API 619.Rotary Compressor
Short Description
API standard for rotary compressor, oil gas standard...
Description
S T D - A P I / P E T R O S T D bL7-ENGL 1777
m
0732270 05b?3LV h30
Rotary Type Positive Displacement Compressors for Petroleum, Chemical, and Gas Industry Services API STANDARD 61 9 THIRD EDITION, JUNE 1997
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
American Petroleum Institute
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD*API/PETRO STD bL9-ENGL L997 E 0732270 05b73L5 577
m
Rotary Type Positive Displacement Compressors for Petroleum, Chemical, and Gas Industry Services
Manufacturing, Distribution and Marketing Department
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
API STANDARD 61 9 THIRD EDITION, JUNE 1997
American Petroleum Institute
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D - A P I I P E T R O STD bLS-ENGL L977 II 0732Z70 05b73Lb 403
All rights reserved No part of this work may be reproduced stored in a retrieval system, or transmitted by any m e a n s , electronic, mechanical,photocopying, recording, or otherwise, without prior written permissionfrom the publishel: Contact the Publisher; API Publishing Setvices, 1220 L Street, N. W ,Washington, D.C. 20005. Copyright O 1997 American Petroleum Institute
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
API publications necessarily address problems of a general nature. W~threspect to particbe reviewed. ular circumstances, local, state, and federal laws and regulations should API is not undertaking to meet the duties of employers, manufacturers,or suppliers to warn and properly train and equip their employees, andothers exposed, concerning health and safety risks and precautions, nor undertaking their obligations under local, state, or federal laws. Information concerning safety and health risks and proper precautions with to respect parbe obtained from the employer, the manufacturer or ticular materials and conditions should supplier of thatmaterial, or the materialsafety data sheet. Nothing contained in any API publication is to be construed as granting any right, by implication or otherwise, for the manufacture, sale,or use of any method, apparatus,or product covered by letters patent. Neither should anything containedin the publication be confor infringement of letters patent. strued as insuring anyone against liability Generally, MI standards are reviewed and revised,reaflkmed, or withdrawn at least every five years. Sometimes a one-time extensionof up to two years willbe added to this review cycle. This publication will no longer be in effect five years afterits publication date as an operative API standard or, where an extension has been granted, upon republication. Status of the publication can be ascertained from the API Authoring Department [telephone(202) 682-8000]. A catalog of API publications and materialsis published annually and updated quarterly by M I , 1220 L Street, N.W., Washington, D.C. 20005. This document was produced underM I standardization procedures that ensure appropriate notification and participation in the developmental process andis designated as an M I standard. Questions concerning the interpretation of the content of this standard or comments and questions concerning the procedures under which this standard was developed should be directed in writing to thedirector of the Authoring Department (shown on the title page of this document), American Petroleum Institute, 1220 L Street, N.W., Washington, D.C. 20005. Requests for permission to reproduce or translate all or any part of the material published herein shouldalso be addressed to the director. API standardsare published to facilitate the broad availability of proven, sound engineering and operating practices. These standards are not intended to obviate the need for applystandards should be ing sound engineering judgment regarding whenandwherethese utilized. The formulation and publication of API standards is not intended in any way to inhibit anyone from using any other practices. Any manufacturer marking equipment or materials in conformance with the marking requirements of an API standard is solely responsible for complying with all the applicable requirements of that standard.M I does not represent, warrant, or guarantee that such prodstandard. ucts do in fact conformto the applicable API
S T D = A P I / P E T R O S T D bLS-ENGL L777
0732290 0 5 L 7 3 1 7 3 V T
m
This standard is based on the accumulated knowledge and experienceof manufacturers and users of rotarytype positive displacement compressors. The objective of this standard is to provide a purchase specification to facilitate the manufacture and procurementof rotary type positive displacement compressors for use in petroleum, chemical, and gas industry services. The primary purpose of this standard is to establish minimum mechanical requirements. This limitationin scope is oneof charter as opposed to interest and concern. Energy conservation is of concern and has become increasingly important in all aspects of equipment design, application, and operation. Thus, innovative energy-conserving approaches should be aggressively pursued by the manufacturer and the user during these steps. Alternative approaches that may result in improved energy utilization shouldbe thoroughly investigated and brought forth.This is especially trueof new equipment proposals, sincethe evaluation of as opposed to acquisition cost purchase options will be based increasingly on total life costs alone. Equipment manufacturers, in particular, are encouraged to suggest alternatives to those specified when such approaches achieve improved energy effectiveness and reduced total life costs without sacrificeof safety or reliability. This standard requires the purchaserto specify certain details and features. Although it is recognized that the purchaser may desire to modify, delete, or amplify sections of this standard, it is strongly recommended that such modifications, deletions, and amplificationsbe made by supplementing this standard, rather than by rewriting or incorporating sections thereof into another complete standard. API standards are published as an aid to procurement of standardized equipment and materials. These standardsare not intended to inhibit purchasers or producers from purchasing or producing products made to other standards. do so. Every effort hasbeen made by API publications maybe used by anyone desiring to data contained in them; however, the the Instituteto assure the accuracy and reliability of the Institute makes no representation, warranty,or guarantee in connection withthis publication and hereby expressly disclaims any liability or responsibility for loss or damage resulting from its use or for the violation of any federal, state, or municipal regulation with which this publication may conflict. be submitted to the director ofthe ManufacturSuggested revisions are invited and should ing, Distribution and Marketing Department, American Petroleum Institute,1220 L Street, N.W., Washington, D.C. 20005.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
iii COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD.API/PETRO STD bL9-ENGL L997 I0732290 05b73LB 28b M
CONTENTS .
1
REFERENCES ........................................................ 2.1 Standards ........................................................ 2.2UnitConversion ...................................................
1 1
2
3
DEFINITIONS. ........................................................ This Standard ........................................ 3.1TermsUsedIn
2 2
4
BASICDESIGN ....................................................... 3 4.1General .......................................................... 3 ................................................... 5 4.2PressureCasing 4.3 CasingConnections ................................................ 6 4.4 External Forces and Moments ........................................ 6 4.5RotatingElements ................................................. 6 4.6 Shaft Seals ....................................................... 7 ....................................................... 10 4.7Dynamics 4.8Bearings ........................................................ 14 4.9 BearingHousings ................................................ 16 16 4.10 Lube-Oil and Seal-Oil Systems ...................................... 18 4.11Materials ....................................................... 4.12 Nameplates and Rotation Arrows .................................... 21 21 4.13Quality .........................................................
5
ACCESSORIES....................................................... 21 5.1 Drivers ......................................................... 21 ............................................. 22 5.2CouplingsandGuards 5.3 Mountingplates.................................................. 22 5.4 Controls andInstrumentation ....................................... 27 5.5 Piping. ......................................................... 29 5.6IntercoolersandAftercoolers ....................................... 31 31 5.7Intake Air Filters ................................................. 5.8 Pulsation SuppressordSilencers for Dry Screw Compressors .............. 32 5.9 SpecialTools .................................................... 33
6
INSPECTION. IIESTING. AND PREPARATION FOR SHIPMENT ............ 33 ......................................................... 33 6.1General ....................................................... 33 6.2Inspection 6.3 Testing ......................................................... 34 for Shipment .......................................... 37 6.4Preparation
7
VENDOR’SDATA .................................................... 7.1General ......................................................... 7.2 Proposals ....................................................... .................................................... 7.3ContractData
2
\
1 1
38 38 39 40
V
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
page
SCOPE ............................................................... 1.1 AlternativeDesigns................................................ 1.2ConflictingRequirements ...........................................
