The maximum operating temperature is arbitrarily set at 250ºC because harder temper adversely affects design stress in the creep rupture temperature range.
G22
The minimum tensile strength of reduced tension specimens in accordance with QW-462.1 of Section IX is not less than 760 MPa.
G23
This alloy is subject to severe loss of impact strength at room temperature after exposure in the range of 550ºC to 750ºC..
G24
For stress relieved tempers (T351, T3510, T3511, T451, T4510, T4511, T651, T6510, T6511), stress values for materials in the basic temper are used.
G25
The tension test specimen from plate 13 mm and thicker is machined from the core and does not include the cladding alloy; therefore, the allowable stress values for thickness less than 13 mm are used.
G26
The tension test specimen from plate 13 mm and thicker is machined from the core and does not include the cladding alloy; therefore, the allowable stress values shown are 90% of those for the core material of the same thickness.
G27
Alloy N06022 in the solution annealed condition is subject to severe loss of impact strength at room temperatures after exposure in the range of 550ºC to 675ºC.
G28
For external pressure design, the maximum design temperature is limited to 550ºC.
G29
The maximum allowable stress values for greater than 900ºC are 9.7 MPa (927ºC), 7.6 MPa (954ºC), and 5.0 MPa (982ºC).
G30
The maximum allowable stress values for greater than 900ºC are 5.0 MPa (925ºC), 4.0 MPa (950ºC), 3.2 MPa (975ºC), and 2.6 MPa (1000ºC). The maximum use temperature is 982ºC; the value listed at 1000ºC is provided for interpolation purposes only.
G31
The maximum allowable stress values for greater than 900°C are 7.8 MPa (925°C), 5.2 MPa (950°C), 3.5 MPa (975°C), and 2.4 MPa (1000°C). The maximum use temperature is 982°C; the value listed at 1000°C is provided for interpolation purposes only.
G32
The maximum allowable stress values for greater than 900°C are 6.6 MPa (925°C), 4.4 MPa (950°C), 2.9 MPa (975°C), and 2.0 MPa (1000°C). The maximum use temperature is 982°C; the value listed at 1000°C is provided for interpolation purposes only.
H1
For temperatures above 550ºC, these stress values may be used only if the material is annealed at a minimum temperature of 1040ºC and has a carbon content of 0.04% or higher.
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Material Dialog Boxes
404
H2
For temperatures above 550ºC, these stress values may be used only if the material is heat treated by heating it to a minimum temperature of 1040ºC and quenching in water or rapidly cooling by other means.
H3
For Section I applications, cold drawn pipe or tube is annealed at 1038ºC minimum.
H4
The material is given a 940ºC to 995ºC stabilizing heat treatment.
T1
Allowable stresses for temperatures of 125ºC and above are values obtained from time-dependent properties.
T2
Allowable stresses for temperatures of 150ºC and above are values obtained from time dependent properties.
T3
Allowable stresses for temperatures of 175ºC and above are values obtained from time dependent properties.
T4
Allowable stresses for temperatures of 205ºC and above are values obtained from time dependent properties.
T5
Allowable stresses for temperatures of 260ºC and above are values obtained from time dependent properties.
T6
Allowable stresses for temperatures of 290ºC and above are values obtained from time dependent properties.
T7
Allowable stresses for temperatures of 315ºC and above are values obtained from time dependent properties.
T8
Allowable stresses for temperatures of 400ºC and above are values obtained from time dependent properties.
T9
Allowable stresses for temperatures of 425ºC and above are values obtained from time dependent properties.
T10
Allowable stresses for temperatures of 455ºC and above are values obtained from time dependent properties.
T11
Allowable stresses for temperatures of 480ºC and above are values obtained from time dependent properties.
T12
Allowable stresses for temperatures of 510ºC and above are values obtained from time dependent properties.
T13
Allowable stresses for temperatures of 540ºC and above are values obtained from time dependent properties.
T14
Allowable stresses for temperatures of 565ºC and above are values obtained from time dependent properties.
T15
Allowable stresses for temperatures of 595ºC and above are values obtained from time dependent properties.
T16
Allowable stresses for temperatures of 620ºC and above are values obtained from time dependent properties.
T17
Allowable stresses for temperatures of 650ºC and above are values obtained from time dependent properties.
T18
Allowable stresses for temperatures of 675ºC and above are values obtained from time dependent properties.
CodeCalc User's Guide
Material Dialog Boxes W1
No welding or brazing permitted.
W2
For Section VIII applications, UNF-56(d) applies for welded constructions.
W3
For welded and brazed constructions, stress values for O (annealed) temper material are used.
W4
The stress values given for this material are not applicable when either welding or thermal cutting is employed.
W5
These S values do not include a longitudinal weld efficiency factor. For Section III applications, for materials welded without filler metal, ultrasonic examination, radiographic examination, or eddy current examination, in accordance with NC 2550, shall provide a longitudinal weld efficiency factor of 1.0. Other long. weld efficiency factors are in accordance with the following:
For single butt weld, with filler metal, 0.80. For single or double butt weld, without filler metal, 0.85. For double butt weld, with filler metal, 0.90. For single or double butt weld, with radiography, 1.00.
