ML17264A613

Rev 0 to Verification of Pressure Locking Analysis Program Preslok

ML17264A613
Person / Time
Site:	Ginna
Issue date:	08/02/1996
From:	Ezekoye L, Wendy Moore, Walker L ROCHESTER GAS & ELECTRIC CORP.
To:
Shared Package
ML17264A608	List: ML17264A607 ML17264A610 ML17264A611 ML17264A612 ML17264A613
References
V-EC-1606, V-EC-1606-R, V-EC-1606-R00, NUDOCS 9609270308
Download: ML17264A613 (90)

Text

+'

I WESTINGHOUSE PROPRIETARY CLASS 2C Westinghouse Calculation Note Cover Sheet PAGE! OP t Z.

CALC NO:

V-EC-0 606 REV:

0 TITLE:

VERIFICATIONOF PRESSURE LOCKING ANALYSISPROGRAM PRESLOK PROJECT:

WOG PURPOSE: (see page(s))

5 SHOP ORDER:

220 RESULTS: (see page(s))

5; 6 IS THERE MICROFILMASSOCIATED WITH THIS CALCULATION?

YES l NO AUTHOR(S):

NAME (Print or Type)

WILLIAME. MOORE SIGNATURE DATE

~/z/e VERIFIER(S):

NAME (Print or Type)

L IKE EZEKOYE SIGNATURE DATE Method of Verification Used:

Indepent Review MANAGER NAME (Print or Type)

I I. WALKER Sl URE DATE zlsist.

This document contains intormabon prapnetaiy to westinghouse Etecatc Corporabon. Energy systems Business Unit. and Nuclear Technology Division: it is submitted in cantidence and is to be used solely tor the purpose tor which it is tumtshed. then returned upon request.

This document and such mtormabon is not ta be reproduced. transmitted. disclosed or used otherwise et whole or in part without pnor wnnen authonzabon ot Wesbnghause Electric Corparaaon, Energy Systems Business Unit and Nuclear Technology Oivison.

Copyright 1996, Wesanghouse Elecmc Coiporaaon All Rights Reserved 9609270308 960924 PDR" ADOCK 05000244 P

PDR

e l

/Iw A

kA-oE-qg-o7b A.do Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Gale. No.: V-EC-1606 Page Group: AEE C'ALCULATIONNOTE METHODOLOGY CHECKLIST cALc-NQTE NUMBER:

V-EC-1 606 CHECKUST TO BE COMPLETED BY AUTHOR(S).

REV.

0 (CHECK APPROPRIATE RESPONSE) 1.

Is the Subject and/or the Purpose of the Design Analysis Clearly Stated?..

.Yes l No 2.

Are the Required Inputs and Their Sources Provided?.........

Yes l No N/A 3.

Are the Assumptions Clearly Identified and Justified?..........

Yes Z No N/A 4:

Are the Methods and Units Clearly Identified?

5.

Have the Limits of Applicability Been Identified?.:..

Yes Z No N/A

~.... Yes Z No N/A 6.

Are the Results of Literature Searches, if Conducted.

or Other Background Data Provided?

Yes No N/Al 7.

Are all the Pages Sequentially Numbered and Identified by the Calculation Note Number?

8.

Is the Project or Shop Order Clearty Identified?

Yes e No

. Yes e No 9.

Has the Required Computer Calculation Information Been Provided?

10.

Were the Computer Codes Used Under Configuration Control?

...... Yes No

~

N/A Z Yes No N/A d 11.

Were the Computer Code(s) Used Applicable for Modeling the Physical and/or Computational Problems Identified?........

Yes No N/A Ã 12.

Are the Results and Conclusions Clearly Stated?.............

Yes /

No 13.

Are Open Items Properly Identified?.....................

Yes No N/Al 14.

Were Approved Design Control Practices Followed Without Exception?....................................

Yes l No NOTE' If no to any of the above, page number contalnlng justlfIcation:

0

CALC-NOTE NUMBER V-EC-1606 REV:

0 PAGE:

PROPRIETARY CLASS INFORMATION SHEET'.

The information in this calc note has been determined by the author(s) or appropriate Westinghouse personnel to be; Proprietary Class 1

Proprietary Class 2 (no or some Class 2C content)

Proprietary Class 2C

'roprietary - Must be Classified Prior to Release 2.

If Class 2, describe the specific Class 2 content or method for designating Class 2 content.

3.

If Class 2, justify or provide reference for Class 2 basis.

4.

If Class 2 or 2C, identify customer for which the calc note was specifically generated.

(This information u provide some basis for a Class 2C release using form 36EZ).

CALCULATlONWAS GENERATED FOR THE WESTlNGHOUSE OWNER'S GROUP 5.

If Class 2 or Class 2C. identify plants or types of plants for which the calc note should be considered generically applicable (i.e., if not plant-specific):

If the calc note is plant-specific. list "plant-specific"..(Thi information will provide some basis for a Class 2C release using Form 36EZ).

GENERALLY APPLICABLETO FLEXlBLEWEDGE TYPE GATE VALVES Note that prior to release.

this calc note must be accompanied by a cover sheet which includes the appropriate proprietary information markings and disclosure daises as specified in WCAP-7211, Rev. 3.

Note also that prior to release.

all pages of this calc note must be marked with the appropriate proprietary class designation.

R lAs95HAAPFOAMS~CCOYR PM2

~

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: NOG-220 Cate. No.: V-EC-1606 II Pp 5+ 57 Page Group: AEE TA8LE OF CONTENTS SECTION CALCULATIONNOTE COVER SHEET

.CALCULATIONNOTE METHODOLOGY CHECKLIST PROPRIETARY CLASS INFORMATION SHEET TABLEQF CONTENTS PURPOSE

- CONCLUSIONS METHODOLOGY REFERENCES COMPARISON QF RESULTS SAMPLE PROBLEM - HAND CALCULATION APPENDIX A - USER'S GUIDE FOR PRESLOK APPENDIX B

- PRESLQK VERSION 1 SAMPLE PROBLEM OUTPUT APPENDIX C PRESLQK VERSION 2 SAMPLE PROBLEM OUTPUT PAGE 2'-

12 1 -32

~

1-6 1-6

hP -lcm'- g$ -o7b ke0 b Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Gale. No.: V-EC-1606 Page 5 Group: AEE PURPOSE.