1
S T D * A P I / P E T R O STD bL7-ENGL 1997 m 0732290 05b73117 112 m
k s APPENDIXA APPENDIX B APPENDIX C APPENDIX D
APPENDIXE APPENIMF APPENDIX G APPENDIXH APPENDIX I
TYPICAL DATA SHEETS (NORMATIVE) ..................... 43 MATERIALS AND THEIR SPECIFICATIONS FOR ROTARY COMPRESSORS (INFORMATIVE) .................. 63 TYPICAL VENDOR DRAWINGAND DATA REQUIREMENTS (INFORMATIVE).......................... 67 TYPICAL SCHEMATICS FOR GENERAL PURPOSE OIL SYSTEM (DRY SCREW COMPRESSOR)AND FOR BASIC OIL SYSTEM (FLOODEDSCREW 77 COMPRESSOR) (INFORMATNE) ........................... INTERNATIONAL STANDARDS (INFORMATIVE) ............ 89 PROCEDURE FOR DETERMINATIONOF RESIDUAL UNBALANCE (INFORMATIVE) ............................ 101 FORCES AND MOMENTS (NORMATIVE) ................... 109 NOMENCLAFOR EQUIPMENT (INFORMATIVE) ....... 111 INSPECTORS CHECKLIST (INFORMATNE)................ 115
Figures 1
HelicalCompressorRotors .......................................... 1 LabyrinthShaftSeal ............................................... 8 Seal (purged) .................................. 8 3Restrictive-Ring-Type 4 OilBufferedMechanical(Contact)SealAssembly ....................... 9 5 GasBuffered or Dry Contact-Type Seal Assembly ...................... 11 6 LiquidFilm Seal. ................................................ 11 7Self-Acting Gas Seal .............................................. 12 8 RotorResponsePlot .............................................. 15 9A Typical Mounting Plate Arrangement ................................. 23 9B Qpical Mounting Plate Arrangement ................................. 24 9C Typical Mounting Plate Arrangement ................................. 25 9D Typical Mounting Plate Arrangement ................................. 26 D-1 General Purpose Oil System for Dry Screw Compressor ................. 79 D-2 Basic Oil System for Flooded Screw Compressor....................... 79 D-3OilReservoir .................................................... 80 81 D-4OilSeparator .................................................... D-5 primary (Centrifugal or Rotary) h p Arrangement..................... 82 D-6 Twin Oil Coolers and Filters W i t h Separate Continuous-Flow 83 Transfer Valves .................................................. D-7 Seal-Oil Circulation System for EquipmentW i t h Double Mechanical Seals.. 84 D-8 Lube-Oil Module at Equipment-Dry Screw Compressors ............... 85 D-9A Instrument Piping Details: Pressure Gauges, Switches, and Transmitters .... 86 D-9B Instrument Piping Details: Combined Instrument System for LowPressure Alarms and PumpStart Switches Crypical Design).............. 86 D-9C Instrument PipingDetails: Combined Instrument Systemfor LowPressure Alarms and PumpStart Switches (Alternative Design)........... 86 D-9D Instrument Piping Details: Low-Pressure Trip Switch (Altemative Design) .. 87 D-9E Instrument Piping Details: Single Pressure Gaugefor Differential87 Pressure Use .................................................... D-9F Instrument Piping Details: Diaphragm Actuator........................ 87 D-9G Instrument Piping Details: Panel- and Board-Mounted Gauges and i t h Instrument Valves.................................... 88 Switches W
2
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
vi Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D - A P I I P E T R O STD bLS-ENGL L777 W U732270 05b7320 73q m
page
D-9H Instrument Piping Details: Externally Connected Level Instruments........ 88 D-91 Instrument Piping Details: Differential Diaphragm Actuators. Indicators. Switches. and Transmitters......................................... 88 F-1SensitivityCheckWork Sheet...................................... 102 F-2SensitivityCheckWorkSheet ...................................... 103 104 F-3ResidualUnbalanceWork Sheet.................................... F-3ResidualUnbalanceWork Sheet (Continued) ......................... 105 ......................... 106 F-4SampleCalculationsforResidualUnbalance F-4 Sample Calculations for Residual Unbalance (Continued) ............... 107 G-1 Combined Resultants of the Forces and Moments of Corrections ......... 110 H-1 Dry ScrewCompressor ........................................... 113 H-2 Flooded ScrewCompressor ....................................... 114 Tables 1 2 3
14 Vibration Limits for Screw Compressors.............................. Antifriction Bearing LimitingdmN Factors ............................ 14 29 Conditions RequiringAlarms and Shutdowns .......................... Minimum Requirementsfor Piping Materials .......................... 4 30 34 Maximum Severityof Defects in Castings............................. 5 B- 1 Materials and Their Specifications for Rotary Compressors ............... 65 91 E- 1 International Standards and Referenced Publications.................... 93 E-2 Intemational Materials Standards....................................
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584. .
STD.API/PETRO S T D bL7-ENGL L777 I0732273 05b7321 870 D
Rotary Type Positive Displacement Compressors for Petroleum, Chemical, and Gas Industry Services 1 Scope
1.2 CONFLICTINGREQUIREMENTS
This standard covers the minimum requirements for dry and flooded helical lobe rotary compressors (see Figure 1) used for vacuum or pressure or both in petroleum, chemical, and gas industry services. It is primarily intended for compressors that are in special purpose applications. It does not cover portable air compressors, liquid ring compressors, and vane-type compressors. Standard air compressorsforlight dutyarecoveredinInternationalStandard ISO' 10 440: 1995-Rotary Type Positive Displacement Oil-free Compressors for General ReJinely Services Part 2-Packaged Air Compressors.
In case of conflict between this standard and the inquiry, the inquiry shall govern. At the time of order,the order shall govern.
2 References 2.1 STANDARDS
Thisstandardmakesreference to Americanstandards; be used as otherinternationalornationalstandardsmay mutually agreed between purchaser and vendor provided it can be shown that these other standards meet or exceed the American standards referenced.See Appendix E for a list of corresponding national and intemational standards.
Note: A bullet (O)at the beginningof a paragraph indicates that either a decision is required or further information is to be provided by the purchaser. This infonnation should be indicated on the data sheets (SeeAppendix A); otherwiseit should be stated in the quotation request (Inquiry) or in the order.
Note: Listing in AppendixE does not implythat the corresponding standard is equivalent to the American standard. It is the responsibility of the purchaser and the vendor to verify that the specified standard meets m exceeds the requirements of the standard listed under USA.
1.1 ALTERNATIVEDESIGNS
The vendor may offer alternative designs. Equivalent met2.1.1 Theeditions of the standards, codes,andspecificaas mutually ricfasteners,andflangesmaybesubstituted tions presented in AppendixE that are in effectat the time of E agreed upon by the purchaser and the vendor. See Appendix publication of this standard shall, to the extentspecified for list of corresponding national and international standards. of this standard.Theapplicability of herein,formapart changes in standards, codes, andspecificationsthatoccur lIntemational Organization for Standardization. IS0 publications are availafter the inquiry shall be mutually agreed upon by the purable from the American National Standards Institute, 11 West42nd Street, New York, New York 10036. chaser and the vendor.
Male
Figure 1-Helical Compressor Rotors 1 COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
rotor
~~
S T D * A P I / P E T R O STD bLS-ENGL L797 9 0732290 05b7322 7 0 7 m API STANDARD 619
2
2.1.2 Thepurchaserandthevendorshallmutuallydetermine the measures that must be taken to comply with any governmental codes, regulations, ordinances, or rules are that applicable to the equipment. 2.1.3 It is the vendor’s responsibility to invoke all applicable specifications to each subvendor. 2.2UNIT
CONVERSION
The factors in Chapter 15 of the API Manual of Petroleum Measurement Standards were used to convert fromU.S. Customary to SI units. The resulting exact SI units were then rounded off.
3 Definitions 3.1 TERMS USED IN THIS STANDARD The terms used in this standard are defined in3.1.1 through 3.1.43. Note: Refer to Hgure 1 and Appendix H for additional definitions.
3.1.1 alarm point A preset value of a parameter at which an alam is actuated to warn of a condition that requires corrective action. 3.19 anchor b o b : Bolts holding a mounting plate to a structure or foundation. Note: 7heterm structure is meant to refer to offshore platforms. The term fowrdariom refers to onshore concretdput foundations.
3.1.3 axially (horizontally) split: parallel to the shaft centerline. 3.1.4 critical
Casing joints that are
speed: See 4.7.1.
3.1.5design: The use of theworddesign in any tem (such as design power, design pressure, design temperature, or design speed) should be avoided inthe purchaser’s specifications. This terminology should be used only by the equip ment designer and manufacturer.
3.1.9generalpurposeapplication: An application that is usually spared or is in noncritical service. 3.1.10 hold downbolts (mounting bolts):Bolts holding the equipment to the mounting plate.
3.1.11 hydrodynamic bearings: Bearingsthat use the principles of hydrodynamiclubrication.Theirsurfacesare oriented so that relative motion forms an oil wedge or wedges to support the load without contact. 3.1.12 informative: An appendix of the standard which is provided forinformationand is intended to assist in the understanding or use of the standard. Compliance with an informative appendix is not mandated. 3.1.13 inlet volume flow: The flow rate expressed in volumeflowunitsat the conditions of pressure, temperature, compressibility,andgascomposition,includingmoisture content, at the compressor inlet. Actual volume flowmay be used to refer to flow at any particular location suchas interstage, rotor inlet or compressor discharge and should therefore not be used interchangeably with inlet volume. Note: To determine inlet volume flow, allowance must be made for pressure drop through silencer (pulsation suppressor) and other equipment in vendor’s scope of supply. The purchaser is advised to specify flow requirement in terms of standard volume flow or mass flow dry or wet.