W6
Filler metal is not used in the manufacture of welded pipe or tubing.
W7
Strength of reduced-section tensile specimen required to qualify welding procedures. See QW-150, Section IX.
W8
After welding, heat treat at 625ºC - 650ºC, hold 1½ hr at temperature for the first 25 mm of cross-section thickness and ½ hr for each additional 25 mm, and air cool. For castings used in pumps, valves, and fittings DN 50 and less, PWHT is not required for socket welds and attachment welds when the castings have been temper annealed at 625ºC - 650ºC prior to welding.
W9
If welded or brazed, the allowable stress values for the annealed condition are used and the minimum tensile strength of the reduced tension specimen in accordance with QW-462.1 of Section IX is not less than 205 MPa.
W10
When nonferrous materials conforming to specifications in Section II, Part B are used in welded or brazed construction, the maximum allowable working stresses do not exceed the values given herein for annealed material at the metal temperature shown.
W11
These maximum allowable stress values are to be used in welded or brazed constructions.
W12
These S values do not include a weld factor. For Section VIII, Division 1 applications using welds made without filler metal, the tabulated tensile stress values are multiplied by 0.85. For welds made with filler metal, consult UW-12 of Section VIII, Division 1.
W13
For service at 650ºC or higher, the deposited weld metal is of the same nominal chemistry as the base metal.
W14
No welding permitted.
W15
For Section VIII applications, no welding is permitted.
W16
Use NFA-12 when welded with 5356 or 5556 filler metal, all thicknesses, or 4043 or 5554 filler material, thickness 10 mm.
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Material Dialog Boxes
Division 1 Superseded Material Notes
Notes for the year 1943 (a)
Allowable working stresses in single shear = 0.8 times the given values.
(b)
Allowable working stresses in double shear = 1.6 times the given values.
(c)
Allowable working stresses in bearing = 1.8 times the given values.
(d)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures shall be rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated. The rounding rule is: when the next digit beyond the last place to be retained is less than 5, retain unchanged the digit in the last place retained; when the digit next beyond the last place to be retained is 5 or greater, increase by 1 the digit in the last place retained.
(e)
Values of stresses above 700 F are based upon steel in annealed condition.
1
Limited to plates not over 3/4 in. in thickness and to temperatures not above 750 F.
2
Maximum value for tensile strength permitted in design, 55,000 psi.
3
For present, limited to temperatures not above 750 F.
4
Only seamless steel pipe or tubing, or electric-fusion-welded pipe may be used for temperatures above 750 F.
5
Limited to temperatures not above 450 F.
6
Limited to temperatures not above 750 F.
7
Limited to temperatures not above 850 F.
Notes for the year 1952
406
(a)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures shall be rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated. The rounding rule is: when the next digit beyond the last place to be retained is less than 5, retain unchanged the digit in the last place retained; when the digit next beyond the last place to be retained is 5 or greater, increase by 1 the digit in the last place retained.
1
See Par. UG-6
2
Flange quality in this specification not permitted over 850 F.
3
These stress values are one-fourth the specified minimum tensile strength multiplied by a quality factor of 0.92, except for SA-283, Grade D. and SA-7.
4
For service temperatures above 850 F it is recommended that killed steels containing not less than 0.19% residual silicon be used. Killed steels which have been deoxidized with large amounts of aluminum and rimmed steels may have creep and stress-rupture properties in the temperature range above 850 F, which are somewhat less than those on which the values in the above table are based.
CodeCalc User's Guide
Material Dialog Boxes 5
Between temperatures of 650 F and 1000 F, inclusive, the stress values for Specification SA-201, Grade B, may be used until high temperature test data become available.
6
Only (silicon) killed steel shall be used above 900 F.
7
To these stress values a quality factor as specified in Par. UG-24 shall be applied.
8
These stress values apply to normalized and drawn material only.
9
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints, where freedom from leakage over a long period of time without retightening is required, lower stress values may be necessary as determined from the relative flexibility of the flange and bolts, and corresponding relaxation properties.
10
Between temperatures of —20 to 400 F, stress values equal to the lower of the following will be permitted: 20% of the specified tensile strength, or 25% of the specified yield strength.
11
Not permitted above 450 F; allowable stress value 7000 psi.
12
Between temperatures 0( 750 F to 1000 F, inclusive, the stress values for Specification SA-212, Grade B, may be used until high temperature test data become available.
13
The stress values to be used for temperatures below —20 F when steels are made to conform with Specification SA-300 shall be those that are given in the column for —20 to 650 F.
Notes for the year 1965: (TABLE UCS-23) (a)
Stress values in restricted shear such as dowel bolts, rivets, or similar construction in which the shearing member is so restricted that the section under consideration would fail without reduction of area shall be 0.80 times the given values.