The purpose of this calculation is to provide verification that the MATHCAD program PRESLQK, which was developed for the Westinghouse Owner's Group to perform pressure locking analysis of flexible wedge type gate valves using the Commonwealth Edison method, accurately performs the required calculations.

This verification will apply to Version 1 of the program (preslok1.mcd), which accepts closing valve factor as an input, and also to Version 2(preslok2.mcd),

which accepts the coefficient of friction between the disk and the seat as an input.

CONCl USIONS The conclusion of this report is that both Version 1 and Version 2 of the program PRESLQK, as described in Rev.

1 to the User's Manual, correctly perform the calculations necessary to analyze flexible wedge type gate valves for pressure locking using the Commonwealth Edison methodology.

METHODOLOGY The PRESLOK User's Manual is attached to this calculation as Appendix A and is part of this calculation.

The remainder of the calculation consists of a problem which is worked out by hand and compared to the PRESLOK Version 1

calcuiation results to verify that the MATHCADinstructions accurately reflect the analysis methods being used.

We have also computed the answers for this problem using the PRESLOK Version 2 program by entering the co-efficient of friction corresponding to the valve factor used in the test problem.

The PRESLOK Version 1 and PRESLOK Version 2 outputs for the test problem are attached to this calculation as Appendices 8 and C.

REFERENCES Letter MSE-AEE-11448, January 19, 1996.

This letter transmits the minutes of the WOG Subgroup on Pressure Locking and Thermal Binding meeting on 1/4-1/5/96.

2. 'SER'S GUIDE FOR PRESLQK, A GATE-VALVEPRESSURE'LOCKING ANALYSIS PROGRAM USING THE COMMONWEALTHEDISON MODEL, REVISION 1, February 7, 1996.

This revision of the manual

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.Q. No.: YVOG-220 Calc. No.: Y-EC-1606 I

Page Group: AEE:.

incorporates changes requested at the WQG Subgroup on Pressure Locking and Thermal Binding meeting on 1/4-1/5/96, as well as changes identified during the verification process.

This document is Appendix A of this calculation.

3.

Roark. Raymond J.,

and Young, Warren C., Formulas for Stress and Strain, 5th Edition, McGraw-Hill Book Company, 1975.

COMPARlSON OF RESULTS A line by line comparison of the results was performed, looking at as many significant figures in the MATHCADoutput as were calculated in the hand catculations.

The only result where the difference between the hand calculation and the MATHCADcalculations exceed one digit in the sixth significant figure is in the seat load.

The difference in this result is Hand Calculation S = 82848 644 It)

MATHCADCalculation FS = 82848.014 lb.

- cgigf'erence

- 82,848.81'4

- 82,848.644 xl00

= 0.0002 82, 848. 644 This amount of error is attributable to round off error, since the computer carries more significant digits than the hand calculation.

The programs PRESLQK

.Version 1 and PRESLQK Version 2 are considered verified.

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Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK ProjectJS.O.

No.: HOG-22D Calc. No.: V-EC-1606 IA+~7 APPENDIX A. Page l Group: AEE USER'S GUIDE FOR PRESLOK, A GATE VALVEPRESSURE LOCKING ANALYSIS PROGRAM USING'THE COMMONWEALTHEDISON MODEL REVISION 1

February 7, 1996 While this information js presented in good faith and believed to be accurate, thc Westinghouse Owner's Group does not guarantee satisfactory results from reliance upon such information.

Nothing contained herein is to be construed as a warranty, express or implied. regarding the.

performance. merchantabBity. fitncss or any other.matter with respect to thc product. nor as a recommendation to usc any product or process in conflict with any patent.

The Westinghouse Owner's Group rcservcs thc right. without notice. to alter or improve thc methods described herein.

vec1 606.wog 0207961339

p

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK ProjectlS.O. No.: WOG-220 Calc. No.: V-EC-l606

~ i-+>7 Ji APPENDIX A, Page 2 Group: AEE USER'S GUIDE FOR PRESLOK GATE VALVEPRESSURE LOCKING ANALYSISPROGRAM USING THE COMMONWEALTHEDISON MODEL RECORD OF REVISION PAGE Rev. 0 Rev.

l Original Issue January 2. 1996 February 7, 1996 Corrected various typographical errors that had no effect on the content.

Removed erroneous negative sign from thc equation for Q, on page 16.

Corrected the equation for Ks and added a note after thc equation for K>> on page 16.

Subscript corrected from ybw.to ysw in thc calculation of shear deflection duc to seat load. page

17. Thc section concerning thc calculation of thc equilibrium contact load and the load per seat was rcwrittcn, page 18.

Minor spelling and English corrections werc made to the section discussing "Determining thc Disk to Seat Friction Coefficien,"

page

18. Thc calculation of the stem force component required to overcome thc pressure locking scat'load was put into standard equation format, page

18. Clarifie that thc Static Unseating Force is a program input.

page 18.

(F,~) was removed from the subheading title "Reverse Piston Effect," page

19. Thc figures on pages 14 and 19 werc redrawn.

An equation for thc total force required to overcome pressure locking force was added.

page

19. Thc final paragraph, which discussed acceptance criteria. was deleted, page

19. Table numbers werc added to thc case numbers given next to equations which were taken from Roark, various pages.

vec1 606.wog 02079616pa

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g<g g Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: NOG-220 Calc. No.: V-EC-1606 pg i0 ~=7 APPENDIX A. Page 3 Group: AEE USER'S GUIDE FOR PRESLOK GATE VALVEPRESSURE LOCKING ANALYSIS PROGRAM USING THE COMMONWEALTHEDISON MODEL TABLE OF CONTENTS SECTION TITLE PAGE REVISION

SUMMARY

TABLE OF CONTENTS INTRODUCTION HARDWARE/SOFTWARE REQUIREMENTS GERING STARTED RUNNING THE PRESLOK ANALYSIS INPUT PREPARATION THEORY EXAMPLE USING PRESLOK VERSION l EXAMPLE USING PRESLOK VERSION 2 PAGE NO.

