PV Elite and CodeCalc

PV Elite and CodeCalc Verification and Quality Assurance Manual

Version 2014 (16.0)

November 2013 DICAS-PE-200110E

Copyright Copyright © 1993-2013 Intergraph CAS, Inc. All Rights Reserved. Intergraph is part of Hexagon. Including software, file formats, and audiovisual displays; may be used pursuant to applicable software license agreement; contains confidential and proprietary information of Intergraph and/or third parties which is protected by copyright law, trade secret law, and international treaty, and may not be provided or otherwise made available without proper authorization from Intergraph Corporation. Contains RealDWG™ by Autodesk, Inc. Copyright © 1998-2013 Autodesk, Inc. All rights reserved.

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Terms of Use a.

Use of a software product and Documentation is subject to the End User License Agreement ("EULA") delivered with the software product unless the Licensee has a valid signed license for this software product with Intergraph Corporation. If the Licensee has a valid signed license for this software product with Intergraph Corporation, the valid signed license shall take precedence and govern the use of this software product and Documentation. Subject to the terms contained within the applicable license agreement, Intergraph Corporation gives Licensee permission to print a reasonable number of copies of the Documentation as defined in the applicable license agreement and delivered with the software product for Licensee's internal, non-commercial use. The Documentation may not be printed for resale or redistribution.

b.

For use of Documentation or Other Documentation where end user does not receive a EULA or does not have a valid license agreement with Intergraph, Intergraph grants the Licensee a non-exclusive license to use the Documentation or Other Documentation for Licensee’s internal non-commercial use. Intergraph Corporation gives Licensee permission to print a reasonable number of copies of Other Documentation for Licensee’s internal, non-commercial. The Other Documentation may not be printed for resale or redistribution. This license contained in this subsection b) may be terminated at any time and for any reason by Intergraph Corporation by giving written notice to Licensee.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Limitation of Damages IN NO EVENT WILL INTERGRAPH CORPORATION BE LIABLE FOR ANY DIRECT, INDIRECT, CONSEQUENTIAL INCIDENTAL, SPECIAL, OR PUNITIVE DAMAGES, INCLUDING BUT NOT LIMITED TO, LOSS OF USE OR PRODUCTION, LOSS OF REVENUE OR PROFIT, LOSS OF DATA, OR CLAIMS OF THIRD PARTIES, EVEN IF INTERGRAPH CORPORATION HAS BEEN ADVISED OF THE POSSIBILITY OF SUCH DAMAGES. UNDER NO CIRCUMSTANCES SHALL INTERGRAPH CORPORATION’S LIABILITY EXCEED THE AMOUNT THAT INTERGRAPH CORPORATION HAS BEEN PAID BY LICENSEE UNDER THIS AGREEMENT AT THE TIME THE CLAIM IS MADE. EXCEPT WHERE PROHIBITED BY APPLICABLE LAW, NO CLAIM, REGARDLESS OF FORM, ARISING OUT OF OR IN CONNECTION WITH THE SUBJECT MATTER OF THIS DOCUMENT MAY BE BROUGHT BY LICENSEE MORE THAN TWO (2) YEARS AFTER THE EVENT GIVING RISE TO THE CAUSE OF ACTION HAS OCCURRED. IF UNDER THE LAW RULED APPLICABLE ANY PART OF THIS SECTION IS INVALID, THEN INTERGRAPH LIMITS ITS LIABILITY TO THE MAXIMUM EXTENT ALLOWED BY SAID LAW.

Export Controls Intergraph Corporation’s software products and any third-party Software Products obtained from Intergraph Corporation, its subsidiaries, or distributors (including any Documentation, Other Documentation or technical data related to these products) are subject to the export control laws and regulations of the United States. Diversion contrary to U.S. law is prohibited. These Software Products, and the direct product thereof, must not be exported or re-exported, directly or indirectly (including via remote access) under the following circumstances: a.

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b.

To any person or entity listed on any U.S. government denial list, including but not limited to, the U.S. Department of Commerce Denied Persons, Entities, and Unverified Lists, http://www,bis.doc.gov/complianceandenforcement/liststocheck.htm, the U.S. Department of Treasury Specially Designated Nationals List, www.treas.gov/offices/enforcement/ofac/http://www.pmddtc.state.gov/compliance/debar.html, and the U.S. Department of State Debarred List.

c.

To any entity when Licensee knows, or has reason to know, the end use of the Software Product is related to the design, development, production, or use of missiles, chemical, biological, or nuclear weapons, or other un-safeguarded or sensitive nuclear uses.

d.

To any entity when Licensee knows, or has reason to know, that an illegal reshipment will take place.

Any questions regarding export or re-export of these Software Products should be addressed to Intergraph Corporation’s Export Compliance Department, Huntsville, Alabama 35894, USA.

Trademarks Intergraph, the Intergraph logo, Intergraph Smart, PDS, SmartPlant, SmartMarine, FrameWorks, I-Sketch, IntelliShip, ISOGEN, SmartSketch, SPOOLGEN, SupportManager, and SupportModeler are trademarks or registered trademarks of Intergraph Corporation or its subsidiaries in the United States and other countries. Microsoft and Windows are registered trademarks of Microsoft Corporation. MicroStation is a registered trademark of Bentley Systems, Inc. Other brands and product names are trademarks of their respective owners.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Contents Introduction .................................................................................................................................................. 7 Intergraph CAS Quality Assurance ........................................................................................................... 9 Software Purpose.................................................................................................................................... 9 Intellectual Property Statement ............................................................................................................... 9 Management/Organization .................................................................................................................... 10 PV Elite Development ........................................................................................................................... 10 User Documentation ............................................................................................................................. 10 Product Support .................................................................................................................................... 11 Software Issue Tracking/Resolution ..................................................................................................... 11 Software Verification ................................................................................................................................. 13 Test Control........................................................................................................................................... 13 Beta Tests ............................................................................................................................................. 14 Additional Manual Checks for Staff and Beta Users ............................................................................. 15 PV Elite Test Jobs ................................................................................................................................. 19 Corrective Action Standard ................................................................................................................... 20 Post-Development Procedures ............................................................................................................. 20 Distribution Control ............................................................................................................................... 21 Pre-Shipping Procedures ...................................................................................................................... 21 CodeCalc QA Checks ........................................................................................................................... 23 Introduction ..................................................................................................................................... 23 Shell and Head Checks .................................................................................................................. 24 Nozzle Checks................................................................................................................................ 26 Flange Checks................................................................................................................................ 28 Cone Checks .................................................................................................................................. 31 Floating Heads Checks .................................................................................................................. 32 Horizontal Vessel Checks .............................................................................................................. 34 Leg and Lug .................................................................................................................................... 34 ASME Tubesheets Checks ............................................................................................................ 36 TEMA Tubesheets Checks ............................................................................................................. 37 WRC 107 Checks ........................................................................................................................... 38 Pipe and Pad Checks ..................................................................................................................... 39 Base Ring Checks .......................................................................................................................... 39 Half-Pipe Check .............................................................................................................................. 40 Large Opening Checks ................................................................................................................... 41 Rectangular Vessel Checks ........................................................................................................... 42 PV Elite Sample Benchmark Problem Sets .......................................................................................... 45 Problem 1 - Natural Frequency Calculation ................................................................................... 45 Problem 2 - Example of Stiffening Ring Calculation ...................................................................... 49 Problem 3 - Nozzle Reinforcement, Weld Strength, Weld Size ..................................................... 52 Problem 4 - Vessel under Internal and External Pressure on Legs ............................................... 65 Problem 5 - Vertical Vessel with Wind and Seismic Loads ............................................................ 74 Problem 6 - Comparison against CAESAR II ................................................................................. 83 Problem 7 - ASME Section VIII Division 2 Sample Comparisons .................................................. 86 Problem 8 - EN-13445 Nozzle Reinforcement ............................................................................... 93

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Contents Index ......................................................................................................................................................... 101

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PV Elite and CodeCalc Verification and Quality Assurance Manual

SECTION 1

Introduction ®

®

The PV Elite /CodeCalc Verification and Quality Assurance Manual provides a standard set of PV Elite/CodeCalc jobs that are used in verifying both the operation of the software and the accuracy of the result for each release of the PV Elite/CodeCalc package. The examples presented in this manual are a representative cross-section of the jobs run by Intergraph CAS. The jobs selected for this manual compare the PV Elite/CodeCalc output with results published in industry journals and with results from other software products. The PV Elite/CodeCalc output is (also) verified with hand and/or MathCad™ calculations. The component-analysis part of PV Elite, when sold separately, is called CodeCalc. CodeCalc-specific results can be found in the Software Verification section of this manual. In all other sections, the software is referred to simply as PV Elite. This manual consists of two major sections: Intergraph CAS Quality Assurance and Software Verification. 

Intergraph CAS Quality Assurance describes the quality assurance procedures employed by Intergraph CAS to ensure that PV Elite is producing correct results.



Software Verification explains a series of benchmark jobs that you can use to confirm software accuracy. These jobs compare PV Elite output to published results, to output from similar software, or to hand calculations. For each job in this section, a brief description of the job and any special considerations are discussed. Following the discussion is a graphical representation of the system with selected result comparisons. Because of the volume of output, important results like required thickness, maximum allowable working pressure (MAWP), and stress are listed in tables. Users interested in the entire output can re-analyze the jobs as necessary.

The PV Elite development team is constantly testing and adding new test jobs to the QA benchmark problem set. Currently, there are more than 250 test jobs run which test thousands of different calculations. It is impractical to include all of these tests in this manual. As new Quality Assurance procedures are published, they will be incorporated into the QA methods employed by Intergraph CAS. Users with questions, comments, or suggestions are encouraged to contact Intergraph CAS to discuss future revisions to this document. User requests for new features are always welcome. By working with the user, the PV Elite development staff will continue to develop a product that best meets the demands of pressure-vessel design and analysis users.

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Introduction

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PV Elite and CodeCalc Verification and Quality Assurance Manual

SECTION 2

Intergraph CAS Quality Assurance Software quality assurance is generally a speculative pursuit because, no matter how much testing is performed, the next test may reveal an error in the software. The goal of any quality assurance standard is to perform enough testing to achieve such a level of confidence in the software that errors are rare and unlikely. With this objective in mind, several organizations have published guidelines for use in software quality assurance.

In This Section Software Purpose .......................................................................... 9 Intellectual Property Statement...................................................... 9 Management/Organization ............................................................ 10 PV Elite Development .................................................................... 10 User Documentation ...................................................................... 10 Product Support ............................................................................. 11 Software Issue Tracking/Resolution .............................................. 11

Software Purpose PV Elite is a package of nineteen applications that work together to design and analyze pressure vessels and heat exchangers. The purpose of the software is to provide the mechanical engineer with easy-to-use, technically sound, well-documented calculations that will expedite and simplify vessel-design and re-rating tasks. The software also provides recent, industry-accepted analyses of the designs. Calculations in PV Elite are based on the latest editions of national codes such as the ASME Boiler and Pressure Vessel Code, or other relevant industry standards that are not covered directly by ASME VIII-1, VIII-2 or other codes.

Intellectual Property Statement This manual and its contents should be considered proprietary. This material should not be copied or distributed to other parties without the expressed written consent of Intergraph CAS.

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Intergraph CAS Quality Assurance

Management/Organization At Intergraph CAS, the Chief Architect, Software Engineering Manager, and Product Manager oversee the development and testing of the software product. Software development team members include: engineers, software developers, and a technical writer. All members of the development team support customers and test the software prior to each release. Specialized technical support representatives work closely with the development team. In addition, an on-staff, certified Nuclear Quality Assurance (NQA) lead auditor oversees the quality assurance program followed by the team.

PV Elite Development Intergraph CAS is wholly responsible for all software made available to the public that bears the Intergraph label on the distribution media. Changes to PV Elite are made by or with the consent of the Product Manager. Additional members of the software team include engineers, who interact at the same level and communicate directly with the product manager. Therefore, all software issues can be brought to the attention of Product Manager quickly and easily. Software engineers each bring a different kind of expertise to the team and write routines for specialized functions in the software. For example, the source code to perform structural steel checks may be written by an engineer at Intergraph CAS whose educational background permits him to do this efficiently. All members of the development staff provide customer support for PV Elite, directly or indirectly. One member of the team is tasked with quality assurance procedures for each release.

User Documentation The PV Elite user has online access to documentation spanning all facets of the software, including all of the ancillary processors and interfaces. The standard PV Elite documentation set consists of the following documents: 

PV Elite User's Guide



CodeCalc User's Guide



Quick Start Guide

All of these documents can be accessed online, from the Help tab in PV Elite. The PV Elite documentation accompanies each new version of the program and is supplied in both PDF and CHM (online help) formats. Contact information for Intergraph CAS is included in these documents, as well as displayed in the help system, and in a variety of other locations in the software. We encourage users experiencing problems or confusion with the software to reference the documentation first, and then contact us for further resolution and suggestions.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Intergraph CAS Quality Assurance

Product Support Intergraph CAS welcomes input/suggestions from our users. Users having problems with our software may freely contact Intergraph CAS through our eCustomer support system, which is found on our company website. Our Technical Support staff may ask users with a numerical/computational issue in PV Elite to submit the job to Intergraph CAS. This allows our support staff to identify the problem and locate the cause, and then contact the user for resolution.

Software Issue Tracking/Resolution PV Elite supports standard practices for tracking released software issues, including: 

Incorporating user feedback directly back into the development process.



Notifying users regarding hot fix or service pack updates issued throughout development



Following software release criteria based on issue review and prioritization.

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Intergraph CAS Quality Assurance

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PV Elite and CodeCalc Verification and Quality Assurance Manual

SECTION 3

Software Verification This section describes the test methods through which PV Elite software team performs Quality Assurance testing on PV Elite. In addition, the section describes test methods that you can implement to validate your PV Elite program data against industry-standard benchmarks.

In This Section Test Control ................................................................................... 13 Beta Tests ...................................................................................... 14 Additional Manual Checks for Staff and Beta Users ..................... 15 PV Elite Test Jobs ......................................................................... 19 Corrective Action Standard ............................................................ 20 Post-Development Procedures ...................................................... 20 Distribution Control ........................................................................ 21 Pre-Shipping Procedures ............................................................... 21 CodeCalc QA Checks .................................................................... 23 PV Elite Sample Benchmark Problem Sets ................................... 45

Test Control Currently in the United States there is no organization that formally establishes the credibility of pressure-vessel analysis software. Therefore, software suppliers take on this responsibility. Generally, there are two ways to establish that any software product is performing correctly: 

Comparing product results to hand calculations.



Comparing results to previously verified results from an external source.

If these methods compare favorably to software-generated results, then the software is assumed to be performing as expected. If the results do not compare favorably, the PV Elite development team identifies the differences and corrects the problem.

Testing Process Before a new version of PV Elite is released, the development personnel perform alpha-level testing. This involves checking the Fortran/C++ or assembler code and running of basic test problems designed to test the functionality of the feature addition, error and abort conditions, and so forth. Next, the development staff generates a series of alpha jobs that: 

Test new features against existing software.



Run tests against industry standard programs, such as Compress™ and BJAC™ teams.



Suggest to customers that they independently compare the results of PV Elite against their own in-house program or spreadsheets.



Test new features against hand calculations.



Test new features against published literature, such as the ASME VIII-1, PTB-3, and other codes.

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Software Verification 

Test the interaction between new features and features already existing in the software.

Once these selected alpha jobs are run and verified to the satisfaction of the lead developer, beta series testing begins. The new job results are compared to the previously verified results. Program errors that have been identified are remedied and/or justified. To summarize, at Intergraph CAS, we believe that thoroughly checking software results by hand and comparing these results to those of other software and to benchmarks assures a quality product. This method has worked very well in the past and we will check new versions using this same methodology.

Beta Tests Often before releasing the PV Elite software, we distribute the alpha-tested software to users to perform beta testing. At the end of the test period, we ask that beta users send evaluations to us, so that we can process the information, resolve any issues found, and archive feedback. The following are the beta test files for the CodeCalc module available from within PV Elite. Intergraph CAS ships some of these files with the PV Elite software. Beta Test Files Checks.cci

Shell.cci

Extra_qa.cci

Texample.cci

Fexample.cci

Texample2.cci

Fexample2.cci

Vesexmpl.cci

Lg_nozzl.cci

WRC107.cci

Lg_nozzl.cci

Rctexmpl.cci

Mm_wrc.cci

Appy.cci

ASME_Tubesheet.cci The following section discusses manual checks that users can perform additional verification of the software.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Additional Manual Checks for Staff and Beta Users The tables below display a list of items that should be verified for each release of PV Elite. Different individuals should check each item multiple times.

Installation Checklist Items to Check

Initials

Initials

Comments

Initials

Initials

Comments

A. Program Installation B. File Extraction C. File CRC Check

Database Access Checklist Items to Check A. Structural Steel - AISC89.BIN B. ASME Materials * 1. Check some material properties (selected randomly) with ASME Code 2. Check yield stress vs. temperature table. * Specify different material ID in the input, and check the allowable stresses, density, TEMA number, and external pressure chart.

Units Checklist Items to Check

Initials

Initials

Comments

A. Creation of input files B. Verify change of units Check each input field of the following modules to verify that the help facilities function properly.

Help Checklist Items to Check

Initials

Initials

Comments

A. Check Modules

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Software Verification Items to Check

Initials

Initials

Comments

1. Shells and Heads 2. Nozzles 3. Flange 4. Conical Sections 5. Floating head 6. Horizontal Vessels 7. ASME Tubesheets 8. Tubesheets 9. WRC107/FEA 10. Leg and Lug 11. Pipe and Pad 12. Base Rings 13. Thin Bellows Exp. Joints 14. Thick Joints 15. Half-Pipe 16. Large Openings 17. Rectangular Vessels 18. WRC 297/Annex G 19. Appendix Y B. Check HELP Index. C. Search on a topic. D. Print a HELP topic.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification New Input Generation/General Operation Checklist Items to Check

Initials

Initials

Comments

A. Check each module with a random example. 1. Shells and Heads 2. Nozzles 3. Flange 4. Conical Sections 5. Floating head 6. Horizontal Vessel 7. ASME Tubesheets 8. TEMA Tubesheets 9. WRC 107 10. Leg and Lug 11. Pipe and Pad 12. Base Rings 13. Thin Joints 14. Thick Joints 15. Half Pipes 16. Large Openings 17. Rectangular Vessels 18. WRC 297 19. Appendix Y B. Graphics 1. Onscreen 2. Printed

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Software Verification Items to Check

Initials

Initials

Comments

Initials

Initials

Comments

Initials

Initials

Comments

C. Window operation 1. Merge operation 2. Insert/Delete an item 3. Add an item 4. Browse items

Output Review Checklist Items to Check A. Review output data in 1. Terminal 2. Printer 3. Disk file B. Output Processor 1. Results on screen 2. Print the selected chapters

Operating Environments Checklist Items to Check A. Dealer Version B. Windows C. Network 1. PV Elite and data on network 2. PV Elite on network, data local 3. PV Elite local, data on network

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Vessel Code Checklist Items to Check

Initials

Initials

Comments

Initials

Comments

ASME Section VIII, Div. 1 ASME Section VIII, Div. 2 PD-5500 EN - 13445

Miscellaneous Checklist Items to Check A. ESL/SPLM

Initials

(a)

B. Mouse Operations C. Material Database Editor 1. Editing materials 2. Adding materials (a)

Insures program does not run without the ESL.

PV Elite Test Jobs The PV Elite QA benchmark problem set consists of over 250 different analysis jobs. Each of these jobs is run prior to release time and compared with the results from previous versions. A wide variety of jobs are checked, which includes tests of all wind and seismic codes, checks of baserings, weights, stresses, liquid pressures, MAWP, weights, volumes, required thickness and many others. By analyzing these jobs, the quality of the software is kept very high and consistent. Again, these are just a few sample problems run every time we test the software. Many of the jobs contained in this manual are listed in the table below.

Quality Assurance Test Form Job Name

Perform Analysis

Analysis Date

104EX4 11436 ANDY1 APP1_7

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Software Verification Job Name

Perform Analysis

Analysis Date

APP1_7_2 APP1_7_3 APPLCHK AS_450V2 BEDN237 +200 more jobs

Corrective Action Standard PV Elite users have many channels through which they can reach the Intergraph CAS development staff. The main way to contact us is through the eCustomer system. When a problem or error is detected, the development staff reviews the problem and takes corrective action. When a user problem is verified to be a defect, a TR (trouble report) is filled out using internal Intergraph software. After the TR is completed, the problem is fixed, and the user is notified by email through the eCustomer system. Updated PV Elite files are made available in a product Hot Fix or Service Pack, which can be downloaded from the eCustomer website. In many cases, software issues have workarounds. The Intergraph CAS technical support staff notifies users of workarounds whenever possible.