(b)
Stress values in bearing shall be 1.60 times the given values.
(c)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures shall be rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated. The rounding rule is: when the next digit beyond the last place to be retained is less than 5, retain unchanged the digit in the last place retained; when the digit next beyond the last place to be retained is 5 or greater, increase by 1 the digit in the last place retained.
1
See Par. UCS-6(b).
2
Flange quality in this specification not permitted over 850 F.
3
These stress values are one-fourth the specified minimum tensile strength multiplied by a quality factor of 0.92, except for SA-283, Grade D. SA-7 and SA-36.
4
For service temperatures above 850 F it is recommended that killed steels containing not less than 0.10% residual silicon be used. Killed steels which have been deoxidized with large amounts of aluminum and rimmed steels may have creep and stress-rupture properties in the temperature range above 850 F:, which are somewhat less than those on which the values in the above table are based.
5
Between temperatures of 650 F and 1000 F, inclusive, the stress values for Specification SA-201, Grade B, may be used until high temperature test data become available.
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Material Dialog Boxes
408
6
Only (silicon) killed steel shall be used above 900 F.
7
To these stress values a quality factor as specified in Par. UG-24 shall be applied.
8
These stress values apply to normalized and drawn material only.
9
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints, where freedom from leakage over a long period of time without retightening is required, lower stress values may be necessary JS determined from the relative flexibility of the flange and bolts, and corresponding relaxation properties.
10
Between temperatures of —20 to 400 F, Stress values equal to the lower of the following will be permitted: 20% of the specified tensile strength, or 25% of the specified yield strength.
11
Not permitted above 450 F; allowable stress value 7000 psi.
12
Between temperatures of 750 F to 1000 F. inclusive, the stress values for Specification SA-212, Grade B, may be used until high temperature test data become available.
13
The stress values to be used for temperatures below —20 F when steels are made to conform with Specification SA-300 shall be those that are given in the column for —20 to 650 F.
15
For temperatures below 400 F, stress values equal to 20 per cent of the specified minimum tensile strength will be permitted.
19
These allowable stress values apply also to structural shapes and bars.
20
Stress values apply to normalized, or normalized and tempered or oil quenched and tempered material only, as per applicable specification.
21
Stress values apply to quenched and tempered material only, as per applicable specification.
22
Welding not permitted when carbon content exceeds 0.35 per cent by ladle analysis except for repairs or non-pressure attachments as outlined in Part UF.
23
Welding or brazing not permitted on liquid quenched and tempered material.
24
Maximum allowable stress values shall be as follows: Grade
Liquid Quenched and Tempered (-20 to 200F)
Other Than Liquid Quenched and Tempered (-20 to 200F)
I
15,000
15,000
II
18,750
18,750
III
22,500
22,500
IV
26,250
26,250
V(A,B&E)
30,000
V(C&D)
30,000
25
See Par. UCS-6 (c).
26
This material shall not be used in thicknesses above 0.58 in.
CodeCalc User's Guide
Material Dialog Boxes Notes for the year 1965:(TABLE UHA-23) 1
Due to the relatively low yield strength of this material, the higher stress values at temperatures from 200 through 1050F" were established to permit the use of this material where slip-hay greater deformation is acceptable. The stress values within the above range exceed 621/2 per cent, but do not exceed 90 percent of the yield strength at temperature. These stress values are not recommended for the design of flanges or piping.
2
These stress values at temperatures of 1050F and above should be used only when assurance is provided that the steel has a predominant grain size not finer than ASTM No. 6.
3
These stress values shall be considered basic values to be used when no effort is made to control or check the grain size of the steel.
4
These stress values are the basic values multiplied by a joint efficiency factor of 0.85.
5
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints where freedom from leakage over a long period of time without retightening is required, lower values may be necessary as determined from the flexibility of the flange and bolts and corresponding relaxation.
6
These stress values a quality factor as specified in Par. UG-24 shall be applied.
7
These stress values permitted for material that has been carbide-solution treated.
8
For temperatures below 100F, stress values equal to 20 percent of the specified minimum tensile strength will be permitted.
9
This steel may be expected to develop embrittlement at room temperature after service at temperatures above 800F: consequently, its use at higher temperatures is not recommended unless due caution is observed.
10
At temperatures over 1000F, these stress values apply only when the carbon is 0.04 percent or higher.
11
For temperatures above 800F, the stress values apply only when the carbon content is 0.04 percent and above.
12
These stress values shall be applicable to forgings over 5 inches in thickness.
Notes for the year 1974 (a)
Stress values in restricted shear such as dowel bolts, rivets, or similar construction in which the shearing member is so restricted that the section under consideration would fail without reduction of area shall be 0.80 times the given values.
(b)
Stress values in bearing shall be 1.60 times the given values.
(c)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures shall be rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated. The rounding rule is: when the next digit beyond the last place to be retained is less than 5, retain unchanged the digit in the last place retained; when the digit next beyond the last place to be retained is 5 or greater, increase by 1 the digit in the last place retained.