6-7 20 REFERENCES vecl606.wag 0207961339

Proprietary'lass 2C Verification of Pressure Locking Analysis Program PRESLOK ProjectjS.O. No.: WOG-220 Calc. No.: V-EC-1606 APPENDIX A Page 4 Group: AEE USER'S GUIDE FOR PRESLOK INTRODUCTION Prcssure locking is a phcnomcnon which can cause thc unseating thrust for a gate valve to increase dramatically from its typical stati unseating thrust.

This can possibly result in the valve failing to open duc to thc actuator having insufficient thrust capability.

Prcssure locking can also result in valve damage in cases where thc actuator thrust capability exceeds the valve structural capacity.

For thcsc reasons.

a proper understanding of the conditions which may cause pressure locking, as weil as a methodology for predicting thc increase in unseating thrust for a pressure locked valve.

arc necessary.

A method of analyzing gate valves to predict the incrcasc in unseating thrust for a pressure locked valve has been developed by Commonwealth Edison. and has been presented by Mr. Brian Bunte (Ref. 1). The Westinghouse Owner's Group, in thc Pressure Locking/Thermal Binding Task Team mccting on November 13 and 14, 1995. authorized the preparation of a MATHCADprogram and accompanying user's manual to allow thc uniform use of.the Commonwealth Edison pressure locking analysis methodology.

This manual is thc result of that authorization.

This manual and the program file for performing the analysis are available from the Westinghouse Owner's Group and may bc obtained b'y contacting L'. L Ezekoye at (412) 374-6643 or W. F Moore at (412) 3744351.

Please indicate whether the program is to bc supplied on 3.5 inch diskettes or 5.25 inch diskcttcs.

veci 606.wag 0207961602

Proprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 P /zp 57 APPENDIX A. Page 5 I

Group: AEE USER'S GUIDE FOR PRESLOK HARDWARE/SOFPVARE REQUIREMENTS The program has been written using thc MATHCAD5.0 for Windows program.

This program is available from MathSoft. Inc.

101 Main Street Cambridge, MA 02142 1-800-628-4223 or 617-"577-1017 Fax: 617-577-8829 Thc program is also widely availablc from software vendors.

Thc following hardware and software requirements for running the MATHCAD5.0 for Windows program arc extracted from the User's Guide which is supplied with thc MATHCADprogram:

An 80386 or higher IBM or compatible computer.

A math coprocessor is not rcquircd. but its presence willsignificantly improve pcrformancc.

Microsoft Windows'Version 3.1 or later or Windows NT.

At least 4MB of RAM. All memory above 640K should bc configured as extended memory.

~ >

At least 14MB of free hard disk space for MATHCADfiles.

An additional 1MB on. the hard disk where MATHCADis installed.

At least 8MB of virtual memory.

See the Windows user manual for how to specify virtual memory.

A monitor and graphics card compatible with Windows.

A mouse supported by Windows.

Any printer supported by Windows.

The User's Guide supplied with the MATHCADprogram should be followed for installation of the MATHCADprogram onto your computer.

The scope of this manual is to explain thc usage of thc PRESLOK analysis using the MATHCAD program.

vec1 606.wog 020796 f339

Proprietary Class 2C Verification of'Pressure Locking Analysis Program PRESLOK Project/S.O; No.: WOG-220 Caic. No.: V-EC-1606 APPENDIX A, Page 6 Group: AEE USER'S GUIDE FOR PRESLQK GETTING STARTED The PRESLOK files are supplied to you on either a 3.5 inch or a 5.25 inch diskette.

per your request.

It is recommcndcd that thc first step to use thc files is to copy a "working version" of the files to your hard disk so that the diskette can be retained as a record copy.

The files which are included arc as follows:

prcslokl.mcd MATHCADprogram using the closing valve factor as an input.

prcsiok2.mcd MATHCADprogram using the coefficient of friction between disk and scat as an input.

plinputI.dat ASCII fiilcof input data required by version I of thc PRESLOK program.

plinput2.dat ASCII file of input data required by version 2 of thc PRESLOK program.

The next step to use the program is to create a data filto transfer thc input values for the variables to the PRESLOK analysis program.

The PRESLOK program is expecting these variables to appear in text flic in plain ASCII format with thc riamc "plinputl.dat" for usc with version 1 or "plinput2.dat" for use with version 2. Thc various numbers in the "piinputi.dat" or "plinput2.dat" file can be separated by spaces.

commas. or carriage returns. and may appear as integers. floating point numbers. or as E-format numbers such as 2.35E-2

. An ASCII text filcan be created using thc Windows utility Notepad. or by numerous other methods.

This file should be located in the same directory as thc PRESLOK fiile. since when thc PRESLOK file is loaded.

that directory will become thc MATHCADdefault directory.

The user is also rcfcrrcd to thc chapter on "Data Files" in thc MATHCADUser's Guide iffurther explanation of thc usc of the ".dat" file is needed.

Sample data files arc included in thc program diskette which can be used simply by changing the input values to the proper values for your analysis.

Aitcrnatciy, other file names can bc used for the input data by changing the input file name on ihc page I of thc PRESLOK program to the file name desired.

veci 606.wog 0207961339

Proprietary Class 2C

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Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: O'OG-220 Calc. No.: V-EC-1606

~l 78

."r 5/

V APPENDIX A, Page 7

Group: AEE USER'S GUIDE FOR PRESLOK RUNNING THE PRESLOK ANALYSIS At this point it is assumed that thc user has thc MATHCAD5.0 program loaded onto

,.his computer. and that thc PRESLOK Version 1 or PRESLOK Version 2 file and the "plinputl.dat" or "plinput2.dat" file are available to thc computer in the same directory.

To run thc PRESLQK analysis. the user should perform the following steps:

i.

Double click on the MATHCAD5.0 icon to start the MATHCADprogram.

2.

Go to the File pulldown menu and click on Open {or click on the Open File icon on the Tool Bar.)

3.

In thc Open dialogue box. select thc directory containing thc.presiokl.mcd or

~

presiok2.mcd file and select thc dcsircd version of thc program.

Then click on OK.