3.1.14 local: The term, local, is used in relation to instruments or other ancillaries mounted on, or in close proximity to, the equipment or console. 3.1.15maximumallowabledifferentialpressure: The highest differential pressurethat can be permitted in the casing under the most severe operating conditions of minimum suction pressure and discharge pressure equal to the relief valve setting. 3.1.16maximumallowable speed (revolutions per minute): The highest speed ofthe power inputrotor at which the manufacturer’s design will permit continuous operation.
3.1.17maximumallowabletemperature: Themaxi3.1.6 dry screw compressor: A dry screw compressor uses no liquid for sealing the rotor clearances and driving themum continuous temperaturefor which the manufacturer has designed the equipment (or any part to whichthe tem is to rotor relationship is mainnoncoupledrotor.Therotor referred) when handling the specified fluid at the specified tained by timing gears on each rotor and the noncoupled rotor maximum operating pressure. is driven by the coupled rotor through the timing gears. No rotor to rotor contact occurs in dry thescrew compressor. 3.1.18maximumallowableworkingpressure: The maximum continuous pressure for which the manufacturer 3.1.7 flooded screw compressor: A rotary,helical has designed the equipment(or any part to which the term is lobe compressor which is injected with a lubricant (compatireferred) when handling the specified fluid at the specified ble with the process gas) into the rotor area after the closed maximum operating temperature. thread position of the rotor. This lubricant helps seal rotor clearances and establishes an oil film between rotors. One 3.1.19 maximum continuous speed (revolutions rotor drivesthe other in the absenceof a timing gear. per minute): The speed of the power input rotor at least 3.1.8 gauge board: An open bracket or plate used to supequal to 105 percent of the highest speed requiredby any of port and display gauges, switches, and other instruments. the specified operating conditions. --``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D - A P I / P E T R O S T D bL7-ENGL
L797 W 0732290 05b7323 b y 3 W
ROTARYTYPEPOSKIVE DISPIACEMENTCoMPRESSORS FOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
3
3.1.20maximumpower: Thehighestpowerthecom3.1.35 rotor body: The profile section on or integral with pressor and any shaft-driven appurtenances require for any of the shaft. the specified operating conditions. This power shall include 3.1.36 shutdown point: A preset value of a parameter the effect of any equipment (such as pulsation suppression devices, process piping, intercoolers, after-coolers, and sepa- at which automatic or manual shutdown of the system is required. rators) furnishedby the compressor vendor. 3.1.37specialpurposeapplication: An application 3.1.21maximumsealingpressure: Thehighestpresfor which the equipment is designed for uninterrupted, consure expected at the seals during any specified static or opertinuous operation in critical service and for which there is ating conditions and during startup and shutdown. usually no spare equipment. 3.1.22minimumallowablespeed(revolutions per minute): The lowest speedof the power input rotor at which 3.1.38 standard volume flow: The flow rate expressed the manufacturer’s design will permit continuous operation. in IS0 standard conditions as Normal cubic meters per hour (Nm3/hr) at an absolute pressure of 1.013 bar (14.7pounds per square inch (psi)) and a temperature of 0°C(32°F). U.S. 3.1.23minimumallowabletemperature: Thelowest Customary units are standard cubic feet per minute (scfm) or temperatureforwhichthemanufacturerhasdesignedthe million standard cubic feet per day (mmscfd) atan absolute equipment (or any part to which the term is referred). of pressure of 14.7pounds per square inch and a temperature 3.1.24normaloperating point Thepointatwhich 60°F. is usualoperationisexpectedandoptimumefficiency 3.1.39 standby service: A normally idle or idling piece desired. This point is usually the point at which the vendor of equipment thatis capable of immediate automatic or mancertifies that performance is within the tolerances stated in ual start-up and continuous operation. this standard. 3.1.25 normative: A requirement of the standard. Note: All referenced standards are normative, except the intemational standards in the cross-reference table in Appendix E.
3.1.26owner: Thefinalrecipientoftheequipmentand as the purchaserof the equipment. may delegate another agent
3.1.40 totalindicatedrunout (TIR): Also known as total indicator reading, is the deviation of a diameter or face determined by measurement with a dial indicator. 3.1.41 trip speed (revolutions per minute): The speed at which the independent emergency overspeed device operates to shut down a variable-speed prime mover.
3.1.27panel: An enclosureusedtomount,display,and protect gauges, switches, and other instruments.
3.1.42 unit responsibility: The responsibility for coordiall auxiliary nating the technical aspectsof the equipment and 3.1.28pocketpassingfrequency(hertz): Thefresystems includedin the scope of the order. It includes responquency at which the gas is discharged from the rotor lobes sibility for reviewing such factors as the power requirements, into the discharge port. Pocket passing frequency is rotor rev-speed,rotation,generalarrangement,couplings,dynamics, olutions per minute(rpm)times number of lobes on that rotor noise,lubrication,sealingsystem,materialtestreports, divided by 60. instrumentation, piping, and testing of components. 3.1.29 pressure casing: The composite of all stationary pressure-containing parts of the unit, including all nozzles and other attached parts. 3.1.30 radially split: Casing joints that are perpendicular to the shaft centerline. 3.1.31remote: A devicelocatedawayfromtheequipin a control house. ment or console, typically 3.1.32requiredcapacity: The largest inlet volume required by the specified operating conditions. 3.1.33 rotor: The complete rotor body (see3.1.30)and the shaft and shrunk-on sleeves (when furnished). 3.1.34rotorassembly: Consists ofbothrotorsand, where applicable, timing gears and thrust collars.
3.1.43 vendor: Also known as the supplier, is the agency that supplies the equipment. Note: The vendor may be the manufacturerof the equipment or the manufacturer’s agent and normally is responsible for servicesupport.
4 4.1
Basic Design GENERAL
4.1.1 The equipment (including auxiliaries) covered bythis standard shall be designed and constructed for a minimum service life of 20 years and at least 3 years of uninterrupted operation. It is recognized thatthis is a design criterion. 4.1.2 Thevendorshallassumeunitresponsibilityforall equipment and all auxiliary systems included in the scope of the order.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D = A P I / P E T R OS T D
bLS-ENGL
1917
m
0732270 05b7324
A P I STANDARD 619
4
o 4.1.3 Thepurchaserwillspecifytheequipment’snormalminimizecontamination by moisture,dustandotherforeign during matterpoint. operating andoperation periods of idleness. 4.1.4 Equipment shall be designed to run to the trip speed, specified maximum differential pressure and 1 10 percent of relief valve settings without damage. Note: To run without damage involves factors other than differential pressure, such as maximum discharge temperam or limiting driver p e r . In some cases the manufacturermay require special controls to avoid damage to intemal parts.
4.1.5 Unlessotherwisespecified,coolingwatersystems shall be in accordance with4.1.5.1 and 4.1.5.2. 4.1.5.1 A cooling water system or systems shall designed for the following conditions:
be
Velocity overheat exchange surfaces
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Maximum allowable working pressun (MAW) Test pressure1.5 x MAWP Maximum pressm drop Maximum inlet temperature Maximum outlet temperature Maximum tempemme rise Minimum tempemhue rise Fouling factoron water si& Shell corrosion allowance
1S-2.5 m l s
5-8 ftk
%.9 bar (Note 2) >I 0.4 bar 1 bar
>IOOpsig >I50 psig 15 psi
3OoC
90F
50T 200K 10°K 0.35 m-KkW
120 F 30 F 20 F 0.002hr-fi-F/Btu
3.0 mm
0.125 m
Note 1: The vendor shall notify the purchaser if the criteria for minimum temperatwe rise and velocity over heat exchange surfaces result in a conflict. Thc criteria for velocity over heat exchange surfaces is intended to minimize water-side fouling;the criterion for minimum temperaturerise is intended to minimize the use of cooling wafer. The purchaser will approve the final selection. Note 2 Gauge pressure.
Provision shall be madefor complete venting and draining of the system or systems. 4.1.5.2 To avoid condensation,theminimuminletwater temperaturetothebearinghousingsshouldpreferablybe above the ambientair temperature.