1
See UCS-6(b).
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Material Dialog Boxes
410
3
These stress values are one fourth the specified minimum tensile strength multiplied by a qualify factor of 0.92, except for SA-283, Grade D, and SA-36.
4
For service temperatures above 850 F it is recommended that killed steels containing not less than 0.10 percent residual silicon be used. Killed steels which have been deoxidized with large amounts of aluminum and rimmed steels may have creep and stress rupture properties in the temperature range above 850 F. which are somewhat less than those on which the values in the above Table are based.
5
Between temperatures of 650 and 1000 F, inclusive, the stress values for Specification SA-201. Grade B. may be used until high temperature test data become available.
6
Only killed steel shall be used above 850 F.
7
To these stress values a quality factor as specified in UG-24 shall be applied for castings.
8
These stress values apply to normalized and drawn material only.
9
These stress values are established from a consideration of strength only and will be satisfactory for average service. For bolted joints, where freedom from leakage over a long period of time without retightening is required, lower stress values may be necessary as determined from the relative flexibility of the flange and bolts, and corresponding relaxation properties.
11
Not permitted above 450F; allowable stress value 7000 psi.
12
Between temperatures of 750 and 1000 F, inclusive, the stress values for Specification SA-515, Grade 70. May be used until high temperature test data become available.
13
The stress values to be used for temperatures below —20F when steels are made to conform with supplement (5)SA-20 shall be those that are given in the column for —20 to 650 F.
15
For temperatures below 400 F, stress values equal to 20 percent of the specified minimum tensile strength will be permitted.
19
These allowable stress values apply also to structural shapes and bars.
20
Stress values apply to normalized, or normalized and tempered or oil quenched and tempered material only, as per applicable specification.
21
Stress values apply to quenched and tempered material only, as per applicable specification.
22
Welding or brazing is not permitted when carbon content exceeds 0.35 percent by ladle analysis except for limited types of welding as allowed in Part UF.
23
Welding or brazing not permitted on liquid quenched and tempered material.
CodeCalc User's Guide
Material Dialog Boxes 24
Maximum allowable stress values shall be as follows: Grade
Normalized or Normalized and Liquid Quenched and Tempered Tempered -20 to 650 -20 to 100 200
300
400
500
600
I
15,000
15,000
15,000
II
18,750
18,750
18,750
III
22,500
22,500
22,500
IV
26,250
26,250
25,050
24,600
24,600
24,600 24,600
VA
30,000
28,850
28,850
28,850
28,850
28,850 28,850
VB
30,000
29,050
28,500
28,500
28,200
27,800 26,750
VE
30,000
29,800
28,700
28,700
28,700
28,700 27,500
VC&D
30,000
30,000
VIII
33,700
32,300
32,100
31,900
31,600 31,400
650
24,600
30,000
26
This material shall not be used in thicknesses above 0.58 in.
27
Upon prolonged exposure to temperatures above 800 F. the carbide phase of carbon steel may be converted to graphite.
28
Upon prolonged exposure to temperatures above 875 F, the carbine phase of carbon-molybdenum steel may be converted to graphite.
29
The material shall not be used in thickness above 0.375 in.
30
For temperatures above which stresses are given, the allowable stresses for the annealed plate shall be used.
31
Where the fabricator performs the heat treatment the requirements of UHT-81 shall be met.
32
Section IX, QW-250 Variables QW404.12, QW406.3, QW407.2, and QW-409.1 of QW-422 shall also apply to this material. These variables shall be applied in accordance with the rules for welding of Part UF of Division I.
Division 2 Material Notes for Table 2A (Ferrous Materials) - Customary (a)
The following abbreviations are used: Smls., Seamless; Temp., Temperature; and Wld., Welded.
(b)
An alternative typeface is used for stress values based on successful experience in service (see Notes E1 and E2 ).
(c)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SA-516/SA-516M), the values listed in this Table are applicable to either the customary U.S. version of the material specification or the SI units version of the material specification. For example, the values listed for SA-516 Grade 70 are used when SA-516M Grade 485 is used in construction.
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Material Dialog Boxes
412
(d)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures are rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated.
(e)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
E1
For values at 650ºF and above, the design stress intensity values are based on successful experience in service.
E2
For values at 700ºF and above, the design stress intensity values are based on successful experience in service.
G1
Material that conforms to Class 10, 13, 20, 23, 30, 33, 40, 43, 50, or 53 is not permitted.
G2
Material that conforms to Class 11 or 12 is not permitted.
G3
Material that conforms to Class 11 or 12 is not permitted when the nominal thickness of the material exceeds ¾ in.
G4
Material that conforms to Class 11 or 12 is not permitted when the nominal thickness of the material exceeds 1¼ in.
G5
A product analysis is required on this material.
G6
SA-723 is not used for minimum permissible temperature below 40°F.
G7
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66 2/3 % but do not exceed 90% of the yield strength at temperature. Use of these stresses may results in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors that, when applied to the yield strength values shown in Table Y-1, give allowable stress values that will result in lower values of permanent strain.