4, Thc PRESLOK program willpick up thc input values from the plinputl.dat or plinput2.dat file and perform thc analysis ifthc program is in thc automatic mode (Automatic Mode has a check mark next to it in thc Math pulldown menu-) lfthc MATHCADprogram is not in thc automatic mode, it can be forced to perform thc calculation by clicking on thc Calculate Document function in thc Math pulldown menu.

Results may be inspected by using thc scroll bar on thc right hand side of thc display to scroll through thc display as

" desired.

To change the inputs. open thc Windows utility Notcpad and open thc plinputl.dat or piinput2.dat fil. Make the desired changes to thc file and then save it. To have MATHCADrc-perform thc analysis with thc new input values, open thc Math pulldown menu and click on Calculate Document.

This alternate usc of Notepad and thc MATHCADfunction Calculate Document sSiould bc repeated unul the analysis is correct.

6 Thc output may bc printed using the Print command in the pulldown menu under File or using the print icon in thc Tool Bar.

Thc user is rcferrcd to the MATHCADUser's Guide ifany changes arc desired to the Page Setup or the Printer Setup.

Note that valve idcntifiers or other identifying titles may be added to thc output by using the MATHCADtext entry methods given in thc MATHCADUser's Guide. If the user desires to add thc identifier/title to each page. thc usc of a header is rccommendcd.

The hcadcr can bc defined through the Headers/Footers command in thc Edit pulldown menu or through the Header veci 606.wag 0207961339

f'

gl oi-o7 Propriet'ary Class 2C Verification of Pressure Locking Analysis Program PRESLOK ProjectlS.O. No.: VVOG-220 'alc. No.: V-EC-1606 USER'S GUIDE FOR PRESLOK RUNNING THE PRESLOK ANALYSIS (continued)

APPENDIX A, Page 8 Group: AEE command in the Page Setup dialogue box.

See the Documents and Windows section of the MATHCADUser's Guide for further information about Headers.

7.

Thc program may be exited using the Exit command in thc File pulldown menu.

Sea.t Angle Di'sk Thickness Hub Length FIGURE 1

Disk GEQmetr y vec1606.wog 0207961339

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Verification of Pressure Locking Analysis Program'PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 APPENDIX A, Page.9 Group: AEE USER'S GUIDE FOR PRESLOK INPUT PREPARATION The following inputs are required for the use of the PRESLOK analysis using version 1 of the program:

Pressure Conditions at the time of the pressure locking event.

This includes the upstream. downstream.

and bonnet pressure.

Bonnet Pressure:

Upstream Pressure:

Downstream Pressure:

bonnet Pp Pdomn psl psl psl Valve Disk Geometry.

This includes the hub radius. hub length, mean seat radius. average disk thickness. and seat angle.

Disk Thickness:

Seat Radius:.

Hub Radius:

Hub Leng'th:

Seat Angle:

inches inches inches ble~

inches e

degrees The disk thickness recommended for use in these calculations is the thickness at the centerline of the disk vertically.

See Figure l. This willnormally be.a value which is intermediate between the minimum and maximum thickness of the disk. and this is the thickness which has been used in the comparisons of test measurements which Commonwealth Edison is making with the analytical results.

lt is noted that the magnitude of the pressure locking force increases with the thickness of the disk. so that use of the maximum disk thickness would yield conservative results.

The pressure locking forces predicted by using the maximum value of disk thickness are likely to be unreasonably high though.

The seat radius used in these calculations is the mean seat radius which corresponds to the radius at which one half of the seat area would be outside the mean seat radius and one half of the seat area would be inside the mean radius.

Thus. given the inner and outer seat diameters. the mean seat radius is a--

OD~ + ID~

vec1 606.wag 0207961339

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 i

APPENDIX A, Page 10 Group: AEE USER'S GUIDE FOR PRESLOK When the hub cross-section is not reasonably circular (e.g. many Westinghouse gate valve designs), then an cffectivc hub radius is used which corresponds to a circle of equal area to thc hub cross-sectional area.

Hub Area Thc hub length is thc distance from thc inside face of thc hub to the inside face of thc hub at thc hub radius, as shown on Figurc 1. The seat angle is as shown on Figure l.

0 Valve Disk Material Properties.

This includes the modulus of elasticity and the Poisson's ratio for the disk base material, at thc temperature being con'sidered.

Poisson's Ratio:

Modulus of Elasticity:

Valve Stem Diameter duncnstonless psi Stem Diameter.

Dstem inches This is the stem diameter in thc region of the stem which is inside thc packing.

Static Unseating Thrust Static Pullout Force:

F pounds This is thc static pullout force obtained from testing of thc valve for which the calculation is being performed.

Closing Valve Factor Valve Factor:

dimensionless It.is suggested that this valve factor bc thc factor obtained from test measurements of closing thc valve being considered in a DP test, ifpossible.

To usc version 2 of thc program instead of version 1, thc closing valve factor VF is replaced by thc co-efficient of friction to be considered between the disk and thc seat; and thc input data filis named plinput2.dat. Allother inputs remain the same as for version

1. The different input value is Coefficient of Friction between Disk and Seat Scat to Disk Coefficient of Friction:

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APPENDIX A, Page II Group: AEE USER'S GUIDE FOR PRESLOK THEORY ASSUMPTIONS The valve disk is assumed to act as two ideal, disks connected by a hub.

That i', the disks are assumed to be round, of uniform thickness, and perpendicular to a cylindrical, concentric hub.

A line perpendicular to the hub centerline and at the middle of the hub length is an axis of symmetry for the wedge. The equations in reference 2 for this idealized structure are assumed to conservatively model the actual load due to pressure forces.

This assumption is considered conservative since inspection of the disk drawings show large fillets between the disk hub and seats which should make the valve disk stiffer than assumed in the reference 2 equations.

2.

The coefficient of friction between the valve seat and disk is assumed to be the same under pressure locking conditions as it is under DP conditions.

This assumption is considered to be justified based on bench marking of the calculations against ComEd and EPRI pressure locking test data for similar flex-wedge gate valves.

3.

The upstream, downstream. and bonnet pressure values are considered to be known.

DESIGN INPUTS The following design inputs are used in calculating the force required to unseat a pressure locked MOV:

Pressure Conditions at the time of the pressure locking event.