Post-Development Procedures After a new version of the software has been developed, Intergraph CAS uses the following quality assurance procedures to ensure that the new CDs are correct in content, contain the proper ESL protection schemes, and can be reproduced properly. 1. Scan the development machine for virus infection before producing any distribution set. Use the latest version of Trend Micro Office Scan virus-scanning software. 2. Assemble in a "clean" directory all of the files that comprise the installation set. This includes .EXE files, database files, and example files. 3. Run the CRCCHK program to build the CRC verification file. 4. Generate an installation program using Install Shield. Once the DVD is made, test it according to the Distribution Control procedures outlined below.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Distribution Control To control the distribution and integrity of the program DVDs before sending them out for mass production, Intergraph CAS adheres to the following procedures: 1. After the quality assurance procedures have been completed, use the lead developer's computer to make a production copy of PV Elite. 2. Modify the installation program to load any new executables that may be released with the new version. 3. Load PV Elite onto at least one PC in the production department to check the installation program and DVD integrity. 4. Use Office Scan virus-scanning software to scan each original, all disk drives, and memory for known viruses. 5. Using the appropriate ESL, install and test the masters on another computer. All EXE files accessing the ESL must be tested. 6. Install the masters on a production computer for further use. ESL-specific files should be copied into the appropriate subdirectories for organizational purposes. 7. Send the masters to the DVD duplicator. 8. Install the software from the DVD onto each of the PCs in the engineering and development groups at Intergraph CAS. 9. Load the required set of PV Elite executables onto at least one computer in the production department. 10. Using the DVD and installation checklists, perform periodic testing of the software as necessary. The following section provides the tasks that must be performed by the development and production personnel to verify the quality of disk sets before shipment.

Pre-Shipping Procedures The following procedures help to ensure that the disk sets shipped by Intergraph CAS contain the correct product, are not infected with a virus, and are void of imperfections. 1. When DVDs are received from the duplicator, install and test a random selection from the batch. These final tests will ensure that the DVDs were correctly assembled by the duplicator, that they are not flawed, and that the ESL interaction routines are in order. The tests are software-specific and are detailed elsewhere in this manual. None of these tests should use the environment support available from the programs. Run the tests from the installation directory. Ensure that the installation directory is empty before beginning this procedure. 2. Archive a set of DVDs from the first duplication for future use and referral.

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Software Verification

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PV Elite and CodeCalc Verification and Quality Assurance Manual

SECTION 4

CodeCalc QA Checks In This Section Introduction .................................................................................... 23 Shell and Head Checks ................................................................. 24 Nozzle Checks ............................................................................... 26 Flange Checks ............................................................................... 28 Cone Checks ................................................................................. 31 Floating Heads Checks .................................................................. 32 Horizontal Vessel Checks .............................................................. 34 Leg and Lug ................................................................................... 34 ASME Tubesheets Checks ............................................................ 36 TEMA Tubesheets Checks ............................................................ 37 WRC 107 Checks .......................................................................... 38 Pipe and Pad Checks .................................................................... 39 Base Ring Checks ......................................................................... 39 Half-Pipe Check ............................................................................. 40 Large Opening Checks .................................................................. 41 Rectangular Vessel Checks ........................................................... 42

Introduction This section provides the results of QA tests for CodeCalc, which is also the component-analysis part of PV Elite. For simplicity, this part of PV Elite will be referred to as CodeCalc in this chapter. The following CodeCalc modules have been subjected to Intergraph CAS quality assurance procedures. 

Shell/Head



Nozzle



Flange



Cone



Floating Head



Horizontal Vessel



Leg and Lug



ASME Tubesheets



TEMA Tubesheets



WRC 107/537



Pipe and Pad



Base Ring



Thin Joint



Thick Joint

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Software Verification 

Half-Pipe



Large Opening



Rectangular Vessel

Shell and Head Checks As a part of its quality assurance procedures, Intergraph CAS completed the following shell and head checks on CodeCalc: ASME Appendix 1-4, 2 (CodeCalc job: Checks.cc2/ASME VIII-1 2011a, APP 1, 1-4, 2) Ellipsoidal head under internal pressure. Parameters

CodeCalc

ASME

MAWP (psi)

338.87

339

ASME Appendix 1-4, D (CodeCalc job: Checks.cc2/ASME VIII-1 2011a, APP 1, 1-4, D) -Torispherical head under internal pressure Parameters

CodeCalc

ASME

Req. thickness (in.)

0.4488

0.45

ASME Appendix 1-4, D2 (CodeCalc job: Checks.cc2/ASME VIII-1 2011a, APP 1, 1-4, D2) -Torispherical head under internal pressure Parameters

CodeCalc

ASME

MAWP (psi)

167.16

167

ASME Appendix L-6.1 (CodeCalc job: Checks.cc2/ASME VIII-1 2011a, APP L, L-6.1) Ellipsoidal head under external pressure Parameters

CodeCalc

ASME

A

0.0004623

0.000462

B

5662.91*

5100

EMAWP (psi)

20.9427*

18.9

ASME Appendix L-6.2 (CodeCalc job: Checks.cc2/ASME VIII-1 2011a, APP L, L-6.2) -Torispherical head under external pressure

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Parameters

CodeCalc

ASME

A

0.0004157

0.00042

B

5092.85*

4700

EMAWP (psi)

16.9385*

15.6

ASME Appendix L-6.3 (CodeCalc job: Checks.cc2/APP L, L-6.3) -Hemispherical head under external pressure Parameters

CodeCalc

ASME

A

0.0004623

0.00046

B

5662.91*

5200

EMAWP (psi)

20.9427*

19.23

ASME Appendix L-6.4 (CodeCalc job: Checks.cc2/APP L, L-6.4) - Conical head under external pressure Parameters

CodeCalc

ASME

Design Len.

102.30

102.30

A

0.0005912

0.0006

B

7004.29

6900

EMAWP (psi)

38.1777

37.5

ASME Appendix L-9.2.1 (CodeCalc job: Checks.cc2/APP L, L-9.1, 2) - Minimum design metal temperature (MDMT) of a cylinder Parameters

CodeCalc

ASME

Unadjusted MDMT (°F)

31

31

Adjusted MDMT (°F)

12

12

ASME Appendix. L-5 (CodeCalc job: Checks.cc2/APP L, L-5): Selection of a circumferential stiffening ring for a cylinder under external pressure. A bar type 2 in. x 3.75 in. stiffening ring selected.

PV Elite and CodeCalc Verification and Quality Assurance Manual

25

Software Verification Parameters

CodeCalc

ASME

Moment of Inertia (in. )

16.541

16.57

Required Moment of 4 Inertia (in. )

16.1933

16.25

Weld load

643.78

644

Weld Allowable load

1828.75

1830

Minimum Weld Thickness

0.25

0.25

4

* As of this printing the ASME Appendix L6.1, 6.2, 6.3 appear to be in error in determining the B value from the External Pressure chart CS-2 for SA-285C, with E = 24.5 x 106 psi. When points lie in the linear portion of the chart CS-2 (as in cases 4, 5, 60, CodeCalc uses the formula B = A*E/2.

Nozzle Checks Nozzle checks involve the area of reinforcement and failure path calculations. Intergraph CAS performed the following nozzle checks using CodeCalc: ASME Appendix L-7.3b (CodeCalc Job: Checks.cc2/APP L, L-7.3B): Insert-type Nozzle lying on a longitudinal weld of a cylindrical shell. A 19-in. Diameter and 0.5-in. thick reinforcement pad is selected. Parameters

CodeCalc

ASME

Req. Thk. Shell (in.)

0.5300

0.530

Req. Thk. Noz (in.)

0.0893

0.0893

6.228

6.23

Total Area available (in. )

6.267

6.27

Total weld load, W (lb)

72539.17

72600

Weld load for path 1-1, W 1-1 (lb)

71556.86

71600

Weld load for path 2-2, W 2-2 (lb)

34856.25

34900

Weld load for path 3-3, W 3-3 (lb)

82280.86

82300

Strength of failure path 1-1 (lb)

203289

203000

Strength of failure path 2-2 (lb)

229116

229000

Strength of failure path 3-3 (lb)

250441

250000

2

Reinforcement Area Req. (in. ) 2

26

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification ASME Appendix L-7.4 (CodeCalc Job Checks.cc2/APP L, L-7.4): Abutting-type Nozzle on a cylindrical shell. A 26-in. Diameter and 2.75-in. (average value) thick reinforcement pad is selected. Parameters

CodeCalc

ASME

Req. Thk. Shell (in.)

1.8593

1.83

Req. Thk. Noz (in.)

0.3542

0.292

29.554

29.6

Total Area available (in. )

33.647

33.7

Total weld load, W (lb)

317668.22

318000

Weld load for path 1-1, W 1-1 (lb)

364331.03

364000

Strength of failure path 1-1 (lb)

319507

318000

2

Reinforcement Area Req. (in. ) 2

ASME Appendix L-7.6 (CodeCalc Job Checks.cc2/APP L, L-7.6): Insert-type Nozzle without pad on a 2:1 ellipsoidal head. Parameters

CodeCalc

ASME

Req. Thk. Head (in.)

0.0912

0.091

Req. Thk. Noz (in.)

0.0512

0.051

0.755

0.754

Total Area available (in. )

1.146

1.15

Total weld load, W (lb)

302.43*

250

Weld load for path 1-1, W 1-1 (lb)

2992.86

2990

Weld load for path 2-2, W 2-2 (lb)

7691.86

7690

Strength of failure path 1-1 (lb)

47542

47500

Strength of failure path 2-2 (lb)

39831

39800

2

Reinforcement Area Req. (in. ) 2

*The differences in dimensions, of the order of 1E-3, are magnified after being multiplied by the allowable stress. ASME Appendix L-7.7 (CodeCalc Job Checks.cc2/APP L, L-7.71): Abutting-type Hillside Nozzle on a cylindrical shell.

PV Elite and CodeCalc Verification and Quality Assurance Manual

27

Software Verification Parameters

CodeCalc

ASME

Req. Thk. Shell (in.)

1.1364

1.14

Req. Thk. Noz (in.)

0.1389

0.139

Area Req. in circumferential dir. 2 (in. )

3.720

3.68

Area available in circumferential 2 dir. (in. )

7.486

7.16

Area Req. in longitudinal dir. 2 (in. )

4.545

4.56

Area available in longitudinal dir. 2.607 2 (in. )

2.59

The area available in the longitudinal direction is insufficient. The new area values after increasing the nozzle thickness from 0.5 in. to 0.875 in. Parameters

CodeCalc 2

ASME

Area Req. in longitudinal dir. in. ) 4.545

4.56

Area available in longitudinal dir. 5.198 2 (in. )

5.18

2

Minimum Weld throat. (in. ) 2

Actual Weld throat. (in. )

0.25

0.25

0.3535

0.35

Flange Checks Intergraph CAS completed the following flange checks on CodeCalc: Taylor Forge, Bulletin 502 (CodeCalc Job: Checks.cc2/TAYLOR FORGE)- Integral weld neck flange.

Operating

28

Parameters

CodeCalc

Taylor Forge

Gasket Reaction Diameter, G (in.)

33.888

33.88

Bolt Load W M1 (lb)

432484.688

432484

Gasket Seating Force, HG (lb)

71713.25

71713

End Pressure, MD (in. lb)

623292

623292

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Seating

Parameters

CodeCalc

Taylor Forge

Face Pressure, MT (in. lb)

79248

79242

Gasket Load, MG (in. lb)

111600

111599

Total Moment, Mo (in. lb)

814128

814133

Longitudinal Hub Stress (psi)

22865.0

22865

Radial Flange Stress (psi)

10981.8

10982

Tangential Stress Flange (psi)

6799.5

6800

Bolt Load, W M2 (lb)

120608.648

120609

Flange Design Bolt Load, W (lb)

464192.38

464192

Total Moment, MG (in. lb) *

722364

722371

Longitudinal Hub Stress (psi)

20287.8

20288

Radial Flange Stress (psi)

9744.0

9744

Tangential Stress Flange (psi)

6033.1

6033

*Total Moment is MG in the Taylor Forge bulletin 502 and MA in CodeCalc output. Taylor Forge, Bulletin 502 (CodeCalc Job: Checks.cc2/ FULL FACE SLIP)- Loose, Slip on Flange with a full face gasket.

Operating

Parameters

CodeCalc

Taylor Forge

Dist. to Gasket Load Reaction hg, (in.)

1.328

1.325

Gasket Reaction Diameter, G (in.)

26.844

26.85

Full Face ID Pressure Load, H’GY (lb)

48614.715

48555

Bolt Load, WM1 (lb)

96302.469

96286

Gasket Seating Force, HG (lb)

68003.63

67994

End Pressure, MD (in. lb)

93300

93305

Face Pressure, MT (in. lb)

17364

17390

Total Moment, MO (in. lb)

110676

110695

PV Elite and CodeCalc Verification and Quality Assurance Manual

29

Software Verification

Seating

Parameters

CodeCalc

Taylor Forge

Longitudinal Hub Stress (psi)

1951.8

1995

Radial Flange Stress (psi)

5141.6

5236

Tangential Flange Stress (psi)

13470.3

13176

Bolt Circle Stress (psi)

2585.7

2679

Bolt Load, WM2 (lb)

71806.469

23196

Flange Design Bolt Load, W (lb)

110451.23

110460

Reverse Moment MG (in. lb) *

29160

29101

*Reverse Moment is MG in Taylor Forge bulletin 502 and MR in CodeCalc output. See "Notes" below.

a. The value of hg, in the Taylor Forge Bulletin is off by 0.0029, using

With C = 29.5 in. and B =24 in. this comes out to be 1.3279 and not 1.325. This error is G magnified resulting in error in the calculations of G, W M1, W, H , MT, MO, MG, and H’GY. b. The value of WM2 computed in the Taylor Forge Bulletin is incorrect,

Where b = 1.375, y = 200 Gives W M2 = 71806.5 An example taken from Process Equipment Design by Brownell and Young. (P-243) (CodeCalc Job: Checks.cc2/BROWNELL&YOUNG)- Loose-ring type flange. *Total Flange Moment is MA in Brownell & Young and RMA in CodeCalc output.

Operating

30

Parameters

CodeCalc

Brownell & Young

Gasket Reaction Diameter, G (in.)

33.250

33.25

Bolt Load, W M1 (lb)

151790.469

152100

Gasket Seating Force, HG (lb)

21544.45

21600

End Pressure, MD (in. lb)

198132

226000

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Seating

Parameters

CodeCalc

Brownell & Young

Face Pressure, MT (in. lb)

20220

25200

Gasket Load, MG (in. lb)

13464

18900

Total Moment, MO (in. lb)

231816

270100

Bolt Load, W M2 (lb)

96623.617

93600

Flange Design Bolt Load, W (lb)

172855.25

160500

Total Moment MG (in. lb) *

1806036

140500

Cone Checks Cone checks involve area-of-reinforcement and moment-of-inertia requirements. Intergraph CAS performed the following cone checks using CodeCalc: ASME Appendix L-2.3 (CodeCalc Job: Checks.cc2/ASME VIII-1 2011a, APP L, L-2.3): - A cone-to-cylinder transition under internal pressure.

Large end

Parameters

CodeCalc

ASME

Line Force, QL (lb)

2749.608

2750

12.8802

4.54

Total Area available , Ael(in. )

0.3490

0.500

Line Force, QA (lb)

1312.383

1312.5

2.2146

2.22

0.7799

0.78

2

Reinforcement Area Req., Arl (in. ) 2

Small end

2

Reinforcement Area Req., Ars (in. ) 2

Total Area available, Aes (in. )

ASME Appendix L-3.3 (CodeCalc File: Checks.cc2/APP L, L-3.3): - A cone-to-cylinder transition under external pressure.

Large end

Parameters

CodeCalc

ASME

Line Force, QL (lb)

9.6960

2781

12.6509

12.7

23.5682

28.9

2

Reinforcement Area Req., Arl (in. ) 2

Total Area available, Ael (in. )

PV Elite and CodeCalc Verification and Quality Assurance Manual

31

Software Verification Small end

Line Force, QS (lb)

697.3355

696.9

2

0.7046

0.71

Area available in Shell, Aes ( in. )*

2.5022

2.05*

2.6250

2.63

5.8318

4.68

Reinforcement Area Req., Ars (in. ) 2

2

Area available in Pad (in. ) 2

Total Area available, Aes (in. )

The small end available area from the shell does not match as a result of different values of tr, the minimum required thickness of cone at small end. CodeCalc calculates this value iteratively so that the cone can withstand the design pressure. With, E = 25.125 * 106 psi, A = 4.453 * 10-6, B = 5595.042, D/T = 149.191 CodeCalc computes a tr of 0.392 in., resulting in a MAWP of

which matches the design pressure of 50 psi. The ASME example uses a tr = 0.55 in., which seems incorrect.

Floating Heads Checks Intergraph CAS completed the following floating heads checks on CodeCalc: Tested against Exxon’s in-house design program PEAs- A Type D floating head under both external and internal pressure. (CodeCalc job: Extra_Qa.cc2/TYPE D)

Tubeside Internal Pressure Results:

Operating

Seating

32

Parameters

CodeCalc

PEAs

Head Req. Thickness (in.)

0.3601

0.360

Flange Req. Thickness (in.)

3.2956

3.296

Operating Bolt Load, W M1 (lb)

302398.0

302398

Gasket Seating Force, HG (lb)

44348.5

44348.4

Flo. Head Moment, Mh (in. lb)

-136812

-136739.5

Total Moment, Internal, MO (in. lb)

127584

127660.90

Flange Req. Thickness, Internal Bolt-Up (in.)

3.4527

3.453

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Parameters

CodeCalc

PEAs

Flange Design Bolt Load, W (lb)

335559.0

335559.0

Total Moment, Internal MG (in. lb) *

235939.9

235939.92

Parameters

CodeCalc

PEAs

Head Req. Thickness (in.)

0.6158

0.609

Flange Req. Thickness (in.)

4.0155

4.015

Operating Bolt Load, W M1 (lb)

302398.0

302398

Gasket Seating Force, HG (lb)

430082.6

430082.59

Flo. Head Moment, Mh (in. lb)

-228012

-227899.17

Total Moment, MO (in. lb)

141715.56

141604.46

Flange Req. Thickness (in.)

3.4527

3.453

Flange Design Bolt Load, W (lb)

335559.0

335559.0

Total Moment MG (in. lb) **

235939.94

235939.92

Shellside External Pressure Results:

Operating

Seating

The results below are for Soehrens Calculations for Stresses in Spherical Heads and Flanges. The following table displays the Nomenclature and Equation Numbers per ASME Paper 57-A-247. CodeCalc Tubeside Int.

Parameter

CodeCalc Shellside Ext.

PEA Shellside Ext.

Ttl Stress at Head OD, psi Eqn. 30

6611.2

6611.218

21175.1

21175.1

Ttl Stress at Head ID, psi Eqn. 31

1202.5

1202.488

-33058.6

-33058.6

Ttl Flange Stress, Upper psi Eqn. 35

746.6

746.647

5081.8

5081.8

Ttl Flange Stress, Lower psi Eqn. 36

-7432.6

-7432.58

-3803.6

-3803.6

Parameters

PV Elite and CodeCalc Verification and Quality Assurance Manual

33

Software Verification

Horizontal Vessel Checks Intergraph CAS completed the following horizontal vessel checks on CodeCalc: ASME APP L, L-2.2 (CodeCalc job Checks.cc2/ASME PG 530): Insert-type Nozzle lying on a longitudinal weld of a cylindrical shell. A 19-in. diameter and 0.5-in. thick reinforcement pad selected. Parameters

CodeCalc

ASME

Factor K.2 *

0.7906

0.7904

Total weight of the vessel, full (lb)

345837.91

350000

Longitudinal Compressive Shell allowable (psi)

9440.10

9446

The factor k.2 is an important factor used by CodeCalc to compute the stresses using Zick analysis. ASME has used a different method to find the required thickness. Moreover, ASME does not compute shear stresses at the saddles in this example.