G8
This material has reduced toughness at room temperature after exposure at high temperature. The degree of embrittlement depends on composition, heat treatment, time and temperature. The lowest temperature of concern is about 500ºF. See Appendix A, A-360.
G9
At temperatures over 1000ºF, these stress intensity values apply only when the carbon is 0.04% or higher. This note is applicable only when stresses above 1000ºF are published.
G10
For temperatures above 1000°F, these stress intensity values may be used only if the material has been heat treated by heating to a minimum temperature of 1900°F and quenching in water or rapidly cooling by other means. This note is applicable only when stresses above 1000ºF are published.
CodeCalc User's Guide
Material Dialog Boxes G11
These stress intensity values at temperatures of 1050°F and above should be used only when assurance is provided that the steel has a predominant grain size not finer than ASTM No. 6. This note is applicable only when stresses above 1000°F are published.
G12
These stress intensity values are considered basic values to be used when no effort is made to control or check the grain size of the steel.
G13
This steel may be expected to develop embrittlement after service at moderately elevated temperature. See Appendix A, A-340 and A-360.
G14
All forgings have a maximum tensile strength not in excess of 35 ksi above the specified minimum.
G15
Fabricated from SA-387 Grade 12 Class 1 plate.
G16
Fabricated from SA-387 Grade 12 Class 2 plate.
H1
Annealed.
H2
Normalized and tempered.
H3
Pieces that are formed (after quenching and tempering) at a temperature lower than 25ºF below the final tempering temperature are heat-treated after forming when the extreme fiber strain from forming exceeds 3%. Heat treatment shall be 1075ºF minimum, but not higher than 25ºF below the final tempering temperature for a minimum time of one hour per inch of thickness. Pieces formed at temperatures within 25ºF higher than the original tempering temperature are requenched and tempered, either before or after welding into the vessel.
S1
The maximum thickness of forgings does not exceed 3¾ in. (4 in. as heat treated).
S2
Both NPS 8 and larger, and schedule 140 and heavier.
S3
The minimum thickness of pressure-retaining parts is ¼ in..
S4
The minimum thickness of shells, heads, and other pressure-retaining parts is ¼ in.. The maximum thickness is limited only by the ability to develop the specified mechanical properties.
W1
Not for welded construction.
W2
In welded construction, for temperatures above 850°F, the weld metal has a carbon content of greater than 0.05%.
W3
The following, in addition to the variables in Section IX, QW-250, are considered as essential variables requiring requalification of the welding procedure.
An increase in the maximum or a decrease in the minimum specified preheat or interpass temperatures. The specified range of preheat temperatures does not exceed 150ºF. A change in the thickness T of the welding procedure qualification test plate as follows: a. For welded joints that are quenched and tempered after welding, any increase in thickness (the minimum thickness qualified in all cases is ¼ in.). b. For welded joints that are not quenced and tempered after welding, any changes as follows: (a) For T less than 5/8 in., any decrease in thickness (the maximum thickness qualified is 2T); (b) for T equal to 5/8 in. and over, any departure from the range of 5/8 in. to 2T.
CodeCalc User's Guide
413
Material Dialog Boxes Division 2 Material Notes for Table 2A (Ferrous Materials) - Metric
414
(a)
The following abbreviations are used: Smls., Seamless; Temp., Temperature; and Wld., Welded.
(b)
An alternative typeface is used for stress values based on successful experience in service (see Notes E1 and E2).
(c)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SA-516/SA-516M), the values listed in this Table are applicable to either the customary U.S. version of the material specification or the SI units version of the material specification. For example, the values listed for SA-516 Grade 70 shall be used when SA-516M Grade 485 is used in construction.
(d)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures are rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated.
(e)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
E1
For values at 350°C and above, the design stress intensity values are based on successful experience in service.
E2
For values at 375°C and above, the design stress intensity values are based on successful experience in service.
G1
Material that conforms to Class 10, 13, 20, 23, 30, 33, 40, 43, 50, or 53 is not permitted.
G2
Material that conforms to Class 11 or 12 is not permitted.
G3
Material that conforms to Class 11 or 12 is not permitted when the nominal thickness of the material exceeds 19 mm.
G4
Material that conforms to Class 11 or 12 is not permitted when the nominal thickness of the material exceeds 32 mm.
G5
A product analysis is required on this material.
G6
SA-723 is not used for minimum permissible temperature below +5°C.
G7
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short-time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66-2/3% but do not exceed 90% of the yield strength at temperature. Use of these stresses may result in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors that, when applied to the yield strength values shown in Table Y-1, will give allowable stress values that will result in lower levels of permanent strain.
G8
This material has reduced toughness at room temperature after exposure at high temperature. The degree of embrittlement depends on composition, heat treatment, time, and temperature. The lowest temperature of concern is about 250°C. See
CodeCalc User's Guide
Material Dialog Boxes Appendix A, A-360. G9
At temperatures over 550°C, these stress intensity values apply only when the carbon is 0.04% or higher. This note is applicable only when stresses above 550°C are published.