This includes the upstream, downstream, and bonnet pressure.

Bonnet Pressure:

Pbonnet psl Upstream Pressure:

Pp psl Downstream Pressure:

Pdo n

psl Valve Disk Geometry.

Mis includes the hub radius. hub length, mean seat radius. and average disk thickness.

Disk Thickness:

Seat Radius:

inches inches vec'I 606.wag OZ07961339

hl>- tip- -'~>- y7g gpss 0 Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 57 APPENDIX A, Page l2 Group: AEE USER'S GUIDE FOR'RESLOK Hub Radius:

inches Hub Length:

Hu,lenyh inches Seat Angle:

e degrees Thc disk thickness recommended for use in these calculations is the thickness at the centerline of the disk vertically.

Sec Figurc

1. This willnormally be a value which is intermediate between thc minimum and maximum thickness of thc disk, and this is thc thickness which has been used in thc comparisons of test measurements which Commonwealth Edison is making with the analytical results.

It is noted that the magnitude of the pressure locking force increases with the thickness of thc disk. so that use of the maximum disk thickness would yield conservative results.

Thc pressure locking forces predicted by using the maximum value of disk thickness are likely to be unreasonably high though.

Thc seat radius'sed in these calculations is the mean scat radius which corresponds to thc radius at which one half of thc seat area would bc outside the mean seat radius and onc half of thc scat area would be inside thc mean radius.

Thus, given thc inner and outer scat diameters, thc mean seat radius is OD~ + ID~

8.

When thc hub cross-section is not reasonably circular (e.g. many Westinghouse gate valve designs). then an cffectivc hub radius is used which corresponds to a circle of equ'al area to thc hub cross-sectional area.

b Hub Area The hub length is the distance from the inside face of the hub to the inside face of thc hub at the hub radius, as shown on Figurc I. The scat angle is as shown on Figure I.

Valve Disk Material Properties.

This includes thc modulus of c}asticity and thc Poisson's ratio for thc disk base materiaL Poisson's Ratio:

Modulus of Elasticity:

dimcnsionless pst vec1606.wag 0207961339

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: KOG-220 Calc. No.: V-EC-1606

~J 2/.r zT APPENDIX A Page l3 Group: AEE USER'S GUIDE FOR PRESLOK a~

Valve Stem Diameter Stem Diameter:

Dstem inches This is the stem diameter in the region of the stem which is inside the packing.

Static Unseating Thrust Static Pullout Force:

. F pounds This is the static pullout force obtained from testing of the valve for which the calculation is being performed.

Coefficient of Friction between Disk and Seat Seat to Disk Coefficient of Friction:

p.

dimensionless The analysis program"is presented in two versions, one of which requires ihat the coefficient of friction to be used between the disk and the seat be input directly, and the other which allows the input of the closing valve factor instead.

For. the version which allows the input of the closing valve factor, the coefficient of friction is calculated as follows:

p. = VF-cos 8 l+ V'-me CALCULATIONS The methodology for calculating the thrust required to open the MOVs under the pressure locking scenario is based on the Reference 2 (Roark's) engineering handbook.

The methodology determines the total force required to open the valve under a pressure locking scenario by solving for the four components to this force.

The four components of the force are the pressure locking component. the static unseating component. the piston effect component, and the."reverse piston effect" component.

These magnitudes of these components are determined using the following steps:

veel 606.w09 0207961339

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 gg cP 7g /

57, APPENDIX A, Page 14 Group: AEE USER'S GUIDE FOR PRESLOK Pressure Lockine Com onent of Force R uired to en the Valve The valve disk is modeled as two plates attached at the center by a hub which is concentric with the valve disk. A plane of symmetry is assumed between the valve disks.

This plane of symmetry is considered fixed in the analysis.

Plane OF Symmetr y Modeled As:

Axis of Symmeir y n

Based on this geometry. the following constants are calculated using the reference 2 equations:

Average DP Across Disk Disk Stiffness Constants 2.(1+v) vec1 606.wog 0207961339

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APPENDIX A, Page 15 Group: AEE USER'S GUIDE FOR PRESLOK Geometry Factors C

= 1-1+Z..ln C>

= +1 ln + -1 Cs

= 1+v+(1-v)

C

=

ln +1-Deflection Duc To Prcssure Force Thc prcssure force is assumed to act uniformly upon the inner surface of the disk between the hub diameter and the outer disk diameter.

Thc outcr edge of the disk is assumed to be unimpeded and allowed to deQcct away from the prcssure force.

In addition. the disk hub is allowed to stretch.

The total displacement at the outcr edge of the valve disk duc to shear and bending and duc to hub stretch are calculated using the reference 2 equations.

Corresponding Equations Additional Geometry Factors (ro = b for Table 24. Case 2L) 1+ 4 5 -4 ~ 2+ ln Lt7 = 1-1-

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51 Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: %OG-220 Calc. No.: V-EC-1606 APPENDIX A, Page 16, Group: AEE USER'S GUIDE FOR PRESLOK Moment Factors (ro = b for Table 24. Case 2L)

-DP a~

C9 Mb a~-r> -1.

8 2ab DP Q

~(c~

p~)

Bending Deflection due to Pressure a

DP a~

~by 'rb 2

~b 3

Ii D

D D

Shear Deflection due to Pressure (ro = b for Table 25, Case 2L)

K

= -03

~ 2:1n -1+ 1-21n

'ote:

Since ro b,

1-2.1n = l K

DP

.a~

re Deflection from Hub Stretch due to Pressure P~

= x(u~

b~) DP n'b~

ZE

%otal Deflection due to Pressure

~q

= ~Sq '~ '~b An evenly distributed force is assumed to act between the valve seat and the outer edge of the valve disk. This force acts to deflect the outer diameter of the valve disk inward and to compress the disk hub.

The pressure force is reacted to by an increase veci 606.wog 0207961602

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Verification of Pressure Locking Analysis Program PRESLOK ProjectJS.O. No.: WOG-220 Calc. No.: V-EC-1606 p~ eaoP s7 APPENDIX A, Page 17 Group: AEE USER'S GUIDE FOR PRESLOK in this contact force between the valve disk and seats.