Leg and Lug Intergraph CAS completed the following leg and lug checks on CodeCalc: Design of legs for a vertical vessel under internal pressure and wind loading, verified by hand calculations (CodeCalc job: ExtraQa.cc2/Hand Check Legs). Angle legs attached in the diagonal orientation (both legs attached to the vessel). Wind velocity is 100 miles/hr. Importance factor = 1 Force coefficient = 1 Exposure category = C Parameters

CodeCalc

Hand Check

Wind Pressure (psf)

28.038

28.88

Total Wind Force (lb)

1345.848

1376.7

Shear at Top of Leg (lb)

530.53

542.02

Total Overturning Moment at Top of Legs (ft-lb)

3364.6

3441.85

Axial Compression on Leg

910.71

915.76

Furthest from Neutral Axis (psi)

34

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Unity Check on the Legs: Parameters

CodeCalc Actual

Hand Check Allowable

Actual

Allowable

Weak Axis Bending Stress (psi) 16384.77

24227.28

16723.5

24227

Strong Axis Bending Stress (psi)

11613.22

24227.28

11869

24227

Axial Compressive Stress (psi)

910.71

16053.99

915.7

16068

Unity Check Ratio

1.212

1.237

Design of a support lug for a vertical vessel. Taken from the Pressure Vessel Design Handbook by Bednar, 2nd edition (page 154) example 5.1 (CodeCalc job: Lugs.cc2/BEDNAR EX. 5.1). Parameters

CodeCalc

BEDNAR

Force on One Lug, F (lb)

41,000.64

41,000

Bending Stress in the Base Plate  (psi)

13,814.78

18,700

Gusset Plate Allowable

9,785.29

9,885

Compressive Stress, SgaB (psi) The bending stress in the base plate s which, is Spl2 in the CodeCalc printouts is calculated as,

This expression is for stress on a rectangular plate under uniform pressure p, with three edges fixed and one edge free. (Formulas for Stress and Strain, Roark and Young, 5th edition page 396.) With,

Where, a = 15 in., b = 12 in., t = 1.125 in. The factor  is taken from a table in Roark and Young for a known of a/b, which in this case is 1.25. The correct value of  after interpolating is 0.524, which gives σ a value of 13580.22 psi. While Bednar took the next higher value of  as 0.72, this results in a different value of σ.

PV Elite and CodeCalc Verification and Quality Assurance Manual

35

Software Verification This example is for the design of a support lug with Full Ring-Girder type reinforcement ring. nd Taken from the Pressure Vessel Design Handbook by Bednar, 2 edition (page 158) example 5.2 (CodeCalc job: Lugs.cc2/BEDNAR EX. 5.2).

Ring load pt

Ring mid pt

Parameters

CodeCalc

Bednar

Force on one lug (compression side), Flug (lb.)

5000.00

5000

Force acting in the plane of ring, P (lb.)

2500.00

2500

Bending moment, M1 (lb-in)

29841.55

29900

Tangential thrust, T1 (lb.)

0.00

0.0

Bending moment, M2 (lb-in)

42583.66

17062.5

Tangential thrust, T2 (lb.)

1250.00

1250

ASME Tubesheets Checks These examples follow the 1997 edition of the ASME code. ASME Part UHX - 20.1.1 (c) (CodeCalc job: ASME_Tubesheet.cc2/UHX-20.1.1): U-tube type heat exchanger with integral tubesheet construction. Parameters

CodeCalc

ASME

Eff. Tube hole dia., d*(in.)

0.7500

0.75

Eff. Tube pitch, p*(in.)

1.1508

1.15

Axial Shell bending Stress,σ s,b (psi) -17575.04

-17600

ASME Part UHX - 20.2.1 (c) (CodeCalc job: ASME_Tubesheet.cc2/UHX-20.2.1) A fixed tubesheet with tubesheet extended as flange and gasketed channel side. This is compared with ASME UHX 20.2.1, step 10 case 7.

36

Parameters

CodeCalc

ASME

Shell Membrane Stress due to Joint Interaction, σ sm (psi)

-99.1947

-96.1

Shell Bending Stress due to Joint Interaction, σ s, b (psi)

-61109

-61100

Shell Stress Summation, σs (psi)

61217.12

61200

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Parameters

CodeCalc

ASME

σs, Allow

61500.00

61500

Bending stress σ (Pres. Only) (psi) Effective pres. Pe (Temp. only) (psi) Bending stress σ (Temp. only) (psi)

TEMA Tubesheets Checks A fixed tubesheet with the tubesheet extended has a flange and a gasketed channel side. This TM is compared with B-JAC teams, a heat exchanger design package. (CodeCalc job: Checks.cc2/COMPARISON). Parameters

CodeCalc

B-JAC

Eff. Shell side design Pres., bend., PSU (psi)

5.664

5.8

Eff. Tube side design Pres., bend., PTU (psi)

55.069

55.1

Req. Thk. Shellside, Trs (in.)

0.8304

0.8205

Req. Thk. Tubeside. Trc (in.)

2.5893

2.524

Equiv. Differential Exp. Pres., PD (psi) -0.488

0.0*

Shell longitudinal stress (Tensile), STSMAX (psi)

44

0.0*

Shell longitudinal stress (Comp.), STSMIN (psi)

278

296

Tube longitudinal stress (Tensile), STTMAX (psi)

12556.94

12772

Tube longitudinal Stress (Comp.), STTMIN (psi)

117.77

0*

Tube to Tubesheet load, WJ (lb)

1355.03

1378

TM

This difference in the value of Pd and stresses is due to different interpretation of factor J,

PV Elite and CodeCalc Verification and Quality Assurance Manual

37

Software Verification

…(a)

TEMA suggests that if,

Then, J can be assumed equal to 0, this is used by BJAC. According to some experts J should be taken 0 if,

…(b)

and

CodeCalc uses this interpretation. Consequently, there are differences in the Pd, the Shell longitudinal tensile stress, and the Tube longitudinal compressive stress values obtained from both the programs.

WRC 107 Checks TM

This example is a comparison with another computer program, called Compress . This example compares a round solid attachment on a cylindrical shell. (CodeCalc job: Extra_qa.cc2/COMPAR. TO COMP).

Using WRC 107 March 1979 Version

38

Parameters

CodeCalc

Compress

Beta

0.230

0.23

Total circumferential stress @ Au (psi)

-34281

-30118

Total Longitudinal stress @ Bl (psi)

30083

32407

Total shear stress @ Cu (psi)

-92

-92

Stress Intensity, @ Al (psi)

30283

32574

Stress Intensity, @ Bu (psi)

47999

45950

Stress Intensity, @ Cl (psi)

41165

43630

Stress Intensity, @ Du (psi)

58573

51845

Stress Intensity, @ Dl (psi)

40655

43100

TM

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Pipe and Pad Checks A B31.3 intersection area of reinforcement and MAWP calculations tested with MathCad calculations. (CodeCalc Job: Extra_Qa.cc2 /Hand_Calcs). Parameters

CodeCalc

PEAs

Req. thk. of header (in.)

0.450

0.449

Req. thk. of branch (in.)

0.194

0.194

Req. reinforcement area (in.2)

3.4855

3.485

Available reinforcement area (in.2)

3.6052

3.604

MAWP of Header (psi)

694.18

694.13

MAWP of Branch (psi)

1385.28

1385.19

Est. MAWP of Assembly (psi)

609.60

609.55

Base Ring Checks This example is benchmarked with hand calculations. A base ring with a continuous top ring. (CodeCalc job: Checks.cc2/PVHB EXAMPLE). The following illustrates the comparison of results for a simplified analysis for base ring thickness from Jawad and Farr. Parameters

CodeCalc

Hand Calcs

Load per bolt, (lb)

43527.7344

43528

Req. Area/Bolt, (in. )

1.7411

1.741

Bolt stress, approx. analysis (psi)

18925.10

16413

Concrete stress, operating condition (psi)

813.64

875.31

Basering Thk., simplified (in.)

1.8677

1.937

2

More accurate analysis using neutral axis shift calculations for base ring thickness, from Singh and Soler. Parameters

CodeCalc

Hand Calcs

Bolt stress (psi)

14244.13

12549

PV Elite and CodeCalc Verification and Quality Assurance Manual

39

Software Verification Parameters

CodeCalc

Hand Calcs

Concrete stress (psi)

493.33

478.84

Basering Thk. (in.)

1.4573

1.432

Parameters

CodeCalc

Hand Calcs

Req. Thk. as fixed beam (in.)

1.7850

1.916

Req. Thk. per Moss (in.)

1.3669

1.467

Parameters

CodeCalc

Hand Calcs

Req. Thk. in tension (in.)

0.3286

0.378

Req. Thk. in compression (in.)

0.672

0.672

Continuous Top Ring Calculations:

Gusset Thickness:

Skirt Thickness at Operating Condition: Parameters

CodeCalc

Hand Calcs

Req. Thk. in tension (in.)

0.3286

0.398

Req. Thk. in compression (in.)

0.2835

0.287

Half-Pipe Check ASME Appendix EE-3 (CodeCalc Job: Checks.cc2/ ASME EXAMPLE): A cylindrical shell with a half-pipe. Parameters

CodeCalc

ASME

Min. req. thk. of shell, Int. press. (in.)

0.2392

0.24

385.3763

366

6080.0000

6080

0.0502

0.050

Max. permissible pressure, P (Pprime) (psig)

¢

Longitudinal tensile stress in shell, S (Sprime) (psi) Req. half-pipe thk., T (in.)

40

¢

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Parameters

CodeCalc

ASME

Min. fillet weld size, Fillet (in.)

0.1180

0.12

Large Opening Checks Shell with a large nozzle (CodeCalc Job: Checks.cc2/SENIOR GB TEST): Tested against hand calculations performed by a client. Parameters

CodeCalc

Hand Calcs.

Longitudinal hub stress, SH* (psi)

19520

19494

Radial flange stress, SR* (psi)

1036

1032

Tangential flange stress, ST* (psi)

10945

10960

Parameters

CodeCalc

Hand Calcs.

Longitudinal hub stress, Shs (psi)

13314.04

13161

Radial stress, Srs (psi)

603.63

610

Tangential stress, Sts (psi)

5578.62

5564

Parameters

CodeCalc

Hand Calcs.

Longitudinal hub stress, Sho (psi)

16997.471

16960

Radial stress, Sro (psi)

902.257

898

Tangential stress, Sto (psi)

9750.84

9759

Stresses at the head-shell junction,

Stresses at the opening head junction,

PV Elite and CodeCalc Verification and Quality Assurance Manual

41

Software Verification

Rectangular Vessel Checks ASME APP. 13, 13-17(b) (CodeCalc job: Rctexmpl.cc2/EXAMPLE A2): A rectangular vessel with two long sides having different thickness (sketch A2), designed for internal pressure.

Membrane

Bending

Parameters

CodeCalc

ASME

Short side plate, (psi)

1242.00

1242

Long side plate, t2 (psi)

488.39

488

Long side plate, t22 (psi)

100.81

101

Short side plate, @ Q (psi)

±2560.62

±2571

Short side plate, @ Q1 (psi)

±15775.12

±15778

Long side plate, @ M (psi)

±3679.71

±3683

Long side plate, @ Q (psi)

±250.06

±250

Long side plate, @ M1 (psi)

±9556.91

±9572

Long side plate, @ Q1 (psi)

±6162.16

±6153

ASME APP. 13, 13-17(c) (CodeCalc job Rctexmpl.cc2/EXAMPLE A3): A rectangular vessel with uniform wall thickness and corners bend to a radius (sketch A3) designed for internal pressure.

Membrane

Bending

42

Parameters*

CodeCalc

ASME

Short side plate, @ C (psi)

450.00

450

Long side plate, @ A (psi)

300.00

300

Corner section, (psi)

485.41

485

Moment at mid pt of long side, Ma (in.-lb)

-2812.6814

-2820

Short side plate, Inner @ C (psi)

10123.91

10084

Short side plate, Outer @ C (psi)

-10123.91

-10084

Short side plate, Inner @ D (psi)

5623.91

-5583*

Short side plate, Outer @ D (psi)

-5623.91

5583*

Long side plate, Inner @ A (psi)

-16876.09

-16927

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Parameters*

CodeCalc

ASME

Long side plate, Outer @ A (psi)

16876.09

16927

Long side plate, Inner @ B (psi)

1123.91

1080

Long side plate, Outer @ B (psi)

-1123.91

-1080

Corner section, Inner (psi)

12248.52

12209

Corner section, Outer (psi)

-12248.52

-12209

As of this printing, ASME is in error about the stress state at point D. The stress at the point D on the short side is as per ASME Section VIII Div. 1 Appendix 13-7 Equation 29.

With, MA = -2812.68 in-lb P = 15 psi I1 = 0.0833 in4 L1 = 10 in. L2 = 20 in. R = 10 in. For the inner side, c=ci=0.5 Which gives, (Sb)Di = 5623.91 psi, while ASME has a stress value of -5583 psi. ASME Appendix 13, 13-17(g) (CodeCalc job: Extra_QA.cc2/ASME EXAMPLE 13): A vessel of obround cross section, with an I-section reinforcement member welded on, Sketch B2. Taking the pressure P = 29.9 psi. to get the ASME stress values. Parameters

CodeCalc

ASME

Combined MOI, I11 (in. )

6.8592

6.859

Short side plate, @ C (psi)

978.19

978.32

Long side plate, @ A (psi)

489.09

489.16

Short side plate, Outer @ C (psi)

-15647.72

-15641.75

Long side plate, Outer @ A (psi)

16935.70

16928.78

4

Membrane

Bending

PV Elite and CodeCalc Verification and Quality Assurance Manual

43

Software Verification

Total

Parameters

CodeCalc

ASME

Short side plate, Outer @ C (psi)

-14669.54

-14662.96

Long side plate, Outer @ A (psi)

17424.79

17417.946

ASME Appendix 13, 13-17(i) (CodeCalc job: Rctexmpl.cc2/EXAMPLE C1): A vessel of circular cross section, with a single diametral staying plate, Sketch C1. These stresses are maximum stresses occurring at the shell-plate junction.

Membrane

Bending

Total

44

Parameters

CodeCalc

ASME

Shell section (psi)

800.00

800

Diametral plate (psi)

2.10

2.1

Shell section, Inner (psi)

8884.12

8856

Diametral plate, Inner (psi)

25140.69

25020

Shell section, Inner (psi)

9684.12

9656

Diametral plate, Inner (psi)

25142.79

25022

PV Elite and CodeCalc Verification and Quality Assurance Manual

SECTION 5

PV Elite Sample Benchmark Problem Sets In This Section Problem 1 - Natural Frequency Calculation ................................... 45 Problem 2 - Example of Stiffening Ring Calculation ...................... 49 Problem 3 - Nozzle Reinforcement, Weld Strength, Weld Size .... 52 Problem 4 - Vessel under Internal and External Pressure on Legs ....................................................................................................... 64 Problem 5 - Vertical Vessel with Wind and Seismic Loads ........... 74 Problem 6 - Comparison against CAESAR II ................................ 83 Problem 7 - ASME Section VIII Division 2 Sample Comparisons . 86 Problem 8 - EN-13445 Nozzle Reinforcement .............................. 93

Problem 1 - Natural Frequency Calculation The purpose of this problem is to ensure that PV Elite is computing the fundamental frequency of a vertical tower correctly. This problem is a comparison against the sample presented in Henry Bednar’s Pressure Vessel Design Handbook, 2nd Edition (Page 126). The result for this problem should be approximately 1.15 sec/cycle or 0.9 hertz.

PV Elite and CodeCalc Verification and Quality Assurance Manual

45

Software Verification PV Elite® Vessel Analysis Program: Input Data Natural Frequency Comparison to Bednar p126 Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Perform a Corroded Hydrotest Is this a Heat Exchanger User Defined Hydro. Press (Used if > 0) User defined MAWP Load Load Load Load Load Load Load Load Load Load Load Load

Case Case Case Case Case Case Case Case Case Case Case Case

1 2 3 4 5 6 7 8 9 10 11 12

100.00 psig 200 F UG99-b Vertical 0.0000 in. 0.0000 in. - 1994 F Welded None RT 1 0.0 Y N N N N N 0.0000 psig 0.0000 psig

NP+EW+WI+BW NP+EW+EQ+BS NP+OW+WI+BW NP+OW+EQ+BS NP+HW+HI NP+HW+HE IP+OW+WI+BW IP+OW+EQ+BS EP+OW+WI+BW EP+OW+EQ+BS HP+HW+HI HP+HW+HE

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

ASCE-7 93 [V] 0.0000 mile/hr C: Open Terrain 1.0 0.0000 ft. 0.0 Vs. Elev. N (Ope) 0.0000 (Empty) 0.0000 (Filled) 0.0000

Seismic Design Code Seismic Zone Importance Factor Soil Type Horizontal Force Factor Percent Seismic for Hydrotest Design Nozzle for M.A.W.P. + Static Head Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9 Material Database Year

ASCE-7 88 0.0000 1.0000 S1 2.0000 0.0000 Y N N 1997

Configuration Directives: Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use Code Case 2286 Use the MAWP to compute the MDMT Using Metric Material Databases, ASME II D

No No No No No No No

Complete Listing of Vessel Elements and Details: Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Skirt Inside Diameter Diameter of Skirt at Base Skirt Thickness Internal Corrosion Allowance Design Temperature Internal Pressure Design Temperature External Pressure Effective Diameter Multiplier

46

10 20 Skirt Sup. 10.000 60.000 60.000 0.5000 0.0000 100 F 100 F 1.2

ft. in. in. in. in.

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness Yield Stress, Operating UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Product Form Efficiency, Longitudinal Seam Efficiency, Head-to-Skirt or Circ. Seam

SA516-70 17500. psi 17500. psi 26250. psi 0.0010000 lb./cu.in. 1.25 in. 38000. psi B CS-2 K02700 Plate 1.0 1.0

Element From Node 10 Detail Type Weight Detail ID F Dist. from "FROM" Node / Offset dist 5.0000 ft. Miscellaneous Weight 10000. lb. Offset from Element Centerline 0.0000in. -------------------------------------------------------Element From Node 20 Element To Node 40 Element Type Cylinder Description Distance "FROM" to "TO" 20.000 ft. Inside Diameter 60.000 in. Element Thickness 0.5000 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 100 F Design External Pressure 10.000 psig Design Temperature External Pressure 100 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 20 Detail Type Weight Detail ID E Dist. from "FROM" Node/Offset dist 10.000 ft. Miscellaneous Weight 15000. lb. Offset from Element Centerline 0.0000 in. -------------------------------------------------------Element From Node 40 Element To Node 50 Element Type Cylinder Description Distance "FROM" to "TO" 19.000 ft. Inside Diameter 60.000 in. Element Thickness 0.5000 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 100 F Design External Pressure 10.000 psig Design Temperature External Pressure 100 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 50 Detail Type Weight Detail ID C Dist. from "FROM" Node / Offset dist 9.5000 ft. Miscellaneous Weight 10000. lb. Offset from Element Centerline 0.0000 in. --------------------------------------------------------

PV Elite and CodeCalc Verification and Quality Assurance Manual

47

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Efficiency, Longitudinal Seam Efficiency, Circumferential Seam

60 80 Cylinder 16.000 96.000 0.7500 0.0000 0.0000 0.0000 10.000 100 F 10.000 100 F 1.2 SA-516 1.0 1.0

ft. in. in. in. in. in. psig psig 70

Element From Node 60 Detail Type Weight Detail ID B Dist. from "FROM" Node / Offset dist 8.0000 ft. Miscellaneous Weight 20000. lb. Offset from Element Centerline 0.0000 in. -------------------------------------------------------Element From Node 60 Element To Node 80 Element Type Cylinder Description Distance "FROM" to "TO" 16.000 ft. Inside Diameter 96.000 in. Element Thickness 0.7500 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 100 F Design External Pressure 10.000 psig Design Temperature External Pressure 100 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 60 Detail Type Weight Detail ID B Dist. from "FROM" Node / Offset dist 8.0000 ft. Miscellaneous Weight 20000. lb. Offset from Element Centerline 0.0000 in. -------------------------------------------------------Element From Node 80 Element To Node 90 Element Type Cylinder Description Distance "FROM" to "TO" 16.000 ft. Inside Diameter 96.000 in. Element Thickness 0.7500 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 100 F Design External Pressure 10.000 psig Design Temperature External Pressure 100 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 1.0 Efficiency,. Circumferential Seam 1.0 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Miscellaneous Weight Offset from Element Centerline

80 Weight A 8.0000 ft. 20000. lb. 0.0000 in.

PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Natural Frequency for the Operating Case (No Liquid), Freese Method Natural Frequency Calculation

48

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification | | Element | Centroid | Elem. End | Elem. Ang. | Element From| To | Total Wgt. | Deflection | Deflection | Rotation | Empty Wgt. | | lbm | in. | in. | | lbm ------------------------------------------------------------------------10 | 20 | 10011.4 | 0.077412 | 0.30044 | 0.0048560 | 10011.4 20 | 40 | 15022.8 | 1.13129 | 2.39547 | 0.012092 | 15022.8 40 | 50 | 10021.7 | 3.91854 | 5.68701 | 0.016406 | 10021.7 50 | 60 | 10021.7 | 7.63959 | 9.72088 | 0.018672 | 10021.7 60 | 80 | 20043.8 | 11.5172 | 13.3188 | 0.018782 | 20043.8 80 | 90 | 20043.8 | 15.1227 | 16.9273 | 0.018798 | 20043.8 The Natural Frequency for the Vessel (Empty.) is 0.90323 Hz. Natural Frequency for the Operating Case, Freese Method Natural Frequency Calculation | From| | 10 | 20 | 40 | 50 | 60 | 80 |

| Element To | Total Wgt. | lbm 20 | 10011.4 40 | 15022.8 50 | 10021.7 60 | 10021.7 80 | 20043.8 90 | 20043.8

| Centroid | Elem. End | Elem. Ang. | Deflection | Deflection | Rotation | in. | in. | | 0.077412 | 0.30044 | 0.0048560 | 1.13129 | 2.39547 | 0.012092 | 3.91854 | 5.68701 | 0.016406 | 7.63959 | 9.72088 | 0.018672 | 11.5172 | 13.3188 | 0.018782 | 15.1227 | 16.9273 | 0.018798

| | | | | | | | |

Element Emtpy Wgt. lbm 10011.4 15022.8 10021.7 10021.7 20043.8 20043.8

The Natural Frequency for the Vessel (Ope...) is 0.90323 Hz. Natural Frequency for the Filled Case, Freese Method The Natural Frequency for the Vessel (Filled) is 0.48376 Hz. PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014.

Problem 2 - Example of Stiffening Ring Calculation This sample problem was taken from the ASME Section VIII Division 1 pressure vessel code page 531-532 A-98 addenda. This stiffening ring is a channel welded to the outside of a 169-inch OD vessel. The test here is to compute the required moment of inertia of the ring. The 4 ASME code calculated value for I’s (the required moment of inertia) 15.61 in . PV Elite obtains 4 an almost identical result of 16.2 in . The difference is due to the fact that PV Elite computes the strain factor A to more significant figures than the code example.

PV Elite and CodeCalc Verification and Quality Assurance Manual

49

Software Verification PV Elite® Vessel Analysis Program: Input Data Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Perform a Corroded Hydrotest Is this a Heat Exchanger User Defined Hydro. Press. (Used if > 0) User Defined MAWP User Defined MAPnc

0.0000 psig 0 F Not Specified Horizontal 0.0000 in. 0.0000 in. -20 F Welded None RT 1 0.0 Y N N N N Y N N 0.0000 psig 0.0000 psig 0.0000 psig

Load Load Load Load Load Load Load Load Load Load Load Load Load Load Load Load Load Load Load

NP+EW+WI+FW+BW NP+EW+EE+FS+BS NP+OW+WI+FW+BW NP+OW+EQ+FS+BS NP+HW+HI NP+HW+HE IP+OW+WI+FW+BW IP+OW+EQ+FS+BS EP+OW+WI+FW+BW EP+OW+EQ+FS+BS HP+HW+HI HP+HW+HE IP+WE+EW IP+WF+CW IP+VO+OW IP+VE+OW IP+VF+CW FS+BS+EP+OW FS+BS+EP+OW

Case Case Case Case Case Case Case Case Case Case Case Case Case Case Case Case Case Case Case

1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Type of Surface Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

Vs. Elev. (Ope) (Empty) (Filled)

ASCE-7 93 [V] 70.000 mile/hr C: Open Terrain 1.0 Moderately Smooth 0.0000 in. 33.0 N 0.0100 0.0000 0.0000

Seismic Design Code UBC Seismic Zone (1=1,2=2a,3=2b,4=3,5=4) UBC Importance Factor UBC Soil Type UBC Horizontal Force Factor UBC Percent Seismic for Hydrotest

UBC 94 0.000 1.000 S1 3.000 0.000

Design Nozzle for Des. Press. + St. Head Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9

Y N Y N

Material Database Year Configuration Directives Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use the MAWP to compute the MDMT

Current w/Addenda or Code Year N Y Y Y Y

Complete Listing of Vessel Elements and Details

50

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Element Outside Diameter Element Thickness Internal Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness Yield Stress, Operating UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Product Form Efficiency, Longitudinal Seam Efficiency, Circumferential Seam

10 20 Cylinder

Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Stiffening Ring Moment of Inertia Distance from Shell Surface to Center Stiffening Ring Cross Sectional Area Material Name Stiffening Ring Section Name Height of Section Ring Using Custom Stiffener Section

10 Ring Ring:[1 of 1] 40.000 in. 13.100 in**4 3.0000 in. 2.4000 in² SA-516 70 C6X8.2 6.000 in. No

80.000 in. 169.00 in. 0.3125 in. 0.0000 in. 15.000 psig 700 F 15.000 psig 700 F 1.2 SA-285 C 15700. psi 14300. psi 20410. psi 0.2800 lbm/in3 1.2500 in. 21500. psi A CS-2 K02801 Plate 1.0 1.0

PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 External Pressure Calculation Results ASME Code, Section VIII, Division 1, 2011a Cylindrical Shell From 10 To Ring:[1 of 1] Ext. Chart: CS-2 at 700 F Elastic Modulus from Chart: CS-2 at 700F: 0.245E+08 psi Results for Maximum Allowable Pressure (MAEP): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.312 | 169.00 | 40.00 | 540.80 | 0.2367 | 0.0004801 | 5880.68 | EMAP = (4*B)/(3*(D/t)) = (4* 5880.6768)/(3* 540.8000) = 14.4987 psig Results for Required Thickness (TCA): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.317 | 169.00 | 40.00 | 533.48 | 0.2367 | 0.0004900 | 6001.98 | EMAP = (4*B)/(3*(D/t)) = (4* 6001.9790)/(3* 533.4799) = 15.0008 psig Results for Maximum Stiffened Length (SLEN): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.312 | 169.00 | 38.76 | 540.80 | 0.2294 | 0.0004966 | 6083.58 | EMAP = (4*B)/(3*(D/t)) = (4* 6083.5762)/(3* 540.8000) = 14.9990 psig Cylindrical Shell From Ring[1 of 1] to the end: Ext. Chart: CS-2 at 700 F Elastic Modulus from Chart: CS-2 at 700 F: 0.245E+08 psi Results for Maximum Allowable Pressure (EMAP): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.312 | 169.00 | 40.00 | 540.80 | 0.2367 | 0.0004801 | 5880.68 | EMAP = (4*B)/(3*(D/t)) = (4* 5880.6768)/(3* 540.8000) = 14.4987 psig Results for Required Thickness (TCA): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.317 | 169.00 | 40.00 | 533.48 | 0.2367 | 0.0004900 | 6001.98 | EMAP = (4*B)/(3*(D/t)) = (4* 6001.9790)/(3* 533.4799) = 15.0008 psig Results for Maximum Stiffened Length (SLEN): | TCA | OD | SLEN | D/t | L/D | Factor A | B | | 0.312 | 169.00 | 38.76 | 540.80 | 0.2294 | 0.0004966 | 6083.58 | EMAP = (4*B)/(3*(D/t)) = (4* 6083.5762)/(3* 540.8000) = 14.9990 psig Stiffening Ring Calculations for: Ring:[1 of 1], C6X8.2, SA-516 70

PV Elite and CodeCalc Verification and Quality Assurance Manual

51

Software Verification Effective Length of Shell Area (in2) Shell: 2.498 Ring : 2.400 Total: 4.898 Centroid of Ring plus Shell Inertia Shell: 0.020 Ring : 13.100 Total: 13.120 Available Moment of Inertia,

Distance (in.) 0.1562 3.3125 = Distance 1.5465 -1.6097 Ring plus Shell

Required Stress in Ring plus Shell Required Strain in Ring plus Shell

BREQ AREQ

7.99 in. Area*Dist 0.390 7.950 8.340 1.703 in. A*Dist2 5.975 6.219 12.194 25.314 in**4 5103.88 psi 0.0004150

Required Moment of Inertia, Ring plus Shell = ( OD² * SLEN * (TCA+ARING/SLEN) * AREQ )/ 10.9 = (168.0000²*40.0000*(0.3125+2.4000/40.0000)*0.0004150)/10.9 = 16.2025 in**4 External Pressure Calculations | | Section | Outside | Corroded | Factor | Factor | From| To | Length | Diameter | Thickness | A | B | | | in. | in. | in. | | psi | -------------------------------------------------------------------10 |Ring| 40.0000 | 169.000 | 0.31250 | 0.00048006 | 5880.68 | Ring| 20 | 40.0000 | 169.000 | 0.31250 | 0.00048006 | 5880.68 | External Pressure Calculations | | External | External | External | External | From| To | Actual T. | Required T.| Des. Press.| M.A.W.P. | | | in. | in. | psig | psig | -----------------------------------------------------------10 |Ring| 0.31250 > 14.4987 | Ring| 20 | 0.31250 > 14.4987 | Minimum 14.499 External Pressure Calculations | | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia | From| To | Bet. Stiff.| Bet. Stiff.| Required | Available | | | in. | in. | in**4 | in**4 | -----------------------------------------------------------------10 |Ring| 40.0000 >>> 38.7605 | No Calc | No Calc | Ring| 20 | 40.0000 >>> 38.7605 | 16.2025 | 25.3141 | One or more Elements or Rings Failed Code requirements for External Pressure with the given thickness! PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014

Problem 3 - Nozzle Reinforcement, Weld Strength, Weld Size The next sample problem was adapted from the ASME code Appendix L. This example problem tests PV Elite nozzle calculations in accordance with paragraph UG-37. This sample problem compares with ASME’s hillside nozzle example 7 Addenda 98. PV Elite automatically performs the nozzle calculation in both the hoop direction and the longitudinal direction. The results for areas required and available are in excellent agreement. This particular file applchk.pvi contains all of the ASME nozzle reinforcement calculation examples.

52

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

PV Elite and CodeCalc Verification and Quality Assurance Manual

53

Software Verification PV Elite® Vessel Analysis Program: Input Data Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Perform a Corroded Hydrotest Is this a Heat Exchanger User Defined Hydro. Press. (Used if > 0) User defined MAWP User defined MAPnc

100.00 psig 225 F UG99-b Horizontal 0.0000 in. 0.0000 in. -20 F Welded None RT 1 0.0 Y N N N N

Load Load Load Load Load Load Load Load Load Load Load Load

NP+EW+WI+BW NP+EW+EQ+BS NP+OW+WI+BW NP+OW+EQ+BS NP+HW+HI NP+HW+HE IP+OW+WI+BW IP+OW+EQ+BS EP+OW+WI+BW EP+OW+EQ+BS HP+HW+HI HP+HW+HE

Case Case Case Case Case Case Case Case Case Case Case Case

N Y 0.0000 psig 0.0000 psig 0.0000 psig

1 2 3 4 5 6 7 8 9 10 11 12

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Type of Surface Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

[V]

Vs Elev. (Ope) (Empty) (Filled)

ASCE-7 93 70.000 mile/hr C: Open Terrain 1.0 Moderately Smooth 0.0000 ft. 33.0 N 0.0000 0.0000 0.0000

Seismic Design Code UBC Seismic Zone (1=1,2=2a,3=2b,4=3,5=4) UBC Importance Factor UBC Soil Type UBC Horizontal Force Factor UBC Percent Seismic for Hydrotest

UBC 94 0.000 1.000 S1 2.000 0.000

Design Nozzle for Des. Press. + St. Head Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9 Material Database Year

Y Y N 2009

Configuration Directives: Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use Code Case 2286 Use the MAWP to compute the MDMT Using Metric Material Databases, ASME II D

No No No No No No No

Complete Listing of Vessel Elements and Details:

54

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Product Form Efficiency, Longitudinal Seam Efficiency, Circumferential Seam

10 20 Cylinder 5.0000 ft. 60.000 in. 0.7500 in. 0.0000 in. 0.0000 in. 0.0000 in. 250.00 psig 704 F 0.0000 psig 0 F 1.2 SA515-60 15000. psi 14300. psi 22500. psi 0.2830 lb./cu.in. 1.2500 in. B CS-2 K02401 Plate 1.0 1.0

Element From Node 10 Detail Type Nozzle Detail ID APP EX-2 Dist. from "FROM" Node / Offset dist 1.0000 ft. Nozzle Diameter 11.75 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Material Name SA516-70 ----------------------------------------------------------------Element From Node 20 Element To Node 30 Element Type Elliptical Description Distance "FROM" to "TO" 0.2500 ft. Inside Diameter 23.625 in. Element Thickness 0.1880 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 150.00 psig Design Temperature Internal Pressure 400 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 17500. psi Allowable Stress, Hydrotest 26250. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K02700 Product Form Plate Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Elliptical Head Factor 2.0 Element From Node 20 Detail Type Nozzle Detail ID APP EX6 Dist. from "FROM" Node / Offset dist 0.0000 in. Nozzle Diameter 8.0 in. Nozzle Schedule 20 Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-B ----------------------------------------------------------------

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55

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Efficiency, Longitudinal Seam Efficiency, Circumferential Seam

30 40 Cylinder 5.0000 ft. 30.000 in. 1.5000 in. 0.0000 in. 0.0000 in. 0.0000 in. 1000.0 psig 150 F 0.0000 psig 0 F 1.2 SA516-55 13800. psi 13800. psi 20700. psi 0.2830 lb./cu.in. 1.2500 in. C CS-2 K01800 1.0 1.0

Element From Node 30 Detail Type Nozzle Detail ID APP EX-7 Dist. from "FROM" Node / Offset dist 2.0000 ft. Nozzle Diameter 4.0 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA516-60 --------------------------------------------------------------Element From Node 40 Element To Node 50 Element Type Cylinder Description Distance "FROM" to "TO" 5.0000 ft. Inside Diameter 30.000 in. Element Thickness 0.3750 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 250.00 psig Design Temperature Internal Pressure 150 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA516-55 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 40 Detail Type Nozzle Detail ID APP L EX-1 Dist. from "FROM" Node / Offset dist 3.0000 ft. Nozzle Diameter 4.0 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 180.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-B ---------------------------------------------------------------

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Product Form Efficiency, Longitudinal Seam Efficiency, Circumferential Seam Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Material Name

50 60 Cylinder 5.0000 ft. 60.000 in. 0.7500 in. 0.0000 in. 0.0000 in. 0.0000 in. 250.00 psig 700 F 0.0000 psig 0 F 1.2 SA515-70 17500. psi 14300. psi 26250. psi 0.2830 lb./cu.in. 1.2500 in. A CS-2 K03101 Plate 1.0 1.0 50 Nozzle APP EX-3 2.0000 ft. 11.75 in. None 150 0.0 N 0.0000 lb. GR 1.1 SA516-70

Element From Node 50 Detail Type Nozzle Detail ID APP EX-3B Dist. from "FROM" Node / Offset dist 2.0000 ft. Nozzle Diameter 11.75 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 180.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Material Name SA516-70 ---------------------------------------------------------------Element From Node 60 Element To Node 70 Element Type Cylinder Description Distance "FROM" to "TO" 5.0000 ft. Inside Diameter 96.000 in. Element Thickness 2.0000 in. Internal Corrosion Allowance 0.06250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 425.00 psig Design Temperature Internal Pressure 800 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 11400. psi Allowable Stress, Hydrotest 26250. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K02700 Product Form Plate Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0

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Software Verification Element From Node 60 Detail Type Nozzle Detail ID APP EX-4 Dist. from "FROM" Node / Offset dist 2.0000 ft. Nozzle Diameter 16.0 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Material Name SA516-70 ----------------------------------------------------------------Element From Node 70 Element To Node 80 Element Type Cylinder Description Distance "FROM" to "TO" 5.0000 ft. Inside Diameter 83.000 in. Element Thickness 2.0000 in. Internal Corrosion Allowance 0.2500 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.2500 in. Design Internal Pressure 500.00 psig Design Temperature Internal Pressure 400 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA515-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 13700. psi Allowable Stress, Hydrotest 26250. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation A External Pressure Chart Name CS-2 UNS Number K03101 Product Form Plate Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 70 Detail Type Nozzle Detail ID APP EX-5 Dist. from "FROM" Node / Offset dist 2.0000 ft. Nozzle Diameter 14.5 in. Nozzle Schedule None Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA515-60 -----------------------------------------------------------------Element From Node 80 Element To Node 90 Element Type Cylinder Description Distance "FROM" to "TO" 5.0000 ft. Inside Diameter 42.000 in. Element Thickness 0.5630 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.2500 in. Design Internal Pressure 300.00 psig Design Temperature Internal Pressure 650 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA515-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node 80 Detail Type Nozzle Detail ID APP 8 Dist. from "FROM" Node / Offset dist 2.0000 ft. Nozzle Diameter 10.0 in. Nozzle Schedule 80 Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Material Name SA106-B ----------------------------------------------------------------

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Software Verification Element From Node 90 Element To Node 95 Element Type Flat Description Distance "FROM" to "TO" 0.04692 ft. Inside Diameter 42.000 in. Element Thickness 0.5630 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.2500 in. Design Internal Pressure 5.0000 psig Design Temperature Internal Pressure 650 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA515-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Flat Head Attachment Factor 0.30000001 Small diameter if Non-Circular 0.0000 in. -----------------------------------------------------------------Element From Node 95 Element To Node 100 Element Type Cylinder Description Distance "FROM" to "TO" 15.375 ft. Inside Diameter 53.270 in. Element Thickness 0.9900 in. Internal Corrosion Allowance 0.3125 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.2500 in. Design Internal Pressure 100.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 100.00 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 17500. psi Allowable Stress, Hydrotest 26250. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K02700 Product Form Plate Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Matl

95 Nozzle DUPPS 2.0000 ft. 24.0 in. None 150 0.0 N 0.0000 lb. GR 1.1 SA106-B

PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 INPUT VALUES, Nozzle Description: APP EX-7

From: 30

Pressure for Reinforcement Calculations Temperature for Internal Pressure Maximum Allowable Pressure New & Cold

P Temp

1000.000 psig 150 F 10.48 psig

Shell Material Shell Allowable Stress at Temperature Shell Allowable Stress at Ambient

S Sa

SA516-55 13800.00 psi 13800.00 psi

Inside Diameter of Cylindrical Shell Shell Finished (Minimum) Thickness Shell Internal Corrosion Allowance Shell External Corrosion Allowance

D t c co

30.0000 in. 1.5000 in. 0.0000 in. 0.0000 in.

Distance from Cylinder/Cone Centerline

L1

12.0000 in.

Distance from Bottom/Left Tangent

7.2500 ft.

User Entered Minimum Design Metal Temperature

-20.00 F

Type of Element Connected to the Shell: Nozzle

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Software Verification Material Material UNS Number Material Specification/Type Allowable Stress at Temperature Allowable Stress at Ambient

Sn Sna

SA516-60 K02100 Plate 15000.00 psi 15000.00 psi

Diameter Basis (for tr calc only) Layout Angle Diameter

ID 0.00 deg 4.0000 in.

Corrosion Allowance Joint Efficiency of Shell Seam at Nozzle Joint Efficiency of Nozzle Neck

can E1 En

0.0000 in. 1.00 1.00

Outside Projection Weld leg size between Nozzle and Pad/Shell Groove weld depth between Nozzle and Vessel Inside Projection Weld leg size, Inside Element ot Shell ASME Code Weld Type per UW-16

ho Wo Wgnv h Wi

4.0000 0.5000 1.5000 0.0000 0.0000 None

Class of attached Flange Grade of attached Flange

in. in. in. in. in.

150 GR 1.1

The Pressure Design option was Design Pressure + static head. Nozzle Sketch (may not represent actual weld type/configuration) Insert Nozzle No Pad, no Inside projection Note: Checking Nozzle 90 degrees to the Longitudinal axis. Reinforcement CALCULATION, Description: APP EX-7 ASME Code, Section VIII, Division 1, 1998, A-98 UG-37 to UG-45 Actual Inside Diameter Used in Calculation Actual Thickness Used in Calculation

4.000 in. 0.500 in.

Nozzle input data check completed without errors. Reqd thk per UG-37(a) of Cylindrical Shell, TR [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (1000.00*15.0000)/(13800*1.00-0.6*1000.00) = 1.1364 in. Reqd thk per UG-37(a) of Cylindrical Shell, TR [Mapnc] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (10.48*15.0000)/(13800*1.00-0.6*10.48) = 0.0114 in. Reqd thk per UG-37(a) of Nozzle Wall, TRN [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (1000.00*2.00)/(15000*1.00-0.6*1000.00) = 0.1389 in. Reqd thk per UG-37(a) of Nozzle Wall, TRN [Mapnc] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (10.48*2.00)/(15000*1.00-0.6*10.48) = 0.0014 in. UG-40, Limits of Reinforcement: [Internal Pressure] Parallel to Vessel Wall (Diameter Limit) D1 Parallel to Vessel Wall, opening length d Normal to Vessel Wall (Thickness Limit), no pad Tlnp

13.0950 in. 6.5473 in. 1.2500 in.

UG-40, Limits of Reinforcement: [Mapnc] Parallel to Vessel Wall (Diameter Limit) Parallel to Vessel Wall, opening length Normal to Vessel Wall (Thickness Limit), no pad

13.0950 in. 6.5473 in. 1.2500 in.

D1 d Tlnp

Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 | Design | External Area Required Ar | 3.720 | NA Area in Shell A1 | 6.101 | NA Area in Nozzle Wall A2 | 1.135 | NA Area in Inward Nozzle A3 | 0.000 | NA Area in Welds A41+A42+A43| 0.250 | NA Area in Element A5 | 0.000 | NA TOTAL AREA AVAILABLE Atot | 7.486 | NA

| | | | | | | |

Mapnc | 0.037 sq.in. | 9.784 sq.in. | 1.567 sq.in. | 0.000 sq.in. | 0.250 sq.in. | 0.000 sq.in. | 11.601 sq.in.|

The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations

37.66 Degs.

The area available without a pad is Sufficient. Area Required [A]:

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification = (d * tr*F + 2 * tn * tr*F * (1-fr1)) UG-37(c) = (6.5473 * 1.1364*0.5 +2 * 0.5000 * 1.1364*0.5*(1-1.00)) = 3.720 sq.in. Reinforcement Areas per Figure UG-37.1 Area Available in Shell [A1]: = d(E1*t - F*tr) - 2 * tn( E1*t - F*tr) * (1 - fr1) = 6.547 (1.00 * 1.5000 - 0.5 * 1.136) - 2 * 0.500(1.00 * 1.5000 - 0.5 * 1.1364) * (1 - 1.000) = 6.101 sq.in. Area Available in Nozzle Projecting Outward [A2]: = (2 * tlnp) * (tn - trn) * fr2/sin(alpha3) = (2 * 1.250) * (0.5000 - 0.1389) * 1.0000/sin(52.7) = 1.135 sq.in. See Appendix L, L-7.7.7(b) for more information. Area Available in Inward Weld + Outward Weld [A41 + A43]: = Wo^(2) * fr2 + (Wi-can/0.707)^(2) * fr2 = 0.5000^(2) * 1.0000 + (0.0000)^(2) * 1.0000 = 0.250 sq.in. Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations: MDMT of the Nozzle Neck to Flange Weld, Curve: C ---------------------------------------------------------------------Govrn. thk, tg = 0.500 , tr = 0.139 , c = 0.0000 in. , E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.278 , Temp. Reduction = 110 F Min Metal Temp. w/o impact per UCS-66 Min Metal Temp. at Required thickness (UCS 66.1)

-36 F -146 F

MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), Curve: C ---------------------------------------------------------------------Govrn. thk, tg = 0.500 , tr = 0.139 , c = 0.0000 in. , E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.278 , Temp. Reduction = 110 F Min Metal Temp. w/o impact per UCS-66 -36 F Min Metal Temp. at Required thickness (UCS 66.1) -146 F Governing MDMT of all the sub-joints of this Junction:

-146 F

ANSI Flange MDMT including Temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) Flange MDMT with Temp reduction per UCS-66(b)(1)(b) Flange MDMT with Temp reduction per UCS-66(b)(1)(c)

-20 F -20 F -155 F

Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is: Design Pressure/Ambient Rating = 1000.00/285.00 = 3.509 Note: Use the minimum value from (b)(1)(b) and (b)(1)(c) above as the calculated nozzle flange MDMT. Weld Size Calculations, Description: APP EX-7 Intermediate Calc. for nozzle/shell Welds Results Per UW-16.1: | Required Thickness Nozzle Weld | 0.2500 = Min per Code

| |

Tmin

0.5000 in.

Actual Thickness 0.3535 = 0.7 * Wo in.

Weld Strength and Weld Loads per UG-41.1, Sketch (a) or (b) Weld Load [W]: = (A-A1+2*tn*fr1*(E1*t-tr))*Sv = (3.7201 - 6.1009 + 2 * 0.5000 * 1.0000 *(1.00 * 1.5000 - 0.5682)) * 13800 = 0.00 lb. F is always set to 1.0 throughout the calculation. Weld Load [W1]: = (A2+A5+A4-(Wi-Can/.707)^(2)*fr2)*Sv = (1.1350 + 0.0000 + 0.2500 - 0.0000 * 1.00) * 13800 = 19112.62 lb. Weld Load [W2]: = (A2 + A3 + A4 + (2 * tn * t * fr1)) * Sv = (1.1350 + 0.0000 + 0.2500 + (1.5000)) * 13800 = 39812.62 lb. Weld Load [W3]: = (A2+A3+A4+A5+(2*tn*t*fr1))*S = (1.1350 + 0.0000 + 0.2500 + 0.0000 + (1.5000)) * 13800 = 39812.62 lb. Strength of Connection Elements for Failure Path Analysis Shear, Outward Nozzle Weld [Sonw]: = (pi/2) * Dlo * Wo * 0.49 * Snw = (3.1416/2.0) * 8.1841 * 0.5000 * 0.49 * 13800 = 43465. lb.

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Software Verification Shear, Nozzle Wall [Snw]: = (pi *(Dlr + Dlo)/4) * (Thk - Can) * 0.7 * Sn = (3.1416 * 3.6829) * (0.5000 - 0.0000) * 0.7 * 15000 = 60743. lb. Tension, Shell Groove Weld [Tngw]: = (pi/2) * Dlo * (Wgnvi-Cas) * 0.74 * Sng = (3.1416/2.0) * 8.1841 * (1.5000 - 0.0000) * 0.74 * 15000 = 214045. lb. Strength of Failure Paths: PATH11 = (SONW + SNW) = (43464 + 60742) = 104207 lb. PATH22 = (Sonw + Tpgw + Tngw + Sinw) = (43464 + 0 + 214045 + 0) = 257509 lb. PATH33 = (Sonw + Tngw + Sinw) = (43464 + 214045 + 0) = 257509 lb. Summary of Path 1-1 = Path 2-2 = Path 3-3 =

Failure Path Calculations: 104207 lb., must exceed W = 0 lb. or W1 = 19112 lb. 257509 lb., must exceed W = 0 lb. or W2 = 39812 lb. 257509 lb., must exceed W = 0 lb. or W3 = 39812 lb.

Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 1301.887 psig The MAWP of this junction was limited by the parent Shell/Head. Checking Nozzle in plane parallel to the vessel axis. Reinforcement CALCULATION, Description: APP EX-7 ASME Code, Section VIII, Division 1, 1998, A-98 UG-37 to UG-45 Actual Inside Diameter Used in Calculation Actual Thickness Used in Calculation

4.000 in. 0.500 in.

Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (1000.00*15.0000)/(13800*1.00-0.6*1000.00) = 1.1364 in. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Mapnc] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (10.48*15.0000)/(13800*1.00-0.6*10.48) = 0.0114 in. Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (1000.00*2.00)/(15000*1.00-0.6*1000.00) = 0.1389 in. Reqd thk per UG-37(a)of Nozzle Wall, Trn [Mapnc] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (10.48*2.00)/(15000*1.00-0.6*10.48) = 0.0014 in. UG-40, Limits of Reinforcement : [Internal Pressure] Parallel to Vessel Wall (Diameter Limit) Dl Parallel to Vessel Wall Rn+tn+t Normal to Vessel Wall (Thickness Limit), no pad Tlnp

8.0000 in. 4.0000 in. 1.2500 in.

UG-40, Limits of Reinforcement : [Mapnc] Parallel to Vessel Wall (Diameter Limit) Parallel to Vessel Wall Normal to Vessel Wall (Thickness Limit), no pad

8.0000 in. 4.0000 in. 1.2500 in.

Dl Rn+tn+t Tlnp

Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 | Design | External Area Required Ar | 4.545 | NA Area in Shell A1 | 1.455 | NA Area in Nozzle Wall A2 | 0.903 | NA Area in Inward Nozzle A3 | 0.000 | NA Area in Welds A41+A42+A43 | .250 | NA Area in Element A5 | 0.000 | NA TOTAL AREA AVAILABLE Atot | 2.607 | NA

| | | | | | | |

Mapnc 0.046 sq.in. 5.954 sq.in. 1.247 sq.in. 0.000 sq.in. 0.250 sq.in. 0.000 sq.in. 7.451 sq.in.

The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations

90.00 Degs.

The area available without a pad is Insufficient. RECOMMENDATION: Add a Reinforcing Pad.

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Software Verification SELECTION OF POSSIBLE REINFORCING PADS: Based on the Estimated Diameter Limit:

Diameter 7.9375

Thickness 0.6875 in.

Area Required [A]: = (d * tr*F + 2 * tn * tr*F * (1-fr1)) UG-37(c) = (4.0000*1.1364*1.0+2*0.5000*1.1364*1.0*(1-1.00)) = 4.545 sq.in. Reinforcement Areas per Figure UG-37.1 Area Available in Shell [A1]: = d(E1*t - F*tr) - 2 * tn(E1*t - F*tr) * (1 - fr1) = 4.000 (1.00 * 1.5000 - 1.0 * 1.136) - 2 * 0.500(1.00 * 1.5000 - 1.0 * 1.1364) * (1 - 1.000) = 1.455 sq.in. Area Available in Nozzle Projecting Outward [A2]: = (2 * tlnp) * (tn - trn) * fr2 = (2 * 1.250) * (0.5000 - 0.1389) * 1.0000 = 0.903 sq.in. Area Available in Inward Weld + Outward Weld [A41 + A43]: = Wo^(2) * fr2 + (Wi-can/0.707)^(2) * fr2 = 0.5000^(2) * 1.0000 + (0.0000)^(2) * 1.0000 = 0.250 sq.in. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Wall Thickness for Internal/External pressures ta Wall Thickness per UG16(b), tr16b Wall Thickness, shell/head, internal pressure trb1 Wall Thickness tb1 = max(trb1, tr16b) Wall Thickness tb2 = max(trb2, tr16b) Wall Thickness per table UG-45 tb3

Press.] = 0.1389 = 0.0625 = 1.1364 = 1.1364 = 0.0625 = 0.2256

in. in. in. in. in. in.

Determine Nozzle Thickness candidate [tb]: = min[tb3, max(tb1,tb2)] = min[0.226 , max(1.136 , 0.063)] = 0.2256 in. Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max(ta, tb) = max(0.1389 , 0.2256) = 0.2256 in. Available Nozzle Neck Thickness = 0.5000 in. --> OK Weld Size Calculations, Description: APP EX-7 Intermediate Calc. for nozzle/shell Welds Results Per UW-16.1: Required Thickness Nozzle Weld 0.2500 = Min per Code

Tmin

0.5000

in.

Actual Thickness 0.3535 = 0.7 * Wo in.

Weld Strength and Weld Loads per UG-41.1, Sketch (a) or (b) Weld Load [W]: = (A-A1+2*tn*fr1*(E1*t-tr))*Sv = (4.5455 - 1.4545 + 2 * 0.5000 * 1.0000 *(1.00 * 1.5000 - 1.1364)) * 13800 = 47672.73 lb. F is always set to 1.0 throughout the calculation. Weld Load [W1]: = (A2+A5+A4-(Wi-Can/.707)^(2)*fr2)*Sv = (0.9028 + 0.0000 + 0.2500 - 0.0000 * 1.00) * 13800 = 15908.33 lb. Weld Load [W2]: = (A2 + A3 + A4 + (2 * tn * t * fr1)) * Sv = (0.9028 + 0.0000 + 0.2500 + (1.5000)) * 13800 = 36608.33 lb. Weld Load [W3]: = (A2+A3+A4+A5+(2*tn*t*fr1))*S = (0.9028 + 0.0000 + 0.2500 + 0.0000 + (1.5000)) * 13800 = 36608.33 lb. Strength of Connection Elements for Failure Path Analysis Shear, Outward Nozzle Weld [Sonw]: = (pi/2) * Dlo * Wo * 0.49 * Snw = (3.1416/2.0) * 5.0000 * 0.5000 * 0.49 * 13800 = 26554. lb. Shear, Nozzle Wall [Snw]: = (pi *(Dlr + Dlo)/4) * (Thk - Can) * 0.7 * Sn = (3.1416 * 2.2500) * (0.5000 - 0.0000) * 0.7 * 15000 = 37110. lb.

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Software Verification Tension, Shell Groove Weld [Tngw]: = (pi/2) * Dlo * (Wgnvi-Cas) * 0.74 * Sng = (3.1416/2.0) * 5.0000 * (1.5000 - 0.0000) * 0.74 * 15000 = 130769. lb. Strength of Failure Paths: PATH11 = (SONW + SNW) PATH22 = (Sonw + Tpgw = (26554 + PATH33 = (Sonw + Tngw = (26554 + Summary of Path 1-1 = Path 2-2 = Path 3-3 =

= (26554 + 37110) = 63664 lb. + Tngw + Sinw) 0 + 130768 + 0) = 157323 lb. + Sinw) 130768 + 0) = 157323 lb.

Failure Path Calculations: 63664 lb., must exceed W = 47672 lb. or W1 = 15908 lb. 157323 lb., must exceed W = 47672 lb. or W2 = 36608 lb. 157323 lb., must exceed W = 47672 lb. or W3 = 36608 lb.

Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 801.776 psig Approximate M.A.P.(NC) for given geometry

830.279

psig

The Drop for this Nozzle is : 5.1594 in. The Cut Length for this Nozzle is, Drop + Ho + H + T : 11.4842 in. Percent Elongation Calculations: Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro)

11.111 %

Please Check Requirements of UCS-79 as Elongation is > 5%. PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014

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Software Verification

Problem 4 - Vessel under Internal and External Pressure on Legs TM

This example, known as cmpwisd.pvi, is a comparison between another program (Compress ver. 4.4) and PV Elite. Several items are tested such as basic results for internal and external pressure, nozzle reinforcement, natural frequency and leg design are compared. The results all compare within acceptable limits.

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Software Verification PV Elite® Vessel Analysis Program: Input Data Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Perform a Corroded Hydrotest Is this a Heat Exchanger User Defined Hydro. Press. (Used if > 0) User defined MAWP User defined MAPnc

150.00 psig 275 F UG99-b Horizontal 0.0000 in. 0.0000 in. -20 F Welded None RT 1 0.0 Y N N N N

Load Load Load Load Load Load Load Load Load Load Load Load

NP+EW+WI+BW NP+EW+EQ+BS NP+OW+WI+BW NP+OW+EQ+BS NP+HW+HI NP+HW+HE IP+OW+WI+BW IP+OW+EQ+BS EP+OW+WI+BW EP+OW+EQ+BS HP+HW+HI HP+HW+HE

Case Case Case Case Case Case Case Case Case Case Case Case

N N 0.0000 psig 0.0000 psig 0.0000 psig

1 2 3 4 5 6 7 8 9 10 11 12

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Type of Surface Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

[V]

Vs Elev. (Ope) (Empty) (Filled)

ASCE-7 93 85.000 mile/hr C: Open Terrain 1.0 Moderately Smooth 2.5000 ft. 33.0 N 0.0000 0.0000 0.0000

Seismic Design Code Seismic Zone Importance Factor Soil Type Horizontal Force Factor Percent Seismic for Hydrotest

ASCE 7-88 0.000 1.000 S1 2.000 0.000

Design Nozzle for M.A.W.P. (maximum) Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9 Material Database Year

Y N N 1997

Configuration Directives: Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use Code Case 2286 Use the MAWP to compute the MDMT Using Metric Material Databases, ASME II D

No No No No No No No

Complete Listing of Vessel Elements and Details:

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Allowable Stress, Ambient Allowable Stress, Operating Allowable Stress, Hydrotest Material Density P Number Thickness UCS-66 Chart Curve Designation External Pressure Chart Name UNS Number Efficiency, Longitudinal Seam Efficiency, Circumferential Seam Elliptical Head Factor

10 20 Elliptical 0.1667 ft. 48.000 in. 0.4375 in. 0.1250 in. 0.0000 in. 0.0000 in. 150.00 psig 275 F 15.000 psig 300 F 1.178 SA516-60 15000. psi 15000. psi 22500. psi 0.2830 lb./cu.in. 1.2500 in. D CS-2 K02100 1.0 1.0 2.0

Element From Node Detail Type Detail ID Dist. from "FROM" Node/Offset dist Height/Length of Liquid Liquid Density

10 Liquid LIQUID BOTTOM -1.0000 ft. 1.1667 ft. 54.28 lb./cu.ft.

Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle (Used if > 0) Grade of Attached Flange Nozzle Matl

10 Nozzle N3 4"S/120 0.0000 in. 4.0000 in. 120 150 0.0 N 0.0000 lb. GR 1.1 SA106-B

Element From Node 10 Detail Type Leg Detail ID LEGS Dist. from "FROM" Node/Offset dist 0.1666 ft. Diameter at Leg Centerline 50.000 in. Leg Orientation 2 Number of Legs 4 Section Identifier W4X13 Length of Legs 3.1670 ft. ---------------------------------------------------------------Element From Node 20 Element To Node 30 Element Type Cylinder Description Distance "FROM" to "TO" 13.667 ft. Inside Diameter 48.000 in. Element Thickness 0.5000 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 150.00 psig Design Temperature Internal Pressure 275 F Design External Pressure 15.000 psig Design Temperature External Pressure 300 F Effective Diameter Multiplier 1.178 Material Name SA516-60 Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.8 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Height/Length of Liquid Liquid Density

20 Liquid LIQUID 0.0000 13.667 54.288

CYL ft. ft. lb./cu.ft.

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Software Verification Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Matl

20 Nozzle M-1(20"X-STG) 2.5000 ft. 20.0 in. XS 150 270.0 N 0.0000 lb. GR 1.1 SA106-B

Element From Node 20 Detail Type Nozzle Detail ID N6 3"S/160 Dist. from "FROM" Node / Offset dist 3.0000 ft. Nozzle Diameter 3.0 in. Nozzle Schedule 160 Nozzle Class 150 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-B --------------------------------------------------------------Element From Node 30 Element To Node 40 Element Type Elliptical Description Distance "FROM" to "TO" 0.1667 ft. Inside Diameter 48.000 in. Element Thickness 0.4375 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 150.00 psig Design Temperature Internal Pressure 275 F Design External Pressure 15.000 psig Design Temperature External Pressure 300 F Effective Diameter Multiplier 1.178 Material Name SA516-60 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 Elliptical Head Factor 2.0 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Height/Length of Liquid Liquid Density

30 Liquid LIQUID 0.0000 0.1667 54.288

Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Matl

30 Nozzle N1 8"S/80 0.0000 in. 8.0 in. 80 150 0.0 N 0.0000 lb. GR 1.1 SA106-B

Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Matl

30 Nozzle N2 6"S/80 15.000 in. 6.0 in. 80 150 0.0 N 0.0000 lb. GR 1.1 SA106-B

TOP ft. ft. lb./cu.ft.

PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Element Thickness, Pressure, Diameter, and Allowable Stress:

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification | | Int. Press | Nominal | Total Corr | Element | Allowable | From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)| | | psig | in. | in. | in. | psi | -----------------------------------------------------------------------10 | 20 | 155.655 | | 0.12500 | 48.0000 | 15000.0 | 20 | 30 | 155.215 | | 0.12500 | 48.0000 | 12750.0 | 30 | 40 | 150.063 | | 0.12500 | 48.0000 | 15000.0 | Element Required Thickness and MAWP: | | Design | M.A.W.P. | M.A.P. | Minimum | Required | From| To | Pressure | Corroded | New & Cold | Thickness | Thickness | | | psig | psig | psig | in. | in. | --------------------------------------------------------------------10 | 20 | 150.000 | 187.524 | 272.940 | 0.43750 | 0.37561 | 20 | 30 | 150.000 | 191.140 | 262.346 | 0.50000 | 0.42085 | 30 | 40 | 150.000 | 192.802 | 272.940 | 0.43750 | 0.36649 | Minimum 187.524 262.345 MAWP: 187.524 psig, limited by: Elliptical Head. Internal Pressure Calculation Results: ASME Code, Section VIII, Division 1, 1998 Code A-98 Addenda Elliptical Head From 10 To 20 SA516-60 , UCS-66 Crv. D at 275 F Required Thickness Due to Internal Pressure [tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (155.655*48.2500*1.000)/(2*15000.00*1.00-0.2*155.655) = 0.2506 + 0.1250 = 0.3756 in. Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 5.655 psig = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*15000.00*1.00*0.3125)/(1.000*48.2500+0.2*0.3125) = 194.049 - 5.655 = 188.394 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*15000.00*1.00*0.4375)/(1.000*48.0000+0.2*0.4375) = 272.940 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(K*D+0.2*t))/(2*E*t) = (155.655*(1.000*48.2500+0.2*0.3125))/(2*1.00*0.3125) = 12032.133 psi Straight Flange Required Thickness: = (P*R)/(S*E-0.6*P) + c per UG-27 (c)(1) = (155.655*24.1250)/(15000.00*1.00-0.6*155.655)+0.125 = 0.377 in. Straight Flange Maximum Allowable Working Pressure: Less Operating Hydrostatic Head Pressure of 5.278 psig = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (15000.00 * 1.00 * 0.3125)/(24.1250 + 0.6 * 0.3125) = 192.802 - 5.278 = 187.524 psig Percent Elong. per UCS-79, VIII-1-01-57 (75*tnom/Rf)*(1-Rf/Ro)

3.916%

MDMT Calculations in the Knuckle Portion: Govrn. thk, tg = 0.438 , tr = 0.251 , c = 0.1250 in. , E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.802, Temp. Reduction = 20 F Minimum Metal Temp. w/o impact per UCS-66

-55 F

MDMT Calculations in the Head Straight Flange: Govrn. thk, tg = 0.438 , tr = 0.252 , c = 0.1250 in. , E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.806, Temp. Reduction = 19 F Min Metal Temp. w/o impact per UCS-66

-55 F

Cylindrical Shell From 20 To 30 SA516-60 , UCS-66 Crv. D at 275 F Material UNS Number:

K02100

Required Thickness due to Internal Pressure [tr]: = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (155.215*24.1250)/(15000.00*0.85-0.6*155.215) = 0.2959 + 0.1250 = 0.4209 in.

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Software Verification Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 5.215 psig = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (15000.00*0.85*0.3750)/(24.1250+0.6*0.3750) = 196.355 - 5.215 = 191.140 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (15000.00*0.85*0.5000)/(24.0000+0.6*0.5000) = 262.346 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(R+0.6*t))/(E*t) = (155.215*(24.1250+0.6*0.3750))/(0.85*0.3750) = 11857.222 psi Percent Elongation per UCS-79

(50*tnom/Rf)*(1-Rf/Ro)

1.031 %

Minimum Design Metal Temperature Results: Govrn. thk, tg = 0.500, tr = 0.296, c = 0.1250 in., E* = 0.85 Stress Ratio = tr * (E*)/(tg - c) = 0.671 , Temp. Reduction = 33 F Minimum Metal Temp. w/o impact per UCS-66

-55

F

Elliptical Head From 30 To 40 SA516-60 , UCS-66 Crv. D at 275 F Material UNS Number: K02100 Required Thickness due to Internal Pressure [tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (150.000*48.2500*1.000)/(2*15000.00*1.00-0.2*150.000) = 0.2415 + 0.1250 = 0.3665 in. Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 0.000 psig = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*15000.00*1.00*0.3125)/(1.000*48.2500+0.2*0.3125) = 194.049 - 0.000 = 194.049 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*15000.00*1.00*0.4375)/(1.000*48.0000+0.2*0.4375) = 272.940 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(K*D+0.2*t))/(2*E*t) = (150.000*(1.000*48.2500+0.2*0.3125))/(2*1.00*0.3125) = 11595.000 psi Straight Flange Required Thickness: = (P*R)/(S*E-0.6*P) + c per UG-27 (c)(1) = (150.000*24.1250)/(15000.00*1.00-0.6*150.000)+0.125 = 0.368 in. Straight Flange Maximum Allowable Working Pressure: Less Operating Hydrostatic Head Pressure of 0.000 psig = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (15000.00 * 1.00 * 0.3125)/(24.1250 + 0.6 * 0.3125) = 192.802 - 0.000 = 192.802 psig Percent Elong. per UCS-79, VIII-1-01-57 (75*tnom/Rf)*(1-Rf/Ro)

3.916 %

MDMT Calculations in the Knuckle Portion: Govrn. thk, tg = 0.438, tr = 0.241, c = 0.1250 in., E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.777 Temp. Reduction = 22 G Minimum Metal Temp. w/o impact per UCS-66

-55

F

MDMT Calculations in the Head Straight Flange: Govrn. thk, tg = 0.438 , tr = 0.243 , c = 0.1250 in. , E* = 1.00 Stress Ratio = tr * (E*)/(tg - c) = 0.777 , Temp. Reduction = 22 F Min Metal Temp. w/o impact per UCS-66

-55 F

Heads and Shells Exempted to -20F (-29C) by paragraph UG-20F. Hydrostatic Test Pressure Results:

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Pressure Pressure Pressure Pressure Pressure

per per per per per

UG99b UG99b[34] UG99c UG100 PED

= = = = =

1.5 * M.A.W.P. * Sa/S 1.5 * Design Pres * Sa/S 1.5 * M.A.P. - Head(Hyd) 1.25 * M.A.W.P. * Sa/S 1.43 * MAWP

281.286 225.000 391.784 234.405 268.159

psig psig psig psig psig

UG-99(b), Test Pressure Calculation: = Test Factor * MAWP * Stress Ratio = 1.5 * 187.524 * 1.000 = 281.286 psig Horizontal Test performed per: UG-99b Please note that Nozzle, Shell, Head, Flange, etc. MAWPs are all considered when determining the hydrotest pressure for those test types that are based on the MAWP of the vessel. Stresses on Elements due to Hydrostatic Test Pressure: From| 10 | 20 | 30 |

To 20 30 40

| | | |

Stress | Allowable | Ratio | Pressure | 15553.9| 22500.0 | 0.691 | 283.02 | 16182.1| 22500.0 | 0.719 | 283.02 | 15553.9| 22500.0 | 0.691 | 283.02 |

Elements Suitable for Internal Pressure PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012 External Pressure Calculation Results: ASME Code, Section VIII, Division 1, 1998 Code A-98 Addenda Elliptical Head From 10 To 20 Ext. Chart: CS-2 at 300 F Results for Maximum Allowable External Pressure (MAEP): TCA OD D/t Factor A B 0.312 48.88 156.40 0.0008880 11829.65 EMAP = B/(K0*D/t) = 11829.6465/(0.9000 * 156.4000) = 84.0413 psig Results for Required Thickness (Tca): TCA OD D/t Factor A B 0.127 48.88 386.22 0.0003596 5214.29 EMAP = B/(K0*D/t) = 5214.2939/(0.9000 * 386.2247) = 15.0008 psig Check the requirements of UG-33(a)(1) using P = 1.67 * External Design pressure for this head. Material UNS Number: K02100 Required Thickness due to Internal Pressure [tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (25.050*48.2500*1.000)/(2*15000.00*1.00-0.2*25.050) = 0.0403 + 0.1250 = 0.1653 in. Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = ((2*S*E*t)/(K*D+0.2*t))/1.67 per Appendix 1-4 (c) = ((2*15000.00*1.00*0.3125)/(1.000*48.2500+0.2*0.3125))/1.67 = 116.197 psig Maximum Allowable External Pressure [MAEP]: = min(MAEP, MAWP) = min(84.04 , 116.1971) = 84.041 psig Thickness requirements per UG-33(a)(1) do not govern the required thickness of this head. Cylindrical Shell From 20 To 30 External Chart: CS-2 at 300 F Elastic Modulus from Chart: CS-2 at 300 F: 0.290E + 08 psi Results for Maximum Allowable External Pressure (MAEP): TCA OD SLEN D/t L/D Factor A B 0.375 49.00 176.00 130.67 3.5918 0.0002450 3552.49 EMAP = (4*B)/(3*(D/t)) = (4 * 3552.4888)/(3* 130.6667) = 36.2499 psig Results for Required Thickness (Tca): TCA OD SLEN D/t L/D Factor A B 0.264 49.00 176.00 185.84 3.5918 0.0001442 2090.75 EMAP = (4*B)/(3*(D/t)) = (4 * 2090.7549)/(3* 185.8376) = 15.0006 psig Results for Maximum Stiffened Length (Slen): TCA OD SLEN D/t L/D Factor A B 0.375 49.00 422.26 130.67 8.6175 0.0001015 1471.20 EMAP = (4*B)/(3*(D/t)) = (4 * 1471.2010)/(3* 130.6667) = 15.0123 psig Elliptical Head From 30 To 40 Ext. Chart: CS-2 at 300 F Elastic Modulus from Chart: CS-2 at 300F: 0.290E + 08 psi

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Software Verification Results for Maximum Allowable External Pressure (MAEP): TCA OD D/t Factor A B 0.312 48.88 156.40 0.0008880 11829.65 EMAP = B/(K0*D/t) = 11829.6465/(0.9000 * 156.4000) = 84.0413 psig Results for Required Thickness (Tca): TCA OD D/t Factor A B 0.127 48.88 386.22 0.0003596 5214.29 EMAP = B/(K0*D/t) = 5214.2939/(0.9000 * 386.2247) = 15.0008 psig Check the requirements of UG-33(a)(1) using P = 1.67 * External Design pressure for this head. Material UNS Number: K02100 Required Thickness due to Internal Pressure [tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (25.050*48.2500*1.000)/(2*15000.00*1.00-0.2*25.050) = 0.0403 + 0.1250 = 0.1653 in. Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = ((2*S*E*t)/(K*D+0.2*t))/1.67 per Appendix 1-4 (c) = ((2*15000.00*1.00*0.3125)/(1.000*48.2500+0.2*0.3125))/1.67 = 116.197 psig Maximum Allowable External Pressure [MAEP]: = min(MAEP, MAWP) = min(84.04 , 116.1971) = 84.041 psig Thickness requirements per UG-33(a)(1) do not govern the required thickness of this head. External Pressure Calculations | | Section | Outside | Corroded | Factor | Factor | From| To | Length | Diameter | Thickness | A | B | | | ft. | in. | in. | | psi | ------------------------------------------------------------------10 | 20 | No Calc | 48.8750 | 0.31250 | 0.00088804 | 11829.6 | 20 | 30 | 14.6667 | 49.0000 | 0.37500 | 0.00024500 | 3552.49 | 30 | 40 | No Calc | 48.8750 | 0.31250 | 0.00088804 | 11829.6 | External Pressure Calculations | | External | External | External | External | From| To | Actual T. | Required T.| Des. Press.| M.A.W.P. | | | in. | in. | psig | psig | ----------------------------------------------------------10 | 20 | 0.43750 | 0.25155 | 15.0000 | 84.0413 | 20 | 30 | 0.50000 | 0.38867 | 15.0000 | 36.2499 | 30 | 40 | 0.43750 | 0.25155 | 15.0000 | 84.0413 | Minimum 36.250 External Pressure Calculations | | Actual Len. | Allow. Len. | Ring Inertia | Ring Inertia | From| To | Bet. Stiff. | Bet. Stiff. | Required | Available | | | ft. | ft. | in**4 | in**4 | -------------------------------------------------------------------10 | 20 | No Calc | No Calc | No Calc | No Calc | 20 | 30 | 14.6667 | 35.1881 | No Calc | No Calc | 30 | 40 | No Calc | No Calc | No Calc | No Calc | Elements Suitable for External Pressure PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 RESULTS FOR LEGS: Operating Case Description: LEGS Legs attached to: node 10 Section Properties: I Beam W4X13 USA AISC 1989 Steel Table Overall Leg Length Effective Leg Length Distance Leg Up Side of Vessel Number of Legs Cross Sectional Area for W4X13 Section Inertia (strong axis) Section Inertia (weak axis) Section Modulus (strong axis) Section Modulus (weak axis) Radius of Gyration (strong axis) Radius of Gyration (weak axis)

Leglen Nleg Aleg

3.167 ft. 3.167 ft. 0.167 ft. 4 3.830 sq.in 11.300 in4 3.860 in4 5.460 in.3 1.900 in.3 1.720 in. 1.000 in.

Leg Orientation - Weak Axis

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Overturning Moment at top of Legs Total Weight Load at top of Legs Total Shear force at top of Legs Additional force in Leg due to Bracing Occasional Load Factor Effective Leg End Condition Factor

W Fadd Occfac k

5525.9 ft.lb. 14706.1 lb. 804.0 lb. 0.0 lb. 1.330 1.500

The Legs are Not Cross Braced The Leg Shear Force includes Wind and Seismic Effects Maximum Shear at top of one Leg [Vleg]: = (Max(Wind, Seismic) + Fadd) * (Imax/Itot) = (804.0 + 0.0) * (11.3/30.32) = 300.44 lb. Axial Compression, Leg furthest from N.A. [Sma] = ((W/Nleg)+(Mleg/(Nlegm*Rn)))/Aleg) = ((14706/4) + (66310/(2 * 2.08)))/3.830) = 1306.20 psi Axial Compression, Leg closest to the N.A. [Sva] = (W/Nleg)/Aleg = (14706/4)/3.830 = 959.93 psi Allowable Comp. for the Selected Leg (KL/r < Cc) [Sa]: = Occfac * (1-(kl/r)²/(2*Cc²))*Fy/(5/3+3*(Kl/r)/(8*Cc)-(Kl/r³)/(8*Cc³) = 1.33 * (1-( 57.01)²/(2 * 134.58²)) * 32150/(5/3+3*(57.01)/(8* 134.58)-(57.01³)/(8* 134.58³) = 21433.56 psi Bending at the Bottom of the Leg closest to the N.A. [S]: = (Vleg * Leglen * 12/Smdwa) = (300.44 * 3.17 * 12/1.90) = 6009.50 psi Allowable Bending Stress[Sb]: = (0.6 * Fy * Occfac) = (0.6 * 32150 * 1.33) = 25655.70 psi AISC Unity Check [Sc](must be < or = to 1.00): = (Sma/Sa)+(0.85*S)/((1-Sma/Spex)*Sb) = (1306/21433)+(0.85 *6009.499)/((1 -1306/62170) *25655) = 0.2643 PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Nozzle Calculation Summary: Description

| MAWP | Ext | APNC | UG45 | [tr] | Weld | Areas or | psig | | psig | | Path | Stresses ------------------------------------------------------------------N3 4"S/120 | 187.52 | OK | ... | OK | 0.332 | OK | Passed M-1(20"X-STG) | 191.14 | OK | ... | OK | 0.438 | OK | Passed N6 3"S/160 | 191.14 | OK | ... | OK | 0.314 | OK | Passed N1 8"S/80 | 192.80 | OK | ... | OK | 0.435 | OK | Passed N2 6"S/80 | 157.16 | OK | ... | Failed | 0.432 | OK | Passed N2 6"S/80 | 157.16 | OK | ... | Failed | 0.432 | OK | Passed -------------------------------------------------------------------Min. - Nozzles 157.16 N2 6"S/80 Min. Shell&Flgs 187.52 10 20 262.34 Computed Vessel M.A.W.P.

157.16

psig

Warning: A Nozzle Reinforcement is governing the MAWP of this Vessel. Check the Spatial Relationship between the Nozzles From | Node | Nozzle Description | 10 | N3 4"S/120 | 20 | M-1(20"X-STG) | 20 | N6 3"S/160 | 30 | N1 8"S/80 | 30 | N2 6"S/80

| Y Coordinate | Layout Angle | 0.000 | 0.000 | 32.000 | 270.000 | 38.000 | 0.000 | 0.000 | 0.000 | 0.000 | 0.000

| | | | | |

Dia. Limit 7.748 38.500 5.748 16.000 12.272

The nozzle spacing is computed by the following: = Sqrt(ll² + lc²) where ll - Arc length along the inside vessel surface in the long. direction lc - Arc length along the inside vessel surface in the circ. direction If any interferences/violations are found, they will be noted below. No interference violations have been detected! PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014

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Software Verification

Problem 5 - Vertical Vessel with Wind and Seismic Loads This sample problem is called t101 and tests the wind load and seismic calculations performed by PV Elite Math Cad was used to generate and test the programs wind generation routines, as well as the seismic response and loads. The loads from PV Elite are in perfect agreement with the Math Cad spreadsheet.

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification PV Elite® Vessel Analysis Program: Input Data Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Perform a Corroded Hydrotest Is this a Heat Exchanger User Defined Hydro. Press. (Used if > 0) User defined MAWP User defined MAPnc

225.00 psig 350 F UG99-b Note 34 Vertical 0.0000 in. 0.0000 in. -20 F Welded Air/Water/Steam RT 1 0.0 Y Y N N N N N N 0.0000 psig 0.0000 psig 0.0000 psig

Load Load Load Load Load Load Load Load Load Load Load Load

NP+EW+WI NP+EW+EQ NP+OW+WI NP+OW+EQ NP+HW+HI NP+HW+HE IP+OW+WI IP+OW+EQ EP+OW+WI EP+OW+EQ HP+HW+HI HP+HW+HE

Case Case Case Case Case Case Case Case Case Case Case Case

1 2 3 4 5 6 7 8 9 10 11 12

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Type of Surface Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

[V]

Vs Elev. (Ope) (Empty) (Filled)

ASCE-7 93 100.00 mile/hr C: Open Terrain 1.05 Moderately Smooth 0.0000 ft. 33.0 N 0.0100 0.0000 0.0000

Seismic Design Code UBC Seismic Zone (1=1,2=2a,3=2b,4=3,5=4) UBC Importance Factor UBC Soil Type UBC Horizontal Force Factor UBC Percent Seismic for Hydrotest

ASCE-7 93 5.000 1.250 S2 4.000 20.000

Design Nozzle for Des. Press. + St. Head Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9

Y

Material Database Year

1997

N N

Configuration Directives: Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use Code Case 2286 Use the MAWP to compute the MDMT Using Metric Material Databases, ASME II D

No No No No No No No

Complete Listing of Vessel Elements and Details:

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Software Verification Element From Node 10 Element To Node 20 Element Type Skirt Sup. Description Distance "FROM" to "TO" 12.000 ft. Skirt Inside Diameter 120.00 in. Diameter of Skirt at Base 120.00 in. Skirt Thickness 0.6250 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Temperature Internal Pressure 0 F Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 17500. psi Allowable Stress, Hydrotest 26250. psi Material Density 0.2830 lb./in3 P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number Plate Product Form Efficiency, Longitudinal Seam 1.0 Efficiency, Head-to-Skirt or Circ. Seam 0.85 -------------------------------------------------------------------Element From Node 20 Element To Node 30 Element Type Elliptical Description Distance "FROM" to "TO" 0.2500 ft. Inside Diameter 120.00 in. Element Thickness 0.9375 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85 Elliptical Head Factor 2.0 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Height/Length of Liquid Liquid

20 Liquid LIQUID 20 -2.5000 ft. 2.7500 ft. 56.160 b./ft³

Element From Node 20 Detail Type Nozzle Detail ID NOZZLE F Dist. from "FROM" Node / Offset dist 0.0000 in. Nozzle Diameter 32.0 in. Nozzle Schedule 80 Nozzle Class 300 Layout Angle 0.0 Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA516-70 --------------------------------------------------------------------Element From Node 30 Element To Node 40 Element Type Cylinder Description Distance "FROM" to "TO" 12.000 ft. Inside Diameter 120.00 in. Element Thickness 0.9375 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Height/Length of Liquid Liquid Density

30 Liquid LIQUID 0.0000 12.000 56.160

Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Stiffening Ring Moment of Inertia Distance from Shell Surface to Centr Stiffening Ring Cross Sectional Area Material Name Stiffening Ring Section Name Height of Section Ring Using Custom Stiffener Section

30 Ring LARGE END 11.950 ft. 1.4100 in4 2.4370 in. 2.2100 in2 SA-36 WT3X7.5 0.0000 in. No

30 ft. ft. lb./ft3

Element From Node 30 Detail Type Nozzle Detail ID NOZZLE D Dist. from "FROM" Node / Offset dist 10.000 ft. Nozzle Diameter 20.000 in. Nozzle Schedule 80 Nozzle Class 300 Layout Angle 0.0 Blind Flange (Y/N) Y Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-C -----------------------------------------------------------------Element From Node 40 Element To Node 50 Element Type Conical Description Distance "FROM" to "TO" 12.000 ft. Inside Diameter 120.00 in. Element Thickness 0.9375 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85 Cone Diameter at "To" End 72.000 in. Design Length of Cone 144.00 in. Half Apex Angle of Cone 9.4623222 Toriconical (Y/N) N Element From Node 40 Detail Type Nozzle Detail ID NOZZLE C Dist. from "FROM" Node / Offset dist 10.000 ft. Nozzle Diameter 20.000 in. Nozzle Schedule 80 Nozzle Class 300 Layout Angle 0.0 Blind Flange (Y/N) Y Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-C ------------------------------------------------------------------------Element From Node 50 Element To Node 60 Element Type Cylinder Description Distance "FROM" to "TO" 12.000 ft. Inside Diameter 72.000 in. Element Thickness 0.6250 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85

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Software Verification Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Stiffening Ring Moment of Inertia Distance from Shell Surface to Centr Stiffening Ring Cross Sectional Area Material Name Stiffening Ring Section Name Height of Section Ring Using Custom Stiffener Section

50 Ring SMALL END 0.09999 ft. 0.7030 in4 1.7830 in. 1.1900 in2 SA-36 L2.5X2.5X0.2500 [Hard Way] 0.0000 in. No

Element From Node 50 Detail Type Nozzle Detail ID NOZZLE B Dist. from "FROM" Node / Offset dist 10.000 ft. Nozzle Diameter 20.0 in. Nozzle Schedule 80 Nozzle Class 300 Layout Angle 0.0 Blind Flange (Y/N) Y Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA106-C ---------------------------------------------------------------------Element From Node 60 Element To Node 70 Element Type Cylinder Description Distance "FROM" to "TO" 12.000 ft. Inside Diameter 72.000 in. Element Thickness 0.6250 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85 Element From Node 60 Detail Type Nozzle Detail ID NOZZLE A Dist. from "FROM" Node / Offset dist 10.000 ft. Nozzle Diameter 20.0 in. Nozzle Schedule 80 Nozzle Class 300 Layout Angle 0.0 Blind Flange (Y/N) Y Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Material Name SA106-C ---------------------------------------------------------------------Element From Node 70 Element To Node 80 Element Type Elliptical Description Distance "FROM" to "TO" 0.2500 ft. Inside Diameter 72.000 in. Element Thickness 0.6250 in. Internal Corrosion Allowance 0.1250 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 225.00 psig Design Temperature Internal Pressure 350 F Design External Pressure 15.000 psig Design Temperature External Pressure 350 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 0.85 Elliptical Head Factor 2.0 Element From Node Detail Type Detail ID Dist. from "FROM" Node / Offset dist Nozzle Diameter Nozzle Schedule Nozzle Class Layout Angle Blind Flange (Y/N) Weight of Nozzle ( Used if > 0 ) Grade of Attached Flange Nozzle Matl

78

70 Nozzle NOZZLE E 0.0000 in. 18.000 in. 80 300 0.0 N 464.12 lb. GR 1.1 SA106-C

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Wind Analysis Results User Entered Importance Factor is ASCE-7 Gust Factor (Gh, Gbar) Dynamic ASCE-7 Shape Factor (Cf) for the Vessel is User Entered Basic Wind Speed Exposure Category Table Lookup Value Alpha from Table C6 Table Lookup Value Zg from Table C6 Table Lookup Value Do from Table C6

1.050 1.224 0.604 100.0 mile/hr C 7.0000 900.0000 0.0050

Wind Load Results per ASCE-7 93: Sample Calculation for the First Element: Roughness Factor = 1.000 Values [cf1] and [cf2] Because RoughFact = 1 and DQZ > 2.5 and H/D > 7.0 Interpolating to find the final cf: Because H / D < 25.0 CF = CF1 + (CF2-CF1) * (H/D - 7.0)/(25.0 - 7.0) = 0.600 + (0.700 -0.600) * (7.756 - 7.0)/(25.0 - 7.0) = 0.604 Value of Alpha, Zg is taken from Table C6-2 [Alpha, Zg] For Exposure Category C: Alpha = 7.000, Zg = 900.000 ft. Height of Interest for First Element [z] = Centroid Hgt + Base Height = 6.000 + 0.000 = 6.000 ft. but: z = Max(15.000 , 6.000) = 15.000 ft. Because z < 15 feet, use 15 feet to compute kz. Velocity Pressure Coefficient [kZ]: = 2.58(z/zg)^(2/Alpha): z is Elevation of First Element = 2.58(15.000/900)^(2/7.0) = 0.801 Determine if Static or Dynamic Gust Factor Applies Height to Diameter ratio: = Maximum Height(length)^2/Sum of Area of the Elements = 62.052(^2)/496.467 = 7.756 Vibration Frequency = 9.076 Hz Because H/D > 5 Or Frequency < 1.0: Dynamic Analysis Implemented Element O/Dia = 3 ft. Vibration Damping Factor (Operating) Beta = 0.01000 For Terrain Category C S = 1.000, Gamma = 0.230, Drag Coeff. = 0.005, Alpha = 7.000 Compute [fbar] = 10.5 * Frequency(Hz) * Vessel Height(ft)/(S * Vr(mph)) = 10.5 * 9.076 (Hz) * 62.052 (ft)/S * 1.000 (mph) = 59.134 Because FBAR > 40: FBAR = 40.000 Wind Pressure - (performed in Imperial Units) [qz] Importance Factor: I = 1.050 Wind Speed = 100.000 mile/hr qz = 0.00256 * kZ * (I * Vr)² = 0.00256 * 0.801 *(1.050 * 100.000)² = 22.605 psf Force on the First Element [Fz] = qz * Gh * CF * Wind Area = 22.605 * 1.224 * 0.604 * 20952.002 = 2433.031 lb. Element

| z | GH | Area | qz | Force | ft. | | in² | psf | lb. -----------------------------------------------------Node 10 to 20 | 6.0 | 1.224 | 20952.0 | 22.6 | 2433.0 Node 20 to 30 | 12.1 | 1.224 | 438.8 | 22.6 | 50.9 Node 30 to 40 | 18.2 | 1.224 | 21060.0 | 23.9 | 2586.5 Node 40 to 50 | 29.8 | 1.224 | 16912.8 | 27.5 | 2388.4 Node 50 to 60 | 42.2 | 1.224 | 12657.6 | 30.4 | 1975.9 Node 60 to 70 | 54.2 | 1.224 | 12657.6 | 32.6 | 2122.2 Node 70 to 80 | 61.0 | 1.224 | 1549.5 | 33.8 | 268.7 Wind Vibration Calculations

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Software Verification This evaluation is based on work by Kanti Mahajan and Ed Zorilla. Nomenclature Cf - Correction factor for natural frequency D - Average internal diameter of vessel ft. Df - Damping Factor < 0.75 Unstable, > 0.95 Stable Dr - Average internal diameter of top half of vessel ft. f - Natural frequency of vibration (Hertz) f1 - Natural frequency of bare vessel based on a unit value of (D/L²)(10^4) L - Total height of structure ft. Lc - Total length of conical section(s) of vessel ft. tb - Uncorroded plate thickness at bottom of vessel in. V30 - Design Wind Speed provided by user mile/hr Vc - Critical wind velocity mile/hr Vw - Maximum wind speed at top of structure mile/hr W - Total corroded weight of structure lb. Ws - Cor. vessel weight excl. weight of parts which do not effect stiff. lb Z - Maximum amplitude of vibration at top of vessel in. Dl - Logarithmic decrement (taken as 0.03 for Welded Structures) Vp - Vib. Chance, 0.250E+02 no chance. [Vp]: W/(L * Dr2) 117904/(60.50 * 6.4182) 0.47319E+02

Since Vp is > 25.0000 no further vibration analysis is required! The Natural Frequency for the Vessel (Ope...) is 9.07597 Hz. Wind Load Calculation | | Wind | Wind | Wind | Height | Element | From| To | Height | Diameter | Area | Factor | Wind Load | | | ft. | ft. | in2 | psf | lb. | ---------------------------------------------------------------10 | 20 | 6.00000 | 12.1250 | 20952.0 | 22.6045 | 2433.03 | 20 | 30 | 12.1250 | 12.1875 | 438.750 | 22.6045 | 50.9494 | 30 | 40 | 18.2500 | 12.1875 | 21060.0 | 23.9073 | 2586.52 | 40 | 50 | 29.7500 | 9.78750 | 16912.8 | 27.4894 | 2388.40 | 50 | 60 | 42.2500 | 7.32500 | 12657.6 | 30.3872 | 1975.92 | 60 | 70 | 54.2500 | 7.32500 | 12657.6 | 32.6371 | 2122.22 | 70 | 80 | 61.0253 | 7.32500 | 1549.50 | 33.7532 | 268.680 | PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Earthquake Analysis Results The The The The The The The

UBC Zone Factor for the Vessel is .............0.4000 Importance Factor as Specified by the User is .1.250 UBC Frequency and Soil Factor (C) is .........2.750 UBC Force Factor as Specified by the User is ..4.000 UBC Total Weight (W) for the Vessel is ........126210.5 lb. UBC Total Shear (V) for the Vessel is .........43384.9 lb. UBC Top Shear (Ft) for the Vessel is ..........0.0 lb.

The Natural Frequency for the Vessel (Ope...) is 9.07597 Hz. Earthquake Load Calculation | | Earthquake | Earthquake | Element | Element | From| To | Height | Weight | Ope Load | Emp Load | | | ft. | lb. | lb. | lb. | ---------------------------------------------------------10 | 20 | 6.00000 | 12680.2 | 1220.39 | 1032.21 | 20 | 30 | 12.1250 | 14729.2 | 2864.71 | 1032.28 | 30 | 40 | 18.2500 | 68792.1 | 20138.3 | 3927.62 | 40 | 50 | 30.2500 | 12799.0 | 6210.44 | 5252.83 | 50 | 60 | 42.2500 | 6990.49 | 4737.57 | 4007.07 | 60 | 70 | 54.2500 | 6909.11 | 6012.43 | 5085.35 | 70 | 80 | 60.3750 | 1701.74 | 1648.05 | 1393.93 | Top Load 62.00 0 0 PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 The following table is for the Operating Case. Wind/Earthquake Shear, Bending

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Software Verification | | Distance to | Cumulative | Earthquake | Wind | Earthquake | From| To | Support | Wind Shear | Shear | Bending | Bending | | | ft. | lb. | lb. | ft.lb. | ft.lb. | ------------------------------------------------------------------------10 | 20 | 6.00000 | 11825.7 | 42831.9 | 349678. | 1.224E+06 | 20 | 30 | 12.1250 | 9392.69 | 41611.5 | 222368. | 717696. | 30 | 40 | 18.2500 | 9341.74 | 38746.8 | 220026. | 707651. | 40 | 50 | 30.2500 | 6755.22 | 18608.5 | 123444. | 363520. | 50 | 60 | 42.2500 | 4366.82 | 12398.1 | 56712.1 | 177480. | 60 | 70 | 54.2500 | 2390.90 | 7660.48 | 16165.8 | 57129.0 | 70 | 80 | 60.3750 | 268.680 | 1648.05 | 208.320 | 1277.81 | PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Conical Reinforcement Calculations, ASME VIII Div. 1, App. 1 Conical Section From 40 To 50 SA516-70 Elastic Modulus Data from ASME Section II Part D at 350 F Elastic Elastic Elastic Elastic Elastic

Modulus Modulus Modulus Modulus Modulus

for for for for for

Cone Material Small Cylinder Material Large Cylinder Material Large End Reinforcement Small End Reinforcement

Axial Force on Small End of Cone Axial Force on Large End of Cone Moment on Small End of Cone Moment on Large End of Cone

0.281E 0.281E 0.281E 0.281E 0.281E

+ + + + +

08 08 08 08 08

at at at at at

350 350 350 350 350

F F F F F

15601.45 lb. 28400.43 lb. 185709.89 ft.lb. 377508.22 ft.lb.

Both ends of the Cone are Lines of Support. Maximum Centroid Reinforcement Distance Large End Maximum Centroid Reinforcement Distance Small End

1.7591 in. 1.0698 in.

No ring was found close enough to the small end to be considered. Reinforcement Calculations for Cone/Large Cylinder: Required Area of Reinforcement for Large End Under Internal Pressure Large end ratio of pressure to allowable stress 0.01286 Large end max. half apex angle w/o reinforcement 30.000 degrees Large end actual half apex angle 9.462 degrees Required Area of Reinforcement for Large End Under External Pressure Large end ratio of pressure to allowable stress 0.00086 Large end max. half apex angle w/o reinforcement 2.143 degrees Large end actual half apex angle 9.462 degrees Intermediate Value [k]: = max(Y/(Srl * Erl), 1) = max(.49175E+12/(14500.0 * 28099998), 1) = 1.2069 where [Y] is: = Large End All. Stress * Large End Elastic Modulus (Ext. temp.) = 17500.0 * 28099998 = 491749965824.0 psi^2 Allowable Stress of Large End Material (Ext. Temp) Allowable Stress of Cone Material (Ext. Temp)

17500.0 psi 17500.0 psi

Area of Reinforcement Required in Large End Shell [Arl]: = (k*Ql*Rl*tan(angle)/(Ss*E1))*(1-0.25*((P*Rl-Ql)/Ql)*(delta/alpha) = (1.2069*926.1444*60.9375*0.167/(17500*1.00)) * (1-.25*((15.00*60.938-926.144)/926.144) * (2.143/9.462) = 0.6492 in2 Area of Reinforcement Available in Large End Shell [Ael]: = .55*(Dl*ts)^.5 * (ts + tc/Cos(alpha)) = .55 * (121.875 * 0.812)^.5 * (0.812 + 0.812/ 0.986) = 8.9551 in2 Summary Area of Area of Area of

of Reinforcement Area, Large End, External Pressure: reinforcement required per App. 1-8(1) 0.6337 in2 reinforcement in shell per App. 1-8(2) 8.9551 in2 reinforcement in stiffening ring 2.2100 in2

Intermediate Results, Large End, External Pressure Area Available in Cone, Shell, and Reinforcement Force per Unit Length on Shell / Cone Junction Actual Buckling Stress associated with this Force Material Strain associated with this stress

125.08 in2 2341.66 lb./in. 1711.31 psi 0.000122

Required Moment of Inertia, Large End, External Pressure [I's]: = A * Dl2 * Atl/10.9 = 0.000122 * 121.8750 * 121.8750 * 125.08/10.9 = 20.76 in.4

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Software Verification Available Moment of Inertia, Large End, External Pressure: | Area | Centroid | Ar*Ce | Dist | I | Ar*Di² Shl | 4.447 | 0.0000 | 0.000 | 0.3786 | 0.245 | 0.638 Con | 4.508 | -0.4561 | -2.056 | 0.8347 | 0.567 | 3.141 Sec | 2.210 | 2.8433 | 6.284 | -2.4646 | 1.410 | 13.424 TOT | 11.165 | | 4.227 | | 2.222 | 17.203 Centroid of Section 0.3786 Moment of Inertia 19.43 Summary of Large End Inertia Calculations Available Moment of Inertia (Large End) * LOW * Required Moment of Inertia (Large End) Shape Name to Satisfy Area and Inertia Reqmts

| | | | |

19.425 in**4 20.448 in**4 L4X4X0.7500

Reinforcement Calculations for Cone/Small Cylinder Required Area of Reinforcement for Small End under Internal Pressure Small end ratio of pressure to allowable stress 0.01286 Small end max. half apex angle w/o reinforcement 10.000 degrees Small end actual half apex angle 9.462 degrees Required Area of Reinforcement for Small End under External Pressure Allowable Stress of Small End Material (Ext. Temp) Allowable Stress of Cone Material (Ext. Temp)

17500.0 psi 17500.0 psi

Intermediate Value [k]: = max(Y/(Srs * Ers), 1) = max(.49175E+12/(17500.0 * 28099998), 1) = 1.0000 where [Y] is: = Small End All. Stress * Small End Elastic Modulus (Ext. temp.) = 17500.0 * 28099998 = 491749965824.0 psi^2 Area of Reinforcement Required in Small End Shell [Ars]: = k * Qs * Rs * tan(alpha)/(Ss * E1) = (1.0000*881.0325*36.6250*0.1667/(17500*1.00)) = 0.3073 in2 Area of Reinforcement Available in Small End Shell [Aes] = .55*(Ds*ts)½*[(ts-t)+(tc-tr)/cos(alpha))] = .55*(73.250*0.500)½*[(0.500-0.416)+(0.812-0.290)/0.986)] = 2.0432 in² Summary Area of Area of Area of

of Reinforcement Area, Small End, External Pressure: reinforcement required per App. 1-8(3) 0.3073 in² reinforcement in shell per App. 1-8(4) 2.0432 in² reinforcement in stiffening ring 0.0000 in²

Intermediate Results, Small End, External Pressure: Area Available in Cone, Shell, and Reinforcement Force per Unit Length on Shell / Cone Junction Actual Buckling Stress associated with this Force Material Strain associated with this stress

133.28 in2 3335.18 lb./in. 1374.77 psi 0.000098

Required Moment of Inertia, Small End, External Pressure [I's]: = A * Ds2 * Ats/10.9 = 0.000098 * 73.2500 * 73.2500 * 133.28/10.9 = 6.42 in.4 Available Moment of Inertia, Small End, External Pressure: | Area | Centroid | Ar*Ce | Dist | I | Ar*Di² | Shl | 1.664 | 0.0000 | 0.000 | 0.1726 | 0.035 | 0.0 | Con | 2.742 | 0.2774 | 0.760 | -0.1048 | 0.225 | 0.0 | Sec | 0.000 | 0.2500 | 0.000 | -0.0774 | 0.000 | 0.0 | TOT | 4.406 | | 0.760 | 0.260 | 0.1 | Centroid of Section 0.1726 Moment of Inertia 0.34 Summary of Small End Inertia Calculations Available Moment of Inertia (Small End) *LOW* Required Moment of Inertia (Small End) Shape Name to Satisfy Area and Inertia Reqmts

0.340 in**4 6.419 in**4 L4X4X0.3750

The following calculations are only required per 1-5(g)(1) and do include external loads due to wind or seismic. These discontinuity stresses are computed at the shell/cone junction and do not include effects of local stiffening from a junction ring. Results for Discontinuity Stresses per Bednar p. 236 2nd Edition

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Software Verification Stress Type | Stress | Allowable | Location -------------------------------------------------------------Tensile Stress | 24142.27 | 59500.00 | Small Cyl. Long. Compres. Stress | -5902.10 | -59500.00 | Small Cyl. Long. Membrane Stress | 22370.42 | 22312.50 | Small End Tang. Tensile Stress | 11378.65 | 59500.00 | Cone Longitudinal Compres. Stress | 0.00 | -59500.00 | Cone Longitudinal * Tensile Stress | 16213.70 | 22312.50 | Cone Tangential Tensile Stress | 23455.68 | 59500.00 | Large Cyl. Long. Compres. Stress | -5908.25 | -59500.00 | Large Cyl. Long. Membrane Stress | 9573.28 | -22312.50 | Large End Tang. Tensile Stress | 23576.70 | 59500.00 | Cone Longitudinal Compres. Stress | -5787.23 | -59500.00 | Cone Longitudinal Compres Stress | 9804.50 | -22312.50 | Cone Tangential An asterisk (*) denotes that this stress was not applicable for this combination of loads. Cone Large End Not Adequately Reinforced! Cone Small End Not Adequately Reinforced! PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014

Problem 6 - Comparison against CAESAR II This example tests the forces and moments as well as the support reactions for a vertical vessel mounted on lug supports. The load on the vessel was a 1 g load applied in the "x" direction. The results between the two programs are perfect.

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Software Verification PV Elite® Vessel Analysis Program: Input Data Design Internal Pressure (for Hydrotest) Design Internal Temperature Type of Hydrotest Hydrotest Position Projection of Nozzle from Vessel Top Projection of Nozzle from Vessel Bottom Minimum Design Metal Temperature Type of Construction Special Service Degree of Radiography Miscellaneous Weight Percent Use Higher Longitudinal Stresses (Flag) Select t for Internal Pressure (Flag) Select t for External Pressure (Flag) Select t for Axial Stress (Flag) Select Location for Stiff. Rings (Flag) Consider Vortex Shedding Is this a Heat Exchanger User Defined Hydro. Press. (Used if > 0) User defined MAWP User defined MAPnc

100.00 psig 200 F UG99-b Horizontal 0.0000 in. 0.0000 in. -20 F Welded None RT 1 0.0 Y N N N N

Load Load Load Load Load Load Load Load Load Load Load Load

NP+EW+WI+BW NP+EW+EQ+BS NP+OW+WI+BW NP+OW+EQ+BS NP+HW+HI NP+HW+HE IP+OW+WI+BW IP+OW+EQ+BS EP+OW+WI+BW EP+OW+EQ+BS HP+HW+HI HP+HW+HE

Case Case Case Case Case Case Case Case Case Case Case Case

Y 0.0000 psig 0.0000 psig 0.0000 psig

1 2 3 4 5 6 7 8 9 10 11 12

Wind Design Code Basic Wind Speed Surface Roughness Category Importance Factor Type of Surface Base Elevation Percent Wind for Hydrotest Using User defined Wind Press. Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind Damping Factor (Beta) for Wind

[V]

Vs Elev. (Ope) (Empty) (Filled)

ASCE-7 93 70.000 mile/hr C: Open Terrain 1.0 Moderately Smooth 0.0000 ft. 33.0 N 0.0000 0.0000 0.0000

Seismic Design Code Seismic Coefficient Cc Performance Factor Amplification Factor Seismic Coefficient Av

ASCE-7 93 1.000 1.000 1.000 1.000

Design Nozzle for M.A.W.P. + Static Head Consider MAP New and Cold in Noz. Design Consider External Loads for Nozzle Des. Use ASME VIII-1 Appendix 1-9

Y

Material Database Year

1999

N N

Configuration Directives: Do not use Nozzle MDMT Interpretation VIII-1 01-37 Use Table G instead of exact equation for "A" Shell Head Joints are Tapered Compute "K" in corroded condition Use Code Case 2286 Use the MAWP to compute the MDMT Using Metric Material Databases, ASME II D

No No No No No No No

Complete Listing of Vessel Elements and Details:

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PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Element From Node 10 Element To Node 25 Element Type Cylinder Description Distance "FROM" to "TO" 10.000 ft. Inside Diameter 23.250 in. Element Thickness 0.3750 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 70 F Design External Pressure 5.0000 psig Design Temperature External Pressure 70 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Allowable Stress, Ambient 17500. psi Allowable Stress, Operating 17500. psi Allowable Stress, Hydrotest 26250. psi Density of Material 0.2830 lb./cu.in. P Number Thickness 1.2500 in. UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K02700 Product Form Plate Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 ----------------------------------------------------------------Element From Node 25 Element To Node 30 Element Type Cylinder Description Distance "FROM" to "TO" 10.000 ft. Inside Diameter 23.250 in. Element Thickness 0.3750 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 70 F Design External Pressure 5.0000 psig Design Temperature External Pressure 70 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 ----------------------------------------------------------------Element From Node 30 Element To Node 40 Element Type Skirt Sup. Description Distance "FROM" to "TO" 5.0000 ft. Skirt Inside Diameter 23.250 in. Diameter of Skirt at Base 23.250 in. Skirt Thickness 0.3750 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Temperature Internal Pressure 70 F Design Temperature External Pressure 70 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Head-to-Skirt or Circ. Seam 1.0 -----------------------------------------------------------------Element From Node 40 Element To Node 50 Element Type Cylinder Description Distance "FROM" to "TO" 10.000 ft. Inside Diameter 23.250 in. Element Thickness 0.3750 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.0000 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 10.000 psig Design Temperature Internal Pressure 70 F Design External Pressure 5.0000 psig Design Temperature External Pressure 70 F Effective Diameter Multiplier 1.2 Material Name SA516-70 Efficiency, Longitudinal Seam 1.0 Efficiency, Circumferential Seam 1.0 ------------------------------------------------------------------

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85

Software Verification Element From Node Element To Node Element Type Description Distance "FROM" to "TO" Inside Diameter Element Thickness Internal Corrosion Allowance Nominal Thickness External Corrosion Allowance Design Internal Pressure Design Temperature Internal Pressure Design External Pressure Design Temperature External Pressure Effective Diameter Multiplier Material Name Efficiency, Longitudinal Seam Efficiency, circumferential Seam

50 60 Cylinder 10.000 ft. 23.250 in. 0.3750 in. 0.0000 in. 0.0000 in. 0.0000 in. 10.000 psig 70 F 5.0000 psig 70 F 1.2 SA516-70 1.0 1.0

PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014 Earthquake Analysis Results The The The The The

ASCE-7 93 Factor Ac is .......................... ASCE-7 93 Factor Av is .......................... ASCE-7 93 Factor Cc is .......................... ASCE-7 93 Factor P is .......................... Element Mass Multiplier (Ac * Av * Cc * P) is .

1.000 1.000 1.000 1.000 1.000

The Natural Frequency for the Vessel (Ope...) is 4.43804 Hz. Earthquake Load Calculation | | Earthquake | Earthquake | Element | Element | From| To | Height | Weight | Ope Load | Emp Load | | | ft. | lb. | lb. | lb. | ---------------------------------------------------------10 | 25 | 5.00000 | 945.193 | 945.193 | 945.193 | 25 | 30 | 15.0000 | 945.193 | 945.193 | 945.193 | 30 | 40 | 22.5000 | 472.597 | 472.597 | 472.597 | 40 | 50 | 25.0000 | 945.193 | 945.193 | 945.193 | 50 | 60 | 35.0000 | 945.193 | 945.193 | 9453193 | PV Elite® is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014

Problem 7 - ASME Section VIII Division 2 Sample Comparisons These are example problems that compare PV Elite against ASME PTB-3-2010. Discrepancies are noted below the table. The ASME PTB-3 2010 results are per the edition of ASME VIII-2. Problem E3.2 - MDMT Stress Reduction

86

Variable

PV Elite

ASME PTB-3-2010

tn

1.81250 in.

1.8125 in.

MDMT (from Figure 3.8)

-19º F

-19.1º F

D

150.250 in.

150.25 in.

tr

1.2035 in.

1.2035 in.

Rts

0.713

0.7132

Tr

29º F

28.3º F

MDMT (final)

-47º F

-47.4º F

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Problem E4.3.1 - Cylindrical Shell Variable

PV Elite

ASME PTB-3-2010

D

90.250 in.

90.25 in.

tr

0.7229 in.

0.723 in.

tr + c

0.8479 in.

0.848 in.

Problem E4.3.2 - Conical Shell Variable

PV Elite

ASME PTB-3-2010

Dc

150.250 in.

150.25 in.

a

21.038º

21.0375º

tr

1.2894 in.

1.289 in.

tr + c

1.4144 in.

1.414 in.

Problem E4.3.3 - Spherical Shell Variable

PV Elite

ASME PTB-3-2010

tr

2.72979 in.

2.730 in.

Problem E4.3.4 - Torispherical Head Variable

PV Elite

ASME PTB-3-2010

MAWP

132.954 psi

133.0 psi

Problem E4.3.5 - Elliptical Head MAWP Variable

PV Elite

ASME PTB-3-2010

MAWP

549.6555 psi

548.9 psi

Problem E4.3.6 - Combined Load Analysis

PV Elite and CodeCalc Verification and Quality Assurance Manual

87

Software Verification Variable

PV Elite

ASME PTB-3-2013

Fxa

12799.03 psi

12799.0 psi

SE

22400 psi

22400 psi

Problem E4.3.7 - Cone Junction Analysis Part of Vessel

Variable

PV Elite

ASME PTB-3-2010

Large End Cylinder

Sigma_sm

7620.116 psi

7619.1179 psi

Sigma_sb

-21779.057 psi

-21773.7909 psi

Sigma_theta_m

3814.775 psi

3815.6850 psi

Sigma_theta_b

-6533.718 psi

-6532.1373 psi

Sigma_sm_allow

33600 psi

33600 psi

Sigma_theta_m_allo 33600 psi w

33600 psi

Sps

67200 psi

67200 psi

Sigma_sm

7089.908 psi

7088.54 psi

Sigma_sb

-18878.637 psi

-18874.0708 psi

Sigma_theta_m

3431.00 psi

3430.4012 psi

Sigma_theta_b

-5663.591 psi

-5662.2213 psi

Sigma_sm_allow

33600 psi

33600 psi

Sigma_theta_m_allo 33600 psi w

33600 psi

Sps

67200 psi

67200 psi

Sigma_sm

7086.030 psi

7084.4440 psi

Sigma_sb

16940.1504 psi

16934.4318 psi

Sigma_theta_m

20907.1934 psi

20900.5790 psi

Sigma_theta_b

5082.0454 psi

5080.3295 psi

Sigma_sm_allow

33600 psi

33600 psi

Large End Cone

Small End Junction

88

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Small End Cone

Sigma_theta_m_allo 33600 psi w

33600 psi

Sps

67200 psi

67200 psi

Sigma_sm

3811.4343 psi

3810.5711 psi

Sigma_sb

5156.5737 psi

5154.8330 psi

Sigma_theta_m

19684.223 psi

19678.6968 psi

Sigma_theta_b

1546.9722 psi

1546.4499 psi

Sigma_sm_allow

33600 psi

33600 psi

Sigma_theta_m_allo 33600 psi w

33600 psi

Sps

67200 psi

67200 psi

Problem E4.4.1 - External Pressure Analysis Variable

PV Elite

ASME PTB-3-2010

MAEP

48.905 psi

48.5 psi

Problem E4.4.2 - External Pressure Analysis Variable

PV Elite

ASME PTB-3-2010

MAEP

544.787 psi

548.5 psi

Problem E4.4.3 - Spherical Shell and Hemispherical Head Variable

PV Elite

ASME PTB-3-2010

MAEP

1554.089 psi

1554.1 psi

Problem E4.4.4 - Torispherical Head Variable

PV Elite

ASME PTB-3-2010

MAEP

94.383 psi

94.4 psi

PV Elite and CodeCalc Verification and Quality Assurance Manual

89

Software Verification Problem E4.4.5 - Spherical Shell and Hemispherical Head Variable

PV Elite

ASME PTB-3-2010

MAEP*

239.676 psi

240.1 psi

*PV Elite computes Ko based on the outside elliptical aspect ratio.

Problem E4.4.6 - Combined Loads and Allowable Compressive Stresses Variable

PV Elite

ASME PTB-3-2013

Fxa

20155.97 psi

20155.9688 psi

Problem E4.5.1 - Radial Nozzle Analysis Variable

PV Elite

ASME PTB-3-2010

MAWP

497.59 psi

497.5936 psi

PL*

16025.9023 psi

16025.9291 psi

S allow

33600 psi

33600 psi

Problem E4.5.2 - Nozzle Analysis Variable

PV Elite

ASME PTB-3-2010

MAWP

497.59 psi

497.5936 psi

PL*

19839.0 psi

19565.2577 psi

S allow

33600 psi

33600 psi

Problem E4.5.3 - Nozzle Analysis Variable

PV Elite

ASME PTB-3-2010

MAWP

550.2 psi

550.1982 psi

PL*

16174.3 psi

15881.5782 psi

S allow

33600 psi

33600 psi

* In 2011a of ASME VIII-2, there were a number of changes, especially in the area of nozzle reinforcement. Because of these changes, there will be slight differences in the results. Problem E4.6.1 - Blind Flange, required thickness

90

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Variable

PV Elite

ASME PTB-3-2010

tr

1.652 in.

1.6523 in.

Problem E4.6.2 - Welded Flat, head required thickness Variable

PV Elite

ASME PTB-3-2010

tr

0.69475 in.

0.6947 in.

Problem E4.15.1 - Horizontal Vessel Analysis Variable

PV Elite

ASME PTB-3-2010

M1*

-343345.4 in-lbs

-356913.7 in-lbs

M2*

1438748.6 in-lbs

1672855.8 in-lbs

T

33947.5 lbf

33746.5 lbf

K1**

0.1114

0.0682

K*1**

0.2003

0.1265

K2**

1.1229

1.9648

K5

0.7492

0.7492

K6 = K7

0.0504

0.0504

Sigma1

11224.55 psi

11198.5 psi

Sigma2

11544.36 psi

11384.5 psi

Sigma*3

11726.94 psi

11961.1 psi

Sigma*4

11193.97 psi

11070.9 psi

* M1 and M2 are based on the head depth, h, per equation 4.15.3 and 4.15.4, respectively. In PV Elite, this measurement is taken from the inside length, which is where hydraulic pressure is measured. PTB-3-2010 measures the head depth from the outside length. ASME Section VIII, Div. 2 does not specify a preference. ** The K factors in PTB-3-2010 are based on Δ from the 2007 ASME Div. 2 Code. PV Elite uses the correct Δ value per Table 4.15.1 of 2010 Section VIII, Div. 2. Problem E.4.15.2 - Skirt Analysis

PV Elite and CodeCalc Verification and Quality Assurance Manual

91

Software Verification Variable

PV Elite

ASME PTB-3-2013

S compressive

-2804 psi

-2803.8 psi

Fxa

15144 psi

15143.9 psi

Problem E4.16.1 - Flange Analysis Condition

Variable

PV Elite

ASME PTB-3-2010

Operating

Sh

17777.62 psi

17777.9 psi

Sr

6160.27 psi

6155.4 psi

St

5525.20 psi

5547.0 psi

Sh_allow

26700 psi

26700 psi

Sr_allow

17800 psi

17800 psi

St_allow

17800 psi

17800 psi

J

0.832

0.8313

Sh

17889.25 psi

17888.8 psi

Sr

6198.96 psi

6193.8 psi

St

5559.90 psi

5581.5 psi

Sh_allow

36000 psi

36000 psi

Sr_allow

24000 psi

24000 psi

St_allow

24000 psi

24000 psi

J

0.740

0.7398

Gasket Seating

Problem E4.16.2 - Loose Flange Analysis

92

Condition

Variable

PV Elite

ASME PTB-3-2010

Operating

Sh

3884 psi

3899.3 psi

Sr

4103 psi

4112.2 psi

St

17232 psi

17312.6 psi

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification

Gasket Seating

Sh_allow

26700 psi

26700 psi

Sr_allow

17800 psi

17800 psi

St_allow

17800 psi

17800 psi

J

1.637

1.6427

Sh

5326 psi

5204.1 psi

Sr

5626 psi

5204.1 psi

St

23630 psi

23106.3 psi

Sh_allow

36000 psi

36000 psi

Sr_allow

24000 psi

24000 psi

St_allow

24000 psi

24000 psi

J

1.985

1.9388

The G dimension in the ASME example problem did not account for the gasket outside diameter. Module

Variable

PV Elite

ASME PTB-3-2010

Top Head

tr

1.5699 in.

1.5699 in.

tr + c

1.6949 in.

1.6949 in.

tr

3.2342 in.

3.2342 in.

tr + c

3.3592 in

3.3592 in.

P

1673.14 psig

1673.140 psig

tr

1.5923 in.

1.5923 in.

tr + c

1.7173 in.

1.7173 in.

P

1671.597 psig

1671.597 psig

Cylindrical Shell

Bottom Head

Problem 8 - EN-13445 Nozzle Reinforcement This example problem tests PV Elite EN-13445 nozzle calculations in accordance with the latest edition of the EN-13445 code at the time of this writing. The sample problem benchmarks were

PV Elite and CodeCalc Verification and Quality Assurance Manual

93

Software Verification supplied by a third party European consultant. PV Elite automatically performs the nozzle calculation in both the hoop direction and the longitudinal direction. The results for areas required and available are in excellent agreement. This particular file ENNozzleTest.pvdb contains all of the EN-13445 nozzle reinforcement calculation examples shown below and is found in the \QA directory.

Example 01-A – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.093

1.09

Transverse Pmax (MPa)

2.435

2.43

Example 01-B – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.093

1.09

Transverse Pmax (MPa)

2.461

2.46

Example 01-C – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.266

1.27

Transverse Pmax (MPa)

2.823

2.82

Example 01-D – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.689

1.69

Transverse Pmax (MPa)

3.767

3.77

Example 01-E – Longitudinal and Transverse Maximum Pressure

94

Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.689

1.69

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Transverse Pmax (MPa)

3.767

3.02

Example 01-F – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.617

1.62

Transverse Pmax (MPa)

3.385

3.39

Example 01-G – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.604

1.61

Transverse Pmax (MPa)

3.358

3.36

Example 01-H – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.789

1.79

Transverse Pmax (MPa)

3.741

3.75

Example 01-I – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.155

1.16

Transverse Pmax (MPa)

2.422

2.42

Example 01-J – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

0

0

PV Elite and CodeCalc Verification and Quality Assurance Manual

95

Software Verification Transverse Pmax (MPa)

1.724

1.72

Example 01-K – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.168

1.17

Transverse Pmax (MPa)

2.449

2.45

Example 01-L – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.528

1.53

Transverse Pmax (MPa)

3.491

3.49

Example 02-A – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.269

1.27

Transverse Pmax (MPa)

2.435

2.43

Example 02-B – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.765

1.76

Transverse Pmax (MPa)

3.381

3.38

Example 02-C – Longitudinal and Transverse Maximum Pressure

96

Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.472

1.47

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Transverse Pmax (MPa)

2.823

2.82

Example 02-D – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.967

1.97

Transverse Pmax (MPa)

3.767

3.77

Example 02-E – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.283

1.28

Transverse Pmax (MPa)

2.461

2.46

Example 02-F – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.779

1.78

Transverse Pmax (MPa)

3.408

3.41

Example 03-A – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

0.75

0.75

Transverse Pmax (MPa)

1.633

1.63

Example 03-B – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.112

1.21

PV Elite and CodeCalc Verification and Quality Assurance Manual

97

Software Verification Transverse Pmax (MPa)

2.404

2.62

Example 03-C – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.333

1.33

Transverse Pmax (MPa)

2.631

2.64

Example 03-D – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

0.825

0.83

Transverse Pmax (MPa)

1.64

1.64

Example 03-E – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

0.99

0.99

Transverse Pmax (MPa)

2.449

2.45

Example 03-F – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.147

1.15

Transverse Pmax (MPa)

2.808

2.81

Example 03-G – Longitudinal and Transverse Maximum Pressure

98

Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.528

1.53

PV Elite and CodeCalc Verification and Quality Assurance Manual

Software Verification Transverse Pmax (MPa)

3.745

3.75

Example 03-H – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.79

1.53

Transverse Pmax (MPa)

2.553

2.55

Example 03-I – Longitudinal and Transverse Maximum Pressure Module

Variable

PV Elite

Benchmark

Nozzle

Longitudinal Pmax (MPa)

1.619

1.37

Transverse Pmax (MPa)

2.272

2.27

PV Elite and CodeCalc Verification and Quality Assurance Manual

99

Index A

P

Additional Manual Checks for Staff and Beta Users • 15 ASME Tubesheets Checks • 36

H

Pipe and Pad Checks • 39 Post-Development Procedures • 20 Pre-Shipping Procedures • 21 Problem 1 - Natural Frequency Calculation • 45 Problem 2 - Example of Stiffening Ring Calculation • 49 Problem 3 - Nozzle Reinforcement, Weld Strength, Weld Size • 52 Problem 4 - Vessel under Internal and External Pressure on Legs • 65 Problem 5 - Vertical Vessel with Wind and Seismic Loads • 74 Problem 6 - Comparison against CAESAR II • 83 Problem 7 - ASME Section VIII Division 2 Sample Comparisons • 86 Problem 8 - EN-13445 Nozzle Reinforcement • 93 Product Support • 11 PV Elite Development • 10 PV Elite Sample Benchmark Problem Sets • 45 PV Elite Test Jobs • 19

Half-Pipe Check • 40 Horizontal Vessel Checks • 34

R

B Base Ring Checks • 39 Beta Tests • 14

C CodeCalc QA Checks • 23 Cone Checks • 31 Corrective Action Standard • 20

D Distribution Control • 21

F Flange Checks • 28 Floating Heads Checks • 32

I Intellectual Property Statement • 9 Intergraph CAS Quality Assurance • 9 Introduction • 7, 23

Rectangular Vessel Checks • 42

S

L

Shell and Head Checks • 24 Software Issue Tracking/Resolution • 11 Software Purpose • 9 Software Verification • 13

Large Opening Checks • 41 Leg and Lug • 34

T

M

TEMA Tubesheets Checks • 37 Test Control • 13

Management/Organization • 10

N

U User Documentation • 10

Nozzle Checks • 26

W WRC 107 Checks • 38

PV Elite and CodeCalc Verification and Quality Assurance Manual

101

Index

102

PV Elite and CodeCalc Verification and Quality Assurance Manual