G10
For temperatures above 550°C, these stress intensity values may be used only if the material has been heat treated by heating to a minimum temperature of 1040°C and quenching in water or rapidly cooling by other means. This note is applicable only when stresses above 550°C are published.
G11
These stress intensity values at temperatures of 575°C and above should be used only when assurance is provided that the steel has a predominant grain size not finer than ASTM No. 6. This note is applicable only when stresses above 550°C are published.
G12
These stress intensity values are considered basic values to be used when no effort is made to control or check the grain size of the steel.
G13
This steel may be expected to develop embrittlement after service at moderately elevated temperature; see Appendix A, A-340 and A-360.
G14
All forgings have a maximum tensile strength not in excess of 175 MPa above the specified minimum.
G15
Fabricated from SA-387 Grade 12 Class 1 plate.
G16
Fabricated from SA-387 Grade 12 Class 2 plate.
H1
Annealed.
H2
Normalized and tempered.
H3
Pieces that are formed (after quenching and tempering) at a temperature lower than 15°C below the final tempering temperature are heat treated after forming when the extreme fiber strain from forming exceeds 3%. Heat treatment shall be 580°C minimum, but not higher than 15°C below the final tempering temperature for a minimum time of 1 h per 25 mm of thickness. Pieces formed at temperatures within 15°C higher than the original tempering temperature are requenched and tempered, either before or after welding into the vessel.
S1
The maximum thickness of forgings does not exceed 95 mm (100 mm as heat treated).
S2
Both DN 200 and larger, and schedule 140 and heavier.
S3
The minimum thickness of pressure-retaining parts is 6 mm.
S4
The minimum thickness of shells, heads, and other pressure-retaining parts is 6 mm. The maximum thickness is limited only by the ability to develop the specified mechanical properties.
W1
Not for welded construction.
W2
In welded construction, for temperatures above 450°C, the weld metal has a carbon content of greater than 0.05%.
W3
The following, in addition to the variables in Section IX, QW-250, is considered as essential variables requiring requalification of the welding procedure:
An increase in the maximum or a decrease in the minimum specified preheat or interpass temperatures. The specified range of preheat temperatures shall not exceed 85°C.
CodeCalc User's Guide
415
Material Dialog Boxes
A change in the thickness T of the welding procedure qualification test plate as follows: a. For welded joints that are quenched and tempered after welding, any increase in thickness (the minimum thickness qualified in all cases is 6 mm). b. For welded joints that are not quenched and tempered after welding, any change as follows: (a) for T less than 16 mm, any decrease in thickness (the maximum thickness qualified is 2T) (b) for T equal to 16 mm and over, any departure from the range of 16 mm to 2T.
Division 2 Material Notes for Table 2B (Non-Ferrous Materials)
416
(a)
The following abbreviations are used: ann., annealed; fin., finished; rel., relieved; Smls., Seamless; and Wld., Welded.
(b)
An alternative typeface is used for stress values based on successful experience in service (see Notes E1 and E2).
(c)
Where specifications, grades, classes, and types are listed in this Table, and where the material specification in Section II, Part A or Part B is a dual-unit specification (e.g., SB-407/SB-407M), the values listed in this Table are applicable to either the customary U.S. version of the material specification or the SI units version of the material specification. For example, the values listed for SB-407 Grade N08800 are used when SB-407M Grade N08800 is used in construction.
(d)
The values in this Table may be interpolated to determine values for intermediate temperatures. The values at intermediate temperatures are rounded to the same number of decimal places as the value at the higher temperature between which values are being interpolated.
(e)
The properties of steels are influenced by the processing history, heat treatment, melting practice, and level of residual elements. See Nonmandatory Appendix A for more information.
E2
For values at 800ºF, the design stress intensity values are based on successful experience in service.
G1
Due to the relatively low yield strength of these materials, these higher stress values were established at temperatures where the short-time tensile properties govern to permit the use of these alloys where slightly greater deformation is acceptable. The stress values in this range exceed 66-2/3% but do not exceed 90% of the yield strength at temperature. Use of these stresses may result in dimensional changes due to permanent strain. These stress values are not recommended for the flanges of gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. Table Y-2 lists multiplying factors that, when applied to the yield strength values shown in Table Y-1, will give allowable stress values that will result in lower levels of permanent strain.
G2
Use of external pressure charts for material in the form of barstock is permitted for stiffening rings only.
G3
SB-163 Supplementary Requirement S2 is met.
G4
Design stress intensity values for 100°F may be used at temperatures down to –325°F without additional specification requirements.
CodeCalc User's Guide
Material Dialog Boxes G5
A joint efficiency factor of 0.85 has been applied in arriving at the maximum allowable design stress intensity values for this material.
S1
Thickness Configuration. Modified the input echo and output results from the Flange and Floating Head modules to be consistent with the ASME code nomenclature. Added the recommendation for the minimum gasket width in Floating Head calculations.