The valve body seats are conservatively assumed to be fixed. Therefore, the deflection due to the known pressure load must be balanced by the deflection due to the unknown seat load.

The deflection due to the pressure force was previously calculated.

Now, the reference 2 equations are used to determine the contact force between the seat and disk which results in a deflection which is equal and opposite to the deflection due to the pressure force.

This is done by first calculating the amount deflection created by a unit load of seat contact force (w =

1 Ib/in). The equilibrium contact load is then determined by dividing the deflection caused by the unit contact load into the previously calculated deflection due to the pressure force.

The equations are provided below:

Additional Geometry Factors (For Table 24. Case 1L, ro = a '3 Lg =0 ro 1+v a

1-v rp I

=

ln +I-a 2

ro 4

Q.

Bending Deflection due to Seat Load

( ro = a for Table 24. Case 1L)

Cz ro. C~

ro Cs

-4

'4 D

Cs b

b-Shear Deflection due to Seat Load (ro = a'for Table 25. Case 1L)

K

= -12 ln Deflection from Hub Compression Due to Seat Load (w = 1,:.Compressive force = 2 z a)

Total Deflection from Unit Seat Load (w = 1) x.=xi +v +r~

veci 6p6.wog 0207961602

Proprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606

~ I 01 APPENDIX A Page 18 Group: AEE USER'S GUIDE FOR PRESLOK I

Therefore, the equilibrium contact load distribution. in pounds per inch, and the corresponding load applied to each seat is calculated using the relationships below:

iv,q~

=

where y~ is calculated for w = I.

x W

Note that the sign of the equilibrium contact load is positive.

This is because the sign conventions of Reference 2 have been maintained for all of the calculations, resulting in both the pressure load analysis and the line load analysis giving negative deflections, even though the loads and defections for the line load case are phyically in the opposite direction from the loads and deflection for the pressure load case.

The load per seat is then given by Determinine The Disk To Seat Friction Coefficient Several methods. can be used to determine an appropriate seat to disk friction coefficient.'he coefficient of friction between the seat and disk is perhaps best determined based on the opening valve factor from a DP test.

However, due to the difficultysometimes encountered in obtaining a good, consistent value of the opening valve factor from testing, the PRESLQK program is written to accept either a closing valve factor or a co-efficient of friction directly. The equation used to calculate the coefficient of friction from the closing valve factor is given in the Design Inputs section of this User's Manual.

The stem force required to overcome the contact load between the seat and disk which opposes the pressure force is equal to the following, considering two disk faces:

F~

= 2.;Fs'p'coso sino S tatic Unseatin Force The static unseating force represents the opening packing load and the pullout force due to wedging of the valve disk during closure.

These loads are superimposed on the loads due to the pressure forces which occur during pressure locking. The value for this force is based on static test data for the MOVs, and is one of the inputs to the program (Fg.

vec1 606.wag 0207961339

P roprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK ProjectJS.O. No.: WOG-220 Calc. No.: V-EC-1606 I y1 APPENDIX A, Page 19 Group: AEE USER'S GUIDE FOR PRESLOK Piston Effect The piston effect due to valve internal pressure cxcecding outside pressure is calculated using the standard industry equation.

This force assists movement of the valve stem in thc open direction.

\\

Reverse Piston Effect The reverse piston effect is thc term used in this calculation to refer to the pressure force acting downward against thc valve disk. This force is equal to the differential pressure across thc valve disk times thc area of the valve disk times thc sine of the seat angle times 2 (for two disk faces).

F'ma sin0(2P~.-P

-P

}

Bonnet Pr essure Upstream Pr essur e Downstrean Pressure Seat Angle Bonnet Pr essur e Total Force Re uired to Overcome Prcssure Lockin As mentioned previously, the total stem force (tension) rcquircd to overcome pressure locking is the sum of the four components discussed above.

Allof the terms are positive with the exception of the piston effect component.

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igg 0 Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 pp o3 oF >7 APPENDIX A, Page 20 Group: AEE USER'S GUIDE FOR PRESLOK EXAMPLE OF AN ANALYSIS PERFORMED WITH PRESLOK, VERSION I The following is an image of thc input file plinputl.dat used to run an example problem on version 1 of the PRESLOK analysis program:

1005 '80 350 2

4.36 0.3 27.6E6 1.875 15409 0.52 1.25 0.5 Thc input file corresponds to input values as shown:

Bonnet Prcssure:

Upstream Pressure:

Downstream Pressure:

Disk Thickness:

Seat Radius:

Hub Radius:

Hub Length:

Seat Angle:

Poisson's Ratio:

Modulus of Elasticity:

Stem Diamctcr:

Static Pullout Force:

Valve Factor:

Pb t = 1005 psi Pup 380 'psi Pd

= 350 psi t = 2.00 inches a:= 4.36 inches b'= 1.25 inches L".= 0.50 inches e = 5 dcgrces v =0.3 E = 27,600.000 psi Dst m 1.875 inches (dimensionless)

F>0 = 15.409 pounds VF = 0.52 (dimensionless)

Thc next fivpages contain the output of thc PRESLOK program, Version l. using the above input.

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Proprietary Class 2C

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I Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: O'OG-220 Calc. No.: V-EC-1606

p. goo~ >7 APPENDIK A, Page 21 Group: AEE USER'S GUIDE TO PRESLOK Program PRESLOK, Version 1 Revision 0 December 22, 1995 This Mathcad Program is designed to calculate the estimated opening force under pressure locking scenarios for flex-wedge gate valves using a calculational methodology that accounts for wedge stiffness resisting pressure locking forces.

This program was prepared by the Westinghouse Owner's Group based upon the calculational methods developed by Commonwealth Edison.

While this information is presented in good faith and believed to be accurate, the Westinghouse Owner's Group does not guarantee satisfactory results from reliance upon such information. Nothing contained herein is to be construed as a warranty, express or implied, regarding the performance, merchantabiiity, fitness or any other matter with respect to the product, nor as a recommendation to use any product or process in conflict with any patent.