4.1.10 The machine and its driver shall perform on the test stand and on their permanent foundation within the specified acceptance criteria. After installation, the performance of the combined units shall be the joint responsibility of the purchaser and the vendor who has unit responsibility. O
4.1.1 1 Many factors (such as pipingloads,alignmentat operatingconditions,supportingstructure,handlingduring shipment, andhandlingandassemblyatthe site) may adversely affect site performance. To minimize the influence of these factors,the vendor shall review and comment on the purchaser’s piping and foundation drawings. When specified, the vendor’s representative shall a) observe a check on the piping performed by parting the flanges, b) check alignment at the operating temperature,and c) be present duringthe initial alignmentcheck. 4.1.12 Motors, electrical components, and electrical installationsshall be suitable forthe areaclassification (class, group, and &vision or zone) specified by the purchaseron the data sheets and shall meet the requirements of NFPAZ 70, Articles 500,501,502, and 504, as well as local codes specified and furnishedby the purchaser. 4.1.13 Controlofthesoundpressurelevel (SPL) ofall equipment furnished shall be a joint effort of the purchaser and the vendor.The equipment furnished by the vendorshall conformtothemaximumallowablesoundpressurelevel specified by the purchaser. Note: Control ofthe sound level ofthe compressor installation (including the design ofsound enclosures, ifrequind) shall be a joint effort ofthe purchaser and the vendor. These compressors tend to be very noisy. The compresor may require an acoustical enclosurt to achieve acceptablenoise levels.such factors as accessibility for operation and maintenance. purge requirements when handling flammable or toxic gas. noise levels within the enclosure, explosion-proof doors, and see-through window requiremts for machine monitoring shouldbe considered in the design and consauction of acoustical enclosures.
4.1.6 The arrangement of the equipment, including piping 4.1.14 Specifications for liquid separation equipment and auxiliaries, shall be developed jointly by the purchaser gas stream shall be developed required in the discharge and the vendor. Thearrangement shall provide adequate clearjointly by the purchaser and the vendor. for operation and maintenance. ance areas and safe access 4.1.7 All equipment shall be designed to permit rapid and economical maintenance. Major parts suchas casing components and bearing housings shall be designed (shoulderedor cylindrically doweled) and manufactured to ensure accurate alignment on reassembly. 4.1.8 Spare parts for the machine and all furnishedawiliaries shall meet all thecriteria of this standard.
Note: Liquid separalion is always required for flooded screw compressors, and may be required for dry screw compressors if liquid injectionis utilized.
4.1.15 The purchaser will specify whether the installation is indoors (heatedor unheated) oroutdoors (with or without a in roof), as well as the weather and environmental conditions which the equipment must operate (including maximum and minimum temperatures, unusual humidity, and dusty or corrosive conditions).
4.1.9 Oilreservoirsandhousingsthatenclosemoving lubricated parts (suchas bearings, shaft seals, highly polished parts, instruments, and control elements) shallbe designed to COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D * A P I / P E T R O S T D bLS-ENGL 1777 W 0732270 0 5 b 7 3 2 5 '+Lb W
ROTARYTYPE POSITIVE
DISPLACEMENT CoMPRESSORS FOR
PETROLEUM, CHEMICAL,
AND GASINDUSTRY SERVICES
5
4.2 PRESSURE CASING
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
4.2.8 Jackscrews, guide rods, and cylindrical casing-alignment dowels shall be provided to facilitate disassembly and 4.2.1 The hoop-stressvaluesusedinthedesign of the reassembly. When jackscrewsare used as a means of parting casing shall not exceed the maximum allowable stress valcontacting faces, one of the faces shall be relieved (counterues in tension specified in Section VIII, Division 1, of the bored or recessed)to prevent a leaking joint or an improperfit ASME3Code at the maximum operating temperature of the caused by marring of the face. Guide rods shall be of suffimaterial used. cient length to prevent damage to the internalsor casing studs bythecasing duringdisassemblyandreassembly.Lifting 4.2.2 Themaximumallowableworkingpressureofthe lugs or eyebolts shall be provided for lifting only the top half casing shall be at least equal to the specified relief valve setting; if a relief valve is not Specified, the maximum allowable of the casing. Methodsof lifting the assembled machine shall be specified by the vendor. working pressure shall be at least 1.25 times the maximum specified discharge pressure (gauge). 4.2.9 Whenspecifiedforcorrosionresistance,overlay 4.2.2.1 Unlessotherwisespecified,fordryscrewcomcladding or plating shall be applied to the casing wall. This pressors system pressure protection will be furnished by the procedure may require an overboreof the casing during manpurchaser. As an example, for wet CO, ufacture prior to final machining. service (carbonic acid), a stainless overlay 2.5 to 3.2 millime4.2.2.2 For flooded screw compressors, relief valves on the ters (100 to 125 mils) thick couldbe applied to the cast steel oil separators will be furnished by the vendor and sized per casing wall. The casing would be overbored to allow for a API Recommended Practice520 (including fire case) or other multilayer weld overlay lining consisting of a barrier passof criteria as specified by the purchaser. Type 309 stainless steel followedby a cover pass of 308/3 16. 4.2.3 Casings shall be made of steel if (a) rated discharge The casing wouldbe finish machined after the stainless overpressure is over 27.5 bar gauge(400 pounds per square inch), lay. The end wall could be lined similarly or have compatible 260°C (500"F), or (c) gas or (b) discharge temperature is over stainless steel end plates provided. The vendor shall include is flammable or toxic. details of this procedure in the casing design proposal. Note: In cases wherecastironcasings are acceptable,otherconsiderations such as repairability of the casing due to close rotodcaingclearances may be a consideraton in specifying casing. a steel
4-2-10 ~
4.2.4 Casingsdesignedformorethanonemaximumallowable process pressure level are not permitted. When a cooling B jacket is utilized,this jacket shall haveonly external connections between the upper and lower housings (if applicable) and shall have gasketed no connection joints. cifically approved
4.2.10.1 ThedetailsofthreadingshallconformtoASME l . 1.
4.2.5 Axially split casings shall use a metal-to-metal joint (with a suitable joint compound) that is tightly maintained by suitable bolting. Gaskets (including string type) maybe used on the axial joint with purchaser approval. When gasketed joints are used between the end covers and the cylinder of radially split casings, they shall be securely maintained by confinement of the gaskets.
~
lshall t furnished i ~ ~
as specifiedin 4.2.10.1
through 4.2.10.5.
4.2.102
Studs shall be supplied unless cap screws are spe-
by the purchaser. 4.2.10.3 Adequateclearanceshall be providedatbolting locations to permit the useof socket or box wrenches. 4.2.10.4 Internalsocket-type,slotted nut, orspanner-type bolting shall not be used unless specifically approvedby the purchaser. 4.2.10.5 Stud ASTM4 grade markings shall be located on the nut endof the exposed stud end.
4.2.6 Each axially split casing shall be sufficiently rigid to allow removal and replacement of its upper half without dis- 4.2.11 The use of tapped holes in pressure parts shall be minimized. To prevent leakage in pressure sections of casturbing rotor-to-casing running clearances. ings, metal equal in thickness to at least half the nominal bolt 4.2.7 Casings and supports shall be designed to have suffidiameter, in addition to the allowancefor corrosion, shall be cient stren,& and rigidity to limit any change of shaft alignleft around and below the bottom of drilled and tapped holes. ment at the coupling flange, caused by the worst combination The depth of the tapped holes shall be at least 1'I2times the of pressure, torque, and piping forces and moments, to 50 stud diameter. micrometers (0.002 inch). Supportsand alignment bolts shall 4.2.12 The machined finish of the mounting surface shall to moved by the use be rigid enoughto permit the machine be be 3.2 to 6.3 micrometers (125 to 250 micro-inches) arithof its lateral and axial jackscrews. I
l
'American Society Of MechanicalEngineers, York,New York 10017.
COPYRIGHT 2003; American Petroleum Institute
345 East 47th Street, New
4ASTM International. 100 Bar Harbor Drive, West Conshohocken, Pennsylvania 19428.
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
-~~
~
~
S T D - A P I / P E T R O STD b L 7 - E N G L
6
L777 I0 7 3 2 2 7 0 05b732b 352
API STANDARD 619
metic average roughness (Ra). Hold-down or foundation bolt holes shallbe drilled perpendicularto the mounting surfaceor surfaces and spot faced toa diameter three times that of the hole.
4.3.7 Flangesshallconform to ASME B16.1. B16.5, or B16.42 as applicable, except as specified in 4.3.7.1 through
be flanged or 4.3.1 Inletandoutletconnectionsshall machined and studded, orientedas specified. and suitable for the working pressureof the casing as defined in 3.1.18.
4.3.7.3
4.3.7.3.
4.3.7.1 Cast iron flanges shall be flat-faced and shall 4.2.13 The equipment feet shall be provided with vertical have a minimum thickness of Class 250 for sizes 8-inches jackscrews and shall be drilled with pilot holes that are acces- and smaller. sible for use in final doweling. 4.3.7.2 Flat-facedflanges with full raised-facethickness are acceptable on casings otherthan cast iron. 4.3CASINGCONNECTIONS
4.3.3 Connectionswelded to the casing shallmeet the material requirements of the casing, including impact values, ratherthantherequirementsoftheconnectedpiping(see 4.1 1.4.6)All . welding of connections shall be done before hydrostatic testing (see6.3.2). 4.3.4 A casing drain shallbe provided, 4.3.5 Casingopeningsforpipingconnectionsshall be at least NPS 3/4 and shall be flanged or machined and studded. Whereflanged or machined andstuddedopeningsare impractical, threaded openings in sizes N P S V4 through 1V2 are permissible. These threaded openings shall be installed as specified in4.3.5.1through 4.3.5.7. 4.3.5.1 A pipe nipple, preferably not more than 150 millimeters (6 inches) long, shall be screwed into the threaded opening. 4.3.59 Pipe nipples shall be a minimum of Schedule 160 seamless for sizes NPS 1 and smaller and a minimum of Schedule 80 for sizesN P S 1V z and larger. 4.3.5.3 The pipe nipple shall be provided with a weldingneck or socket-weld flange. 4.3.5.4 The nippleandflangematerialshallmeetthe requirements of 4.3.3. 4.3.5.5 Thethreadedconnectionshall be seal-welded; however, seal welding is not permitted oncast iron equip ment, for instrument connections, or where disassembly is requiredformaintenance.Seal-welded joints shall be in accordance withASME B31.3. 4.3.5.6 Tapped openings and bosses for pipe threads shall conform to ASME B 16.5. 4.3.5.7 pipe threads shall be taper threads conforming to ASME B 1.20.1. 4.3.6 Openings for N P S IV4, 2V2,3V2,5,7, and 9 shall not be used. COPYRIGHT 2003; American Petroleum Institute
otherwisespecified,matingparts for thesenonstandard flanges shall be furnished by the vendor. 4.3.8 Machined and studded connections shall conform to the facing and drilling requirements ofASME B 16.1,B 16.5 or B16.42. Studs and nuts shall be furnished installed. The first 1VZ threads at both ends of each stud shall be removed. Connections larger than those covered by ASME shall meet the requirementsof 4.3.7.3. 4.3.9 Tapped openings not connected to pipingshallbe plugged with solid, round-head steel plugs furnished in accordance withASME B 16.1 1. As a minimum, these plugs shall meet the requirements of the casing. Plugs that may later require removal shall beof corrosion-resistant material. A lubricant that meets the proper temperature specification shall be used on allthreaded connections. Tape shall not be applied to threads of plugs inserted into oil passages. Plastic plugs are not permitted. 4.4EXTERNAL
FORCES AND MOMENTS
4.4.1 The compressorshall be designed to withstand external forces and moments on each nozzle calculated per Equations G-1 and G-2 of Appendix G . The vendor shall furnish the allowable forces and moments for each nozzle in tabular form. Note:Silenœls may require additional support.
4.4.2 Casing and supports shall be designed to have sufficientstrengthand rigidity to limitdistortion of coupling alignment due to pressure, torque, and allowable forces and moments to 50 micrometers (0.002 inches). Note: Care should be exercised in the selectionand location of expansionpints to prevent possible early fatigue due to either pulsadon or expansion strain or both Expansionjoints should not be used in flammable or toxic serviœ.
4.5ROTATINGELEMENTS 4.5.1
Rotors
4.5.1.1 Rotor stiffness shall be adequate to prevent contact between the rotor bodies and the casing and between geartimed rotor bodies at the most unfavorable specified condiwith the shaft shallbe permations. Rotor bodies not integral Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
4.3.2 All of the purchaser’s connections shall be accessible for disassembly without the machine being moved.
Connectionsother than thosecovered by ASME
B 16.5 or B16.47 require the purchaser’s approval. Unless
nently attached to the shaft to prevent relative motion under any condition. Structural welds on rotors shall be fúll-penetration continuous welds and shall be stress relieved, with appropriate ASTM heat treatment procedure. 4.5.1.2 Shaftsshallbeforgedsteelunlessotherwiseapproved by the purchaser.
The gear enclosing chamber shall not be subject to contact with the gas. 4.5.2.3 Wheretiminggearshavetoberemoved for seal replacement, it shall be possible to retime the rotors without further disassembly of the casing.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
4.5.2.4 Timinggearsforhelicalandspiralcompressors shall have the same helix hand (rightor left) as the rotors so 4.5.1.3 Whenspecified orwhen vibrationand/oraxialthat axial position has minimal effect on timing. position probes are furnished, the rotor shaft sensing areas to beobservedbyradial-vibrationprobesshallbeconcentric 4.5.2.5 Inspection ports or other means, shall be provided with the bearing journals. All shaft sensing areas (both radial onthehousingcovers,suchthattiminggearsmay be vibration and axial position) shall be free from stencil and inspected without disassembly of the unit. scribe marks or another surface discontinuity, such as an oil hole or a keyway, for a minimum ofone probe-tip diameter 4.6 SHAm SEALS on each side of the probe. These shall not be metallized, 4.6.1 General sleeved, or plated. The final surface finish shall be a maximum of 1.0 micrometer(32micro-inches)Ra,preferably 4.6.1.1 Shaft seals shall be provided to restrict or prevent obtained by honing or burnishing. process gas leakage to the atmosphere and, fordry screws, These areas shall be properly demagnetized to the levels seal fluid leakage into the process gas stream over the range specified inAPI Standard 670 or otherwise treatedso that the of specified operating conditions, including startup and shutcombinedtotalelectricalandmechanicalrunoutdoesnot down. Seal operation shall be suitable for specified variations exceed25percent of themaximumallowedpeak-to-peak in suction conditions that may prevail during startup, shutvibrationamplitude or thefollowingvalue,whicheveris down, or settling out,and during any other special operation greater: specified by the purchaser. The maximum sealing pressure shall be at least equal to the settling out pressure. The shaft by radial-vibrationprobes, a. For areastobeobserved seals and seal system shall be designed to permit safe com5 micrometers (0.25 mil). pressor pressurization with the seal system in operation prior b. For areas to be observed by axial-positionprobes, to process startup. 10 micrometers (0.5 mil). 4.6.1.2 For low-temperatureservicessystemsshallhave 4.5.1.4 Eachrotor set shall be clearly markedwitha provision for maintaining the seal oil above its pour-point unique identification number on each male and female rotor. temperature at the inner-seal drain. This number shallbe on the endof the shaft opposite the couseals preferably shall be accessible for pling or in an accessible area that is not prone to maintenance 4.6.1.3 Shaft inspection and replacement without removing the top half of damage. the casing of a horizontally split compressor or the end hous4.5.1.5 Shaft ends shall conformto API Standard 671. ings of a vertically split unit. 4.5.1.6 Keyways shall have fillet radii conforming to a 4.6.1.4 Shaft seals may be one o f - o r a combination ofASME B17.1. the types described in 4.6.2 through 4.6.6,as specified by the purchaser. Materialsof component parts shallbe suitable for 4.5.2 Timing Gears (Dry Screw Compressors) the service. 4.6.1.5 Flooded screw type compressors shall have 4.5.2.1 Timinggearsshallbemadeofforgedsteeland as described in4.6.4.2. mechanical contact type seals shall be aminimumof AGMAS Quality 12. 'liming gears shall beof the helical type for helical and spiral compressors. Service factor isas defined inAPI Standard 613, and shall be 4.6.2LabyrinthType a minimum of 3.0. The labyrinthseal (a typical seal is shown in Figure 2) may include carbon rings in additionto the labyrinths if approved 4.5.2.2 The meshing relationship between gear-timed by the purchaser. Labyrinths may be stationary or rotating. rotorsshallbeadjustableandtheadjustmentshallbe Eductors or injection systems, when used, shall be furnished arranged for positive locking. The adjustment andlocking complete with piping, regulating and control valves, pressure provisions shall be accessible with the rotors in their bearings. be gauges, strainers,and related components. Each item shall piped and valvedto permit its removal during operation of the 5AmericanGear Manufacturers Association,1500 King Sneet, suite 201, Alexandria, Virginia223 14. is compressor.Wheregasfromthecompressordischarge
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D = A P I / P E T R OS T Db L 7 - E N G L
L777 M 0732290 0 5 b 7 3 2 8 L25
m
API STANDARD 619
8
purging required
Figure 2-Labyrinth Shaft Seal
-
to
Purge
Vent
6
5
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Key: l . Windback labyrinth 2. Seal cage 3. Spacer ring 4. Spacer washer 5. Seal assembly 6. Washer spring 7. Capscrew 8. Spacer ring
L
Figure 3-Restrictive-Ring-Type Seal (Purged)
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD-API/PETRO STD bL9-ENGL L997 H 0732290 05b7329 Ob1
m
ROTARYTVPEPOSITIVE DISPUCEMENFCOMPRESSORS FOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
usedforthemotivepower oftheeductor,provisionsmust made for sealing during startup and shutdown.
4.6.4
be
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
0
4.6.3.2 If an ejector system is used, it shall be provided with automatic control to maintain the desired seal chamber pressure. The motive fluid shall be inert gas or compressor discharge gas,as specified. 4.6.3.3 The purchaser and the vendor shall mutually agree if buffer gas injection is required for the specified operating conditions in addition to any sealing medium.
4.6.3.4 Pipingforcontinuousbuffergasinjectionshall includea150-micron(100-mesh)strainer,automaticdifferential pressure controller, low-pressure alarm, and buffer gas be specipressuregauge. Any alternativearrangementshall tmosphere. furnished the under purchaser. Oilleakage to minimize theoilby fied
Dry Screw Type Compressors
4.6.4.1.1 Single mechanical-type seals (see Figure 4) shall beprovidedwithlabyrinthsandslingers to minimizeoil leakagetotheatmosphere or intothecompressor.Oil or other suitable liquid furnished under pressureto the rotating faces may be supplied from the lube oil system or from an independentoilsysteminaccordancewith 4.10. Gasbuffered dry-contact-type seals are also available for special applications (see Fieme 5).
4.6.3.1 Restrictive-ring-typeseals(seeFigure 3) shall include rings of carbon or other suitable material mounted in retainers or spacers. The sealsmay be operated dry, as in the labyrinth type, or with a sealing liquid, as in the mechanical type. O
Mechanical (Contact) Type
4.6.4.1 Seals for
4.6.3Restrictive-RingType
4.6.4.1.2 Mechanical-typesealsshallincorporateaselfclosing feature to prevent uncontrolled gas leakage from the compressor on shutdown and loss of seal oil pressure. 0
4.6.4.1.3 Whennoprocessgasleakageis permitted, provisions shall be included to keep oil pumps operating to prevent leakageor by other means. 4-6-42 sealsforFlooded 4.6.4.2.1
screwc~~~~~~~
Mechanical-typesealsshall
be provided to
Key: 1. Bushing retainer 2. Bushing sealring 3. Snapring 4. Wavewasherspring 5. Rotationlockpin 6. O-ring 7. Sealhousing 8. Facesealring 9. Snapring 10. Compression ring 11. Spacer 12. O-ring 13. O-ring 14. Shoulder 15. Runner A. Sealface B. Bufferingoilinlet C. Clean oil return D. Clean oilreturn E. Leakage oildrain
11
Figure M i l Buffered Mechanical (Contact) Seal Assembly COPYRIGHT 2003; American Petroleum Institute
9
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
API STANDARD 619
10
pressure to the rotating faces may be supplied from the lube oil systemin accordance with4.10. 4.6.42.2 Where gas leakage to atmosphere is notpermissible, oil flooded screws require dual seal designs with independent seal fluid system. 4.6.5LiquidFilm
Note:Themode shapes commonly referred to as the first rigid (translatory or bouncing) mode, the second rigid(conical or rocking) mode, and the (first, second, third ..., nth) bending mode.
Type
Liquid-film typeseals (see Figure6) shall be provided with metallic sealing rings or sleeves and labyrinths to minimize oil leakageto the atmosphere andinto the compressor.A sealing liquid shall be supplied (asin the mechanicaltype). 4.6.6Self-ActingGas
Seal
4.6.6.1 Seal arrangement shall be single, double,or tandem as specified.
e
4.7.12 A rotor bearing system in resonance willhave its normal vibration displacement amplified. The magnitude of amplification and the rate of phase-angle are related to the amount of damping in the system and the mode shape taken by the rotor.
4.7.1.3 When the rotor amplification factor (see Figure 8) as measured at the shaft radial vibration probes, is greater than or equal to 2.5, the corresponding frequency is called a critical speed, and the correspondingshaftrotationalfrequency is also called a critical speed. For the purposes of this standard, a criticallydampedsystem is one in whichthe amplification factoris less than 2.5. 4.7.1.4 An exciting frequency may be less than, equal to, or greater than the rotational speed of the rotor. Potential exciting frequencies that are to be considered inthe design of rotor-bearing systems shall include but are not limited to the following sources:
4.6.6.2 The self-acting gas seal may require external seal gas but does notrequire any liquid for lubrication or cooling. A typical configurationis shown in Figure 7.Where toxic or flammable sealgases are used, an isolating sealis required to prevent uncontrolled leakage to the atmosphere or to the beara. Unbalance in the rotor system. ing housing. This isolating seal shall preferably be capable of b. Oil film instabilities (whirl). acting as a backup seal should the primary seal fail during c. Internal rubs. operation. The seal gas shall be filtered and shall be free of d. any contaminants that form residues. The seal gas source may Pocket passing frequencies. be taken from the compressor discharge or interstage point. e. Gear tooth meshingand side bands. An alternate seal gas sourcemay be used, and may be f.Couplingmisalignment. required during startup or shutdown. g. Loose rotor-system components. Note: other miations are commonly used depending on the particular applih. Hysteretic andfriction whirl. cation.Thesealwillleakasmallamountofsealgas,andmaybeunidireci. Boundary-layer flow separation. tional in operation. For testing considerationsat the seal manufacturers shop forthistypeofsealseeAppendixA. j. Acoustical and aerodynamic cross-coupling forces. k. Asynchronous whirl. 4.6.7Seal Buffer Gas 1. Ball and race frequencies of antifriction bearings. The seal design shall have provisionsfor buffer gas injec4.7.1.5 Resonances of structural supportsystemsmay tion to each seal. The purchaser will specify whether buffer adversely affect the rotor vibration amplitude. Therefore,resgas injection is to be used and, if so, the composition of that onances of structural support systems thatare within the vengas. In addition, the vendor shall state whether buffer gas dor’s scope of supplyandthateffecttherotorvibration injection is required for any specified operating conditions. amplitude shall notoccur within the range of specified conWhen buffer gas injection is required, the vendor shall state speeds, unless the resonances are critically damped. tinuous the gas requirements including pressures, flowrates, and filtration, and, when specified, furnish the complete control sys4.7.1.6 Rotors shallbe of a stiff-shaft construction with the tem schematic and bill of material. The method of control first actual lateral critical speed at least 120 percent of the will be specified by the purchaser. maximum allowable speed. Unless otherwise specifieda lateral critical analysisis not required. 4.7 DYNAMICS 4.7.1
Note: In most cases based on historical data the vendor will be able to demonstratethatthemachinehasastiffshaftdesign.
Critical Speed
4.7.1.1 When the frequency of a periodic forcingphenomenon (exciting frequency) applied toa rotor-bearing support system coincides witha natural frequency of that system, the system may be in a state of resonance.
4.7.2TorsionalAnalysis 4.7.2.1 Excitations of undamped torsional natural frequencies may come from many sources, which shouldbe consid-
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD.API/PETRO S T D bL7-ENGL L777 E 0732270 05b733L 7 L T m ROTARY TYPEPoSmE DISPLACEMENT COMPRESSORS FOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
-Gas
buffer
11
Key: 1. Housing 2. Seal ring Shoulder 3. 4. Piston ring 5. Pistonringretainingplate 6. Pistonringretainer 7. Assemblylock 8. Compression spring 9. Spacer 1O. Rotation lock 11.O-ring 12.O-ring 13.Compressionspring 14.Assemblylock A. Sealingdam
Figure M a s Buffered orDry Contact-Type Seal Assembly
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Key: 1. Sealringassembly 2. Inner end retaining ring 3.Coverplate 4. Sleeve 5. Spring 6. Rotation lock 7. O-ring 8. Socketheadcapscrew 9. Hexagonheadcapscrew 10. Gasket 11. Shaft sleeve 12. Locknut 13. Hexagon head capscrew 14. Carbon ring assembly 15. Wave washer 16. Shoulder ring A. Oilinlet B. Contaminated oil drain
Figure &Liquid Film Seal
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
~
~~
S T D . A P I / P E T R OS T D
bLS-ENGL
L997 m 0732270 05b7332 b5b
m
API STANDARD 619
12
lntemal
! -
I
Main primary seal
Backup seal or isolating seal
"-
" " " " " "
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Figure 74elf-Acting Gas Seal
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
~
S T D - A P I / P E T R O S T D bL9-ENGL L997 m 0732270 05b7333 592 m ROTARYTYPEPOSITIVE DISPLACEMENT COMPRESSORS FOR
PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
13
4.7.3VibrationandBalance
ered in the analysis. These sources may include but are not limited to the following:
as the 4.7.3.1 Majorpartsoftherotatingelement,such be shaft,timinggears,andnonintegralthrustcollarsshall individually dynamically balanced. When a bare shaft with a single keyway is dynamically balanced, the keyway shall be filled with a fully crowned half key. The initial balance correction to the bare shaft shall be recorded. A shaft with keyways 180 de,gees apart but not in the same transverse plane as described above. shall also be filled
a. Gear problems suchas unbalance and pitch line runout. b. Start-upproblemssuch as speeddetentsandothertorsional oscillations. c. Torsional transients such as star-ups of synchronous electric motors and transients due to generator phase-to-phase fault or phase to ground fault. d. Torsional excitation resulting from drivers suchas electric motors and reciprocating engines. e. Hydraulic governors and electronic feedback and controlloop resonances from variable-frequency motors. f. One- and two-times line frequency. g. Running speed or speeds of all rotating elements. h. Pocket passing frequency.
4.7.3.2 The rotors and timing gears shall be matchmarked or keyed. This assembly shall be check-balanced (including keys). Exposed keys and unfilled keyways are unacceptable. The maximum unbalance shall be per grade G1.O of IS0 1940/ANS16S2.19 corresponding t0-4W1N or 7 g-mm (0.01 oz-in), whichever is greater. Note: Unbalanceis expressed inIS0 tem as balance quality of IS0 1940 or in U.S. Customaryunits as:
4.7.2.2 The undamped torsional natural frequencies of the complete train shallbe at least10percent above or10 percent below any possible excitation frequency within the specified operating speed range (from minimum to maximum continuous speed).
U = 4WIN Where:
U = unbalance per plane, oz-in. W = load perjoumal, p o u n d s . N = rotativespeed,rpm. Note: Balancing small screw compressors with speeds up to 25,000 rpm to
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
4WlN would lead to extremely small unbalancevalues, which are not practi4.7.2.3 Torsionalcriticals at twoormoretimesrunning cal to achieve. The specified minimum unbalance limit typically results in speeds shall preferably be avoided or, in systems in which satisfactory lateral vibrationlevels. corresponding excitation frequencies occur, shall be shown to e 4.7.3.3 Thecalibration of therotorbalancing machine have no adverse affect. In addition to multiples of running be verified in accordance with the balancing machine shall speeds, torsional excitations that are not a function of operatmanufacturer’s procedure on at least a 60 day basis. When be coning speeds or thatare nonsynchronous in nature shall be performed in sidered in the torsional analysis when applicable and shall be specified, the residual unbalance check shall F. accordance with Appendix shown to have no adverse effect. Identification of these frequencies shall be the mutual responsibility of the purchaser Note: If the actual rotor is used,the numberof test weights shall correspond to the numberof lobes on the rotor. and the vendor. 4.7.3.4 Duringtheshoptest of themachine,assembled 4.7.2.4 Whentorsionalresonancesarecalculated to fall with the balanced rotor operating at maximum continuous within the margin specified in 4.7.2.2 (andthe purchaser and speed or at any other speed within the specified operating the vendor have agreed that all efforts to remove the critical speed range, the vibration shall be measured in accordance from within the limiting frequency range have been with M I Standard 670. Acceptance limits are to be agreed exhausted), a stress analysis shall be performed to demonbetween purchaser and vendor. Unless otherwise specified the strate thatthe resonances have no adverse effect on the comlimits in Table 1 will apply. plete train. The acceptance criteria for this analysis shall be mutually agreed upon by the purchaser and the vendor. 4.7.3.5 When shaft vibration probes are supplied, electrical and mechanical runout shall be determined and recorded by O 4.7.2.5 When specified, the vendor shall perform a torrolling the rotor in V-blocks at the journal centerline while sional vibration analysis of the complete coupled train and measuring runout with a noncontacting vibration probe and a shall be responsible for directing the modifications necessary dial indicator at the centerlineof the probe location and one to meet the requirements of 4.7.2.1 through 4.7.2.4 probe-tip diameter to either side.
i
,
~
~
~
I
O
4.7.2.6 In additiontothetorsionalanalysisrequiredin 4.7.2.2 through 4.7.2.5, the vendor shall perform a transient torsional vibration analysis for synchronous driven units and/ or variablespeedmotors.Theacceptancecriteria for this analysis shall be mutually agreed upon by the purchaser and the vendor.
COPYRIGHT 2003; American Petroleum Institute
4.7.3.6 Accuraterecords of electricalandmechanical runout, for the full 360 degrees at each probe location, shall be included in the mechanical test report. bAmerican National Standards Institute, 1 1 West42ndStreet,New New York 10036.
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
York,
S T D * A P I / P E T R O S T D bLS-ENGL L777 W 0732290 05b7334 429 W API STANDARD 61 9
14
4.7.3.7 Ifthevendorcandemonstratethatelectrical or mechanical runoutis present, a maximum of 25 percent of the 1 Table in 1 or test level calculated from Equation 6.5 micrometers (0.25 mil), whicheveris greater, may be vectonally subtracted from the vibration signal measured during the factory test.
Note: The rating life is the number of hours at the normal bearing load and speed that 90percent of a group of identical bearings will complete or exceed before the first evidence of failure.
4.8 BEARINGS
4.8.2AntifrictionBearings
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
4.8.1 General Hydrodynamic radial and thrust bearings shall be required under the following conditions:
'
a.On screwcompressorswithdriversrated greater than 225 kW (300 horsepower),unlessspecificapproval is obtained from the purchaser. b. Where antifriction-bearing dmN factors exceed the limits Table in 2. Table 1-Vibration Limits for Screw Compressors Measurementon Bearing Housing
Hydrodynamic Journal Bearings
Antifriction Bearings
vuResidual Unbalance Work Sheet --``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D - A P I / P E T R O S T D bL9-ENGL L997 m 0732290 0 5 b 7 4 L 9 U T 3
ROTARYTYPEPOSITIVE DISPLACEMENT CoMPRESSORS FOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
105
O"
goo --``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
270"
180"
The circle you have drawn must contain the origin of the polar chart. If it doesn't, the residual unbalance of the rotor exceeds the applied test unbalance. Proceed with the balancing machine sensitivity check before rebalancing is attempted. If the circle does contain the originof the polar chart, the distance between origin of the chart and the center of your circle is the actual residual unbalance present on the rotor correction plane. Measure the distancein units of scale you choosein Step 1 and multiply this number by the scale factor determined in Step 6. Distance in units of scale between origin and center of the circle times scale factor equals actual residual unbalance.
dual
actual
Record Record allowable residual unbalance (from Figure
F-3)
Rotor for Correction plane BY
No.
(am-mm)(oz.-in.) (hashas passed.not)
Date
Figure F-"Residual Unbalance Work Sheet (Continued)
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
ed:
API STANDARD 619
106
No.:
Equipment
G107
Purchase OrderNo.: drive-end, sketch): etc.-use (inlet, Correction Plane
A
Balancing Rotor Allowable N-Maximum &Weight
ofcorrection Journal this (closet to plane):
800
rpm
70,000
rpm
.
908
kg (lbs)
Umm-Maximum Allowable Residual Unbalance= 6350 WAI (4 W/N) € % Q Q q x ~ ; 4 908 x lbs/ 70,000 rprn
0.36
gm-mm (oz.-in.)
Trial unbalance(2 x Umd
0.72
gm" (oz.-in.)
R-Radius {at which weightwil be placed):
6.875
m (in.)
Trial Unbalance Weight =Trial Unbalance/R 0.72 oz.-in./ 6.875 inches
O. 70
ft (oz.)
,-".'u~"".Y
Conversion Information:1 ounce = 28.350 grams
Rotor Sketch
Test Data
A
c-1o1
Test Data-Graphic Analysis Step 1: Plot data on the polar chart (Figure C-2 continued). Scale the so chart the largest and smallest amplitude willfit conveniently. fit circle through the six points and mark the center of this circle. Step 2: With a compass, draw the best Step 3: Measure the diameter of the circlein units of scale chosenin Step 1 and record.
35
Step 4: Record the trial unbalance from above. Step 5: Double the trial unbalance in Step 4 (may use unbalance). residual actual the twice the answer Step in 5 by the answer in Step 3. Step 6: Divide
units
O. 72
g f w t w (oz.-in.) ~
7.44
g f f t - l f f f f ) (oz-in.)
0.047
Scale Factor
You now have a correlation between the units on the polar chart and the gm-in. of actual balance.
Figure F"-Sample Calculations for Residual Unbalance --``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD-API/PETRO STD bLS-ENGL
0732270 05b742L 751
L797
m
ROTARY TYPEPOSITIVE DISPLACEMENT CoMPRESSORS FOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
107
O'
90"
270'
180'
The circle you have drawn must contain the origin of the polarIf chart. it doesn't, the residual unbalance of the rotor exceeds the applied test unbalance. NOTE: Several possibilities for the drawn circle not including the of origin the polar chart include: operator error during balancing, a fautty balancing machine-pickup or cable, or the balancing machine is not sensitive enough. If the circle does contain the origin of the polar chart, the distance between origin of the chart and the centerof your circle is the actual residual unbalance present on the rotor correction plane. Measure the distancein units of scale you choosein Step land multiply this number by the scale factor determined in Step6. Distance in units of scale between origin and center of the circle times scale factor equals actual residual unbalance.
Record actual residual unbalance
5 (0.041) = 0.21
Record allowable residual unbalance (from Figure Correction plane BY
A
22)
Rotorfor
John Inspector
No.
Date
(gm-mm)(oz.-in.)
O. 36
(gm-mm)(oz.-in.)
c-101
(has/hs-&) passed.
11-31-94
Figure F-&Sample Calculations for Residual Unbalance (continued) --``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
S T D - A P I I P E T R O S T D bL7-ENGL L777
0732270 05b7422 h78 9
APPENDIX G-FORCES AND MOMENTS (NORMATIVE)
General
units: In U.S. Customary
The April 1988, November 1979, and October 1973 issues of this standard referred nozzle forces and moments calculations to appropriate NEMA documents with the stipulation thatthe constants intheequations be multiplied by1.85. Experience has shown that there has not been a uniform interpretation of “1.85 times NEMA.” Therefore, the equations have been adapted to compressors by identifying all the constants and clarifying that the equivalent of the exhaust nozzle in the NEMA calculation is the largest compressor nozzle. This is usually, but not necessarily,the inlet nozzle.
G.2 Equations
D, = (16 D”)(inches) 3 +
Where: D, = equivalent pipe diameter of the connection,in millimeters (inches). D,,, = nominal pipe diameter, millimeters in (inches). b. The combined resultantsof the forces and moments of the inlet, sidestream, and discharge connections resolved at the centerlines of the largest connection should not exceed the following:
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
G.l
The design of each compressor body must allow for lim1. The resultants shall notexceed ited piping loads on the various casing nozzles. For maximum system reliability, nozzle loads imposed by piping should be F, + 1.64 M,I40.4 ((3-2) D, as low as possible regardlessof the compressor’s load-canying capability. As a standard, the forces and moments acting In US.Customary units: oncompressors due to the inlet, sid-stream, and discharge connections shouldbe limited by the following: 2F,+ M,I 4 6 2 D, a. Thetotalresultantforceandtotalresultantmoment Where: imposedon thecompressorat anyconnectionshouldnot F, = combined resultantof inlet, sidestream, and disexceed the values shown in Equation G- l. charge forces,in Newtons (pounds). M, = combined resultantof inlet, sidestream,and disF, + 1.09 M,554.1 D, (G-1) charge moments, and moments resulting from forces, in Newton-meters (pound-feet). In U.S. Customary units: D, = diameter [in millimeters (inches)] of one circular opening equal to the totalareas of the inlet, side3F, + M, I927 D, stream, and discharge openings.If the equivalent nozzle diameter is greater than 230 millimeters Where: (9 inches), usea value of D, equal to: F, = resultant force, inNewtons(pounds).(SeeFigure - (460 + Equivalent diurnerer)(millimeters) G-1.) 3 F, = In U.S. Customary units:
,/v
- ( 18 + Equivalenr diarnerer)(inches)
M, = resultant moment, in Newton-meters (foot-pounds) from FigureG- l.
M, = For sizes up to 200 millimeters
3
,/m
2. Theindividualcomponents(FigureG-1) resultants should not exceed:
(8 inches) diameter: in
D, = nominal pipe diameter of the connection, in millimeters (inches).
F, = 16.10,
M,= 24.60,
F, = 40.50, F, = 32.40,
My= 12.30, M,= 12.30,
In U.S. Customary units:
For sizes greater than 200 millimeters (8 inches), use a value
F, = 920, Fy= 2310, F, = 1850,
Of:
M,= 4620,
M y= 23 D, 1 M,= 23 D, 1
1o9 COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
ofthese
API STANDARD 619
110
Parallel to
Compressor Shaft
Figure G-l-Combined Resultantsof the Forces and Momentsof Corrections Where:
F,= horizontal componentof F, parallel to the compressor shaft,in Newtons (pounds). Fy= vertical componentof F,,in Newtons (pounds). F,= horizontal component of F, at right angles to thecompressorshaft, in Newtons(pounds). M,= component of M,aroundthehorizontal axis, in Newton-meters (foot-pounds). expected operating My=component of M, around the vemcal axis, in Newton-meters (foot-pounds). M,= component of M,around the horizontalaxis at right angles to the compressor shaft, in Newton-meters (foot-pounds).
COPYRIGHT 2003; American Petroleum Institute
allowable c. These of values forces moments and pertain to thecompressorstructure only.They do no pertain to the forces and moments in the connecting pipes, flanges, and flange bolting, which should not exceed the allowable stress as defined by applicable codes and regulatory bodies. Loads may be increasedbymutualagreementbetweenthe purchaserand vendor.However,it is recommendedthat loads be minimized.
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
I I
'STD-API/PETRO S T D bL7-ENGL L777 W 0732290 05b7V24 '4bO
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
APPENDIX H-NOMENCLATURE FOR EQUIPMENT (INFORMATIVE)
111 COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
ROTARYTYPEP o s m v E DISPLACEMENT COMPRESSORSFOR PETROLEUM, CHEMICAL, AND GASINDUSTRY SERVICES
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
113
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
9
8
\
Major components: 1. Housing 2. Male rotor 3. Female rotor 4. Radial bearings 5. Axial bearings
2
3
/
/
5
I
6
I
6. Mechanicalseal 7. Oil pump 8. Hydraulic thrust compensating piston 9. Capacity control slide valve 10. Double acting hydraulic piston
Figure H-2-Flooded Screw Compressor
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STD.API/PETRO S T D bL9-ENGL L777
m
0732290 0 5 b 7 q 2 7 L7T
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
APPENDIX I-INSPECTOR’S CHECKLIST (INFORMATIVE)
115 COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
~~
S T D - A P I I P E T R O STD bL7-ENGL L777
0732270 05b7Y28 OOb
INSPECTOR'S CHECKLIST REFERENCE PARAGRAPH API 619
ITEM
DATE INSPECTED
INSPECTED
BY
STATUS
~
Material inspection
6.2.2
Piping fabrication andinstallation
5.5.1.1 5.5.4.2 6.3.2 6.3.3 6.3.3.4.4
Full-pressudfull-load/full-speedtest Inspection ofhuWshaft fitfor hydraulically mounted couplings Governor response and EmergencyOverspeed-Tripsystems test Spare parts test Check after the heatrun Additional tests-as specified Examination of internals for cleanliness: piping oil reservoir bearing housings gear housings coolers filters other Nameplates and Rotation Arrows Overall dimensions and connection locationss Flange dimensions and finish" Anchor bolt layout andsizea ~
6.3.4.1 6.3.4.2 6.3.4.3 6.3.4.4 6.3.4.5 6.3.4.6 6.3.4.7 6.3.4.8 6.3.4.9 6.3.4.10 6.3.4.1 1 6.3.4.12 6.3.5
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Hydrostatic test Mechanical running test Gas leakage test Optional tests: Performance test Complete unit test Tandem test Gear test Helium test Sound-level test Auxiliary equipment test Post-test inspection
4.12
~
seck against certified drawings. COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
INSPECTOR'S CHECKLIST REFERENCE PARAGRAPH M I 619
ITEM
DATE INSPECTED
INSPECTED
BY
Preparation for shipment Corrosion protection-exterior Corrosion protection-interior Corrosion Drotection-lubricated surfaces Closures of all openings
6.4.3.1 6.4.3.2 6.4.3.3 6.4.3.4 6.4.3.6,6.4.3.7 6.4.3.8 4.12.3 Equipment nameplate data 6.4.3.10 Equipment identification Piping connections identification (tagging) 6.4.4 Additional inspections-as specified ~~
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
COPYRIGHT 2003; American Petroleum Institute
Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
STATUS
S T D - A P I / P E T R O STD bL7-ENGL L977
m
0732270 0 5 b 7 4 3 0 7 b 4
m
--``,,,,,``,,``,`,,`````,,```,-`-`,,`,,`,`,,`---
Additional copies available from API Publications and Distribution:
(202)682-8375 Informationabout API Publications, Programs and Services is avaiiable on the World Wlde Web at: hnp.Jhryww.api.org
American Petroleum Institute COPYRIGHT 2003; American Petroleum Institute
1220 L Street, Northwest Washington, D.C. 20005-4070 202-682-8000 Document provided by IHS Licensee=BP Amoco/5928366101, User=, 03/18/2003 01:22:58 MST Questions or comments about this message: please call the Document Policy Management Group at 1-800-451-1584.
Order No.:C61903
View more...
Comments