CodeCalc User's Guide
479
Appendices
480
CodeCalc User's Guide
Index A Actual Nozzle Diameter Thickness • 105 Additional Input U-tube Tubesheets Dialog Box • 209 AISC Database Dialog Box • 285 Allowable Calculations • 263 API 579 (FFS) Tab • 78 API 579 Introduction • 52 Appendices • 433 Appendix Y Flanges • 375 ASME Section VIII Division 2 - Elastic Analysis of Nozzle • 318 ASME Tubesheets • 183
B Bar Options • 62 Base Ring (1) Tab (Base Rings) • 333 Base Ring (2) Tab (Base Rings) • 334 Base Rings • 327 Baseplate • 269 Baseplate Results • 289 Bellows Tab (Thin Joints) • 346 Bibliography of Pressure Vessel Texts and Standards • 469
C Channel Tab • 186 Channel Tab (TEMA Tubesheets) • 156 CodeCalc Overview • 11 CodeCalc Version 2004 Features (1/2004) • 478 CodeCalc Version 2005 Features (1/2005) • 478 CodeCalc Version 2006 Features (1/2006) • 479 CodeCalc Version 4.5 Features (7/90) • 471 CodeCalc Version 5.0 Features (6/91) • 471 CodeCalc Version 5.1 Features (7/92) • 472 CodeCalc Version 5.2 Features (7/93) • 472 CodeCalc Version 5.3 Features (7/94) • 473 CodeCalc Version 5.4 Features (6/95) • 472 CodeCalc Version 5.5 Features (6/96) • 474 CodeCalc Version 5.6 Features (6/97) • 475 CodeCalc Version 6.0 Features (6/98) • 475 CodeCalc Version 6.1 Features (1/99) • 476
CodeCalc User's Guide
CodeCalc Version 6.2 Features (1/2000) • 476 CodeCalc Version 6.3 Features (1/2001) • 476 CodeCalc Version 6.4 Features (1/2002) • 477 CodeCalc Version 6.5 Features (1/2003) • 477 CodeCalc Workflows • 17 Complete Vessel Examples • 433 Computation Control Tab (Configuration Dialog Box) • 29 Compute Remaining Life • 68 Cone Design Tab (Conical Sections) • 110 Cone Geometry Tab • 112 Configuration Dialog Box • 29 Conical Sections • 109 Create a custom material based on an existing material • 35 Create a new custom material • 34 Create a new units file • 32 Create/Edit Units File • 32
D Data Measurement Tab • 81 Design Tab • 302 Diagnostics Tab • 47 Discussion of Results • 360 Discussion of Results (Shells) • 55
E Edit an existing units file • 32 Effective Material Diameter and Thickness Limits • 106 Enter CTPs Dialog Box • 83 Enter Pitting Information Dialog Box • 84 ESL Tab • 47 Example Problems • 433 Examples • 324 Expansion Joint Tab • 205 Expansion Joint Tab (TEMA Tubesheets) • 166 Expansion Joint Tab (Thick Joints) • 351 Expansion Joint Tab (Thin Joints) • 341 External Pressure Calculations • 264 External Pressure Results • 115 External Pressure Results for Heads: • 133
481
Index
F
K
Failure Path Calculations • 107 FEA Options • 317 Figure A1 Dialog Box • 247 Figure A2 Dialog Box • 247 Figure B3-B Dialog Box • 254 File Tab • 25 Finite Element Analysis (FEA) • 323 Fixed Tubesheet Exchanger Dialog Box • 176 Flange Data Tab • 138 Flange Tab • 376 Flange/Bolts Tab • 120 Flanges • 135 Floating Heads • 117
Kettle Tubesheet Dialog Box • 177
G Gasket Data Tab • 144 Gasket Tab • 122, 380 Geometry Tab • 91 Geometry Tab (Shell/Head) • 58 Global Load and Direction Conventions • 315 Groove Options • 83
H Half Pipes • 357 Head Tab • 118 Highest Percentage of Allowable Calculations • 263 Home Tab • 26 Horizontal Vessels • 213 Hub/Bolts Tab • 142 Hubs/Bolts Tab • 378
I Installation • 16 Intermediate Calculations for Flanged Portion of Head • 133 Internal Pressure Results • 115 Internal Pressure Results for the Head: • 133 Iterative Results Per Pressure, Area, And UG-45 • 107
J Jacket Tab • 69 Jacket Tab (Half Pipes) • 359
482
L Large Diameter Nozzle Calculations • 106 Large Openings • 363 Leg Results • 289 Legs and Lugs • 265 Legs and Lugs Tab • 267 Length of Shell Thickness Adjacent to Tubesheet, front end L1 • 173 Length of Shell Thickness Adjacent to Tubesheet, rear L1 • 173 Lifting Lug Dialog Box • 278 Ligament Efficiency Calculations • 261 Loads Tab • 272, 306, 372 Long Side Tab • 258 Longitudinal Loads Tab (Horizontal Vessels) • 222