The Westinghouse Owner's Group reserves the right, without notice, to alter or improve the methods described herein.'his section of the program reads the thirteen items of input data from the plinput1.dat file.

i:= 0..12 input,:= READ(plinputl )

bonnet 'Put0 Psi P up.'= input> psi P down inPu2 Psi t:= ulput3'in a:= input4 in b:= ulput5 In Hub length.= mput6 e:= input> deg v:= ulputs E:= lnput9 psl stem'pu to'~

F:= input<< lbf VF:= input>>

PRESLOK, Vcr. l, Rn. 0 12!22/95 W<sriaghousc'Owner's Group 2/8/96 /0:lO:OSAM Page l of5

pp,h, R<d 5 Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: DOG-220 Calc. No.: V-EC-1606 p) aso.

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APPENDIX A, Page 22 Group: AEE USER'S GUIDE TO PRESLOK Program PRESLOK, Version 1 INPUTS:

Bonnet Pressure Upstream Pressure Downstream Pressure bonnet 1005 'psi P =380 pst P d

=350'psi Disk Thickness (taken at centerline of the hub vertically)

Seat Radius (corresponding to mean seat diameter)

=2 1I1 a.'=4.36 in Hub Radius (taken at plane of symmetry,

. perpendicular to the hub, radius of circle of equivalent area for non-circular hubs)

Seat Angle Poisson's Ratio (disk material at. temperature) b = 1.25.in 8 =5 deg v =0.3 Modulus of Elasticity (disk material at temperature)

E:.=2.76 10 psi 7

Static Pullout Force (measured value from diagnostic test)

F

= 15409 'lbf po Close Valve Factor Stem Diameter VF =0.52 D stem

-1.875 in Hub Length (from inside face of disk to inside face of disk)

Hub length =0.

PRESLOK. Ver. l. Rn. 0 l2/22/95 Westinghouse Owner's Group 2/8/96 l0:l0:l2 AM Page 2 of5

51-HE Ib 07/n g~g g Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606

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APPENDIX A Page ~3 Group: AEE USER'S GUIDETO PRESLOK Program PRESLOK, Version 1 PRESSURE FORCE CALCULATIONS Coefficient of friction between disk and seat:

cos(e)

IL. = VF I ~VF s~{e)

Average DP across disks:

Up down P bonnet 2-Disk Stiffness Constants E'(t) 12 1-v IL =0.496 DPavg =640 psi.

D =2.022 10

~ Ibfh 7

2.'{ I + v)

Geometry Factors:

I b

a C2'.= 1- ~ I+ 2 In 4

a b

G' 1.062 10 psi 7

C 2 =0.1781 b"

b a

b C3'= ~1

~In + - I 4a a

b a

C 3 =0.0311 I

b 2 C8.= 1 ~v+ (1 v)~

2.

a C 8 =0.6788

b. I+-v a

I-v b 2 C 9 In ~

I a

2 b

4-a C.9 =0.2789 a.

L 3-'=

4a a'

a'1

-In + - I a

a a

L3 =0 2.

L9 '.=

-In ~

I PRESLOK. Ver. /. Rcv. 0 /2/22/95 Westinghouse Owner's Group L9 =0 2/8/96 l0:l0:24 AM Poge3 of>

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b b

b a

L:=I + 4 5 4

~ 2+

In 64 a

a a

a b

L 11 =0.0069 I

I,v b

b a

L

= 1-.I -

~ I+(1+v)~In 17 4.

4.

a a

b L. 17 =0.1526 Moment

(

b )-L

,C C.

2ab '

M b =-5265-Ibf t

DPavg Qb

=

-(a -b) 2b Ibf Q b =4466.5' U1 Deflection due to pressure and bending:

a' DPavg a y bq

'.= M z D-C 2 "Q b

-C 3

-L 11

-4 y bq =-3.9041 10 in Deflection due to pressure and shear stress:

a b

K:= -0.3 2 In I sa' a

Ksu < 4743 Ksa DPavg a ysq'=

t.G r

Deflection due to hub stretch:

y sq --2.7177.10

.in orce(a b ) DPavg force gth stretch '

u t h =6.4731 10 in Total Deflection due to pressure forces:

yq:= ybq ~ y<- ystretch PRESLOK, Ver. I. Rn. 0 12122/95 W'c'sringhousc'wner's Group I

4 y

=-7.2691 10 in:

q 2IBI96 l0:l0:37AM Page4of5

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Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-ZZO Calc. No.: V-EC-1606 g~ ='5."'7 APPENDIX A, Page 25 Group: AEE USER'S GUIDETO PRESLOK Program PRESLOK, Version 1 Deflection due to seat contact force and shear stress (per Ibf/in.):

ysw'2.

In a tG

-7 ln'

=-3.079 10 (tbf)

Deflection due to seat contact force and bending (per Ibf/in.):

a'.

ybw' C2 C8 aC9 -L9 b

a.C3 ~L3 b

7 I y b

=%.012e 10 tbf)

Deflection due to hub compression:

y cmpr '=

2:z.a Hub length xb E

-8 ln y

=-5.055.10 cmpr lbf Ilt Total deflection due to seat contact force (per Ibf/In.):

Seat Contact Force for which deflection is equal to previously calculated deflection from pressure forces:

yq F:=2za-s yw UNSEATING FORCES Fpacklng is included in measured static pullout Force

-7 lit y

=+.597 10 w

(~)

F s 207505 lbf piston '

stem bonnet Fpiston 2775 lbf

~

, 2.

+vett

~~

~'( 'onnet op down)

Fve t 6662.4 lbf F preslock F s'(g cos(e) - sin(e))

total 'iston ~

vert "

preslock ~

po reslock Fpo =15409 lbf F total =36167.4 Ibf PRESLOK. Vrr. l, Rcv. 0 l2/22/95 Wc'ssinghousc'wru'r s Group 2/8/96 lO:lO:49 AN Page 5 of5

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<e.d d Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Cate. No.: V-EC-1606 pj's 97 g! ~7 APPENDIX A, Page 26 Group: AEE VSER'S GVIDE FOR PRESLOK EXAMPLE OF AN ANALYSISPERFORMED WITH PRESLOK, VERSION 2 The following is an image of the input file plinput2.dat used to run an example problem on version 2 of the PRESLOK analysis program:

1005 0.3 380 350 2.

4.36 27.6E6 1.875 15409 0.496 1.25 0.5 The input file corresponds to input values as shown:

Bonnet Pressure:

Upstream Pressure:

Downstream Pressure:

Disk Thickness:

Seat Radius:

Hub Radius:

Hub Length:

Seat Angle:

Poisson's Ratio:

Modulus of Elasticity:

Stem Diameter:

Static Pullout Force:

Seat to Disk Coefficient of Friction:

Pbonoet =1005 p

'p

380 psi Pdown = 350 psi t = 2.00 inches a.= 4.36 inches b;= 1.25 inches L'= 0.50 inches 8 = 5 degrees v =0.3 E = 27,600.000 psi stem

1 875 inches (dimensionless)

Fpo 1 5 409 pounds

p. = 0.496 (dimensionless)

The next five pages'ontain the output of the PRESLOK program. Version 2. using the above input.

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USER'S GUIDE FOR PRESLOCK Program PRESLOK, Yersion 2 Revision 0 December 22, 1995

)

This Mathcad Program is designed to calculate the estimated opening force under pressure locking scenarios for flex-wedge gate valves using a calcutational methodology that accounts for wedge stiffness resisting pressure locking forces. This program was prepared by the Westinghouse Owner's Group based upon the calculational methods developed by Commonwealth Edison.

While this information is presented in good faith and believed to be accurate, the.

'estinghouse Owner's Group does not guarantee satisfactory results from reliance.

upon such information. Nothing contained herein is to be construed as a warranty, express or implied, regarding the performance, merchantability, fitness or any other matter with respect to the product, nor as a recommendation to use any product or process in conflict with any patent.

TheWestinghouse Owner's Group reserves the right, without notice, to alter or improve the methods. described herein.

This section of the program reads the.thirteen items of input data from the plinput2.dat file.

i:= 0.. 12 input.,:= READ(plinput2) bonnet 'Putp Psi P := ulput> psl down 'Pu 2'P+

t:= ulput> ul a:= input4 in b:= lnput5 I Hub length ';inputs h e:= input.deg V:= Ulput8 E:= input> psl D s+m.= ulPut<p'ln Fpo

= input< t lbf JL:= ulPut)2 PRESLOK. Ver. 2, Rn. 0 12/22!95 tVesu'nghouse Owner's Group 2/8/96 l0:l9:37AM Page l of5

li -o I H~o0 Proprietary Class 2C Verification of Pressure Locking Anaiysis Program PRESLQK Project/S.O. No.:.%OG-220 Calc. No.: V-EC-1606

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APPEND1X A, Page 28 Group: AEE USER'S GUIDE FOR PRESLOCK Program PRESLOK, Version 2 INPUTS:

Bonnet Pressure Upstream Pressure Downstream Pressure P bonnet 1005 'psi P up 380.psi pdo

=350 p" Disk Thickness (taken at centerline of the hub vertically)

Seat Radius (corresponding to mean seat di'meter) t=2 ln a.=4.36 in Hub Radius (taken at plane of symmetry, perpendicular to the hub, radius of circle of equivalent area for non-circular hubs)

Seat Angle Poisson's Ratio (disk material at temperature)

Modulus of Elasticity (disk material at temperature) b =1.25.in

.9-=5 deg v =0,3 E=2.76.10

.psi 7

Static Pullout Force (measured value from diagnostic test)

Coefficient of Friction between disk and seat:

Stem Diameter F'1 p =0.496 D, te

-1.875.in Hub Length (from inside face of disk to inside face of disk)

Hub length =0.5 in PRESLOK. Ver. 2. Rrv. 0 I2/22/95 Wesunghouse Owner's Group 2/8/96 l0:l9;41 AM Page 2 of5

0

Proprietary Class ZC t

Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 J-az o F'

/

APPENDS A, Page 29 Group: AEE USER'S GUIDE FOR PRESLOCK Program PRESLGK, Version 2.

PRESSURE. FORCE CALCULATIONS Average DP across disks:

up ",'own DPavg:= P bonnet 2.

Disk Stiffness Constants E (t) 12 I-v DPavg = 640.psi D =2.022 10

'Ibfin 7

2.(l ~ v)

Geometry Factors:

1 b

a C 2:= I -

~ I + 2-ln 4

a b

G = 1:062.10 psi 7

C 2.-0.1781 b

b a

b C3.- t-I h + I 4a a

b a

C 3 =0.0311 I

b 2 C 8.'= I + v+(I v)-

2 a

C:8 =0.6788 b I+v a

Cg '=

ln-a 2.,

'b I-v b 2 I-a C'9 =0.2789 a

a a

a.

L3.=

+ I In ~ - I 4a a

a a

L3 =0 a I+v a

I-v a 2 L 9.--

In +

I a

2 a'-

a L9 =0 PRESLOK, Vcr. 2. Rcv. 0 /2/22/95 Wcstinghousc Owner's Group 2/8/96 /0:19:52 AM Page 3 of5

LIft-HF- ')i -D')b Qe.aO Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606

+n< ~'9 ()I g I I/

APPENDIX A, Page 30 Group: AEE USER'S GUIDE FOR PRESLQCK Program PRESLOK, Yersion 2 Geometry Factors: (continued)

I b

b b

b a

L:=I ~4 5 4.

~ 2+ In

.64 a

a a

a b

L. 11 =0.0069 I

I-v b

a L:=I -

I -

I ~(I ~v) In 17'.'.

a a

b L.17 =0.1526 Moment M

'DPavg a 9 (a b~) -'L C

C' ab 8

I, M b =-5265

~Ibf r

DPavg

() b:=

'(n b )

2:b Ibf Q b =4466.5 Deflection due to pressure and bending:

a.

DPavg-a

.4 ybq.'= Mrb.C2.+QbC 3- 'L 11 D

D

-4 yh =-3.9041 10

'in Deflection due to pressure and shear stress:

a b

K:=-0.3 2 In - I+

sa.'

b a

K

=.4743 Ksa DPavg.a t-G y <,=-2.7177.10

.in Deflection due to hub stretch:

"force 'x'(a - b ).DPavg force

" length smtch

2

{2.E)

"stretch Total Deflection due to pressure forces:

yq:- ybq ~y<- ystretch PRESLOK