M Material Database Dialog Box • 385 Material Database Editor • 34 Material Dialog Boxes • 385 Material Properties • 35 Material Properties Dialog Box • 422 MAWP Calculations • 263 Minimum Design Metal Temperature • 107 Miscellaneous Tab • 95, 128 Miscellaneous Tab (Base Rings) • 336 Miscellaneous Tab (Configuration Dialog Box) • 30 Miscellaneous Tab (Thick Joints) • 353 Multiple Load Cases Dialog Box • 198 Multiple Load Cases Dialog Box (TEMA Tubesheets) • 173
N Nozzle / Attachment Tab • 370 Nozzle Tab • 88 Nozzles • 87
O Opening Tab (Large Openings) • 365 Optional Data Tab • 66 Outer Cylinder Dialog Box • 171 Outer Cylinder on the Thick Expansion Joint • 171 Outer Cylindrical Element Corrosion Allowance • 171
CodeCalc User's Guide
Index Outer Cylindrical Element Length (Lo) • 171 Output • 288, 300
P Performing an Analysis • 17 Pipes and Pads • 291 Pipes and Pads Tab (Pipes and Pads) • 291 Point Measurement Data Dialog Box • 83 Printing or Saving Reports to a File • 23 Purpose, Scope and Technical Basis (Shells) • 49 Purpose, Scope, and Technical Basis • 52, 183 Purpose, Scope, and Technical Basis (Flanges) • 135 Purpose, Scope, and Technical Basis (Nozzles) • 87 Purpose, Scope, and Technical Basis (TubeSheets) • 151
R Rectangular Vessels (App. 13) • 229 Reinforcement Calculations • 262 Reinforcement Calculations Under External Pressure • 116 Reinforcement Calculations Under Internal Pressure • 116 Reinforcing Bar Options • 260 Reinforcing Section Options • 261 Required and Available Areas • 106 Required Thickness Calculations • 133 Required Thickness of Shell and Nozzle • 105 Results • 85, 105, 115, 132, 226, 261 Results (ASME Tubesheets) • 211 Results (Base Rings) • 339 Results (Flanges) • 148 Results (Thick Joints) • 356 Results (Tubesheets) • 177 Results (WRC 107/537/FEA) • 318 Reviewing the Results - The Output Option • 22
S Saddle Wear Plate Design • 213 Saddle Webs and Base Plate Dialog Box • 220 Saddle/Wear Tab • 220 Section Options • 64 Seismic Loads • 276
CodeCalc User's Guide
Seismic Loads Tab (Horizontal Vessels) • 223 Selection of Reinforcing Pad • 106 Shell Band Corrosion Allowance • 173 Shell Band Properties Dialog Box • 172 Shell Tab • 185 Shell Tab (Half Pipes) • 358 Shell Tab (TEMA Tubesheets) • 155 Shell Tab (Thick Joints) • 352 Shell Thickness Adjacent to Tubesheet • 173 Shell/Head Tab • 101, 218 Shell/Nozzle Tab (Large Openings) • 366 Shells and Heads • 49 Shells/Heads Tab • 55 Short Side Tab • 256 Small Cylinder and Larger Cylinder Tabs • 113 Soehren's Calculations: • 134 Starting CodeCalc • 17 Stiffening Ring Tab (Horizontal Vessels) • 221 Stress Calculations • 262 Supplemental Loads • 67 Support Lug Dialog Box • 281
T Tabs • 25 Technical Support • 16 TEMA Tubesheets • 151 Thick Joints • 349 Thin Joints • 341 Tools Tab • 28 Trunnion Results • 289 Trunnion Tab • 286 Tube to Tubesheet Joint Input Dialog Box • 190 Tubes Tab • 187 Tubes Tab (TEMA Tubesheets) • 157 Tubesheet Exchanger Dialog Box • 197 Tubesheet Extended as Flange Dialog (TEMA Tubesheets) • 169 Tubesheet Extended As Flange Dialog Box • 209 Tubesheet Gasket Dialog Box • 173 Tubesheet Gasket/Bolting Input Dialog Box • 199 Tubesheet Tab • 192 Tubesheet Tab (TEMA Tubesheets) • 161
483
Index
U UG-45 Minimum Nozzle Neck Thickness • 106 Units File Dialog Box • 33
V Vessel Leg Tab • 284 Vessel Tab • 216, 239, 304, 369
W Weld Size Calculations • 107 Weld Strength Calculations • 107 What Analysis Types are Available? • 12 What Distinguishes CodeCalc From our Competitors? • 12 What's New in PV Elite and CodeCalc • 9 Wind Loads • 273 Wind Loads Tab (Horizontal Vessels) • 224 WRC 107 Options • 315 WRC 107 Stress Calculations • 321 WRC 107 Stress Summations • 318 WRC 107/537 FEA • 301 WRC 107/537 Load Conventions • 314 WRC 297 Tab • 367 WRC 297/Annex G • 367
484
CodeCalc User's Guide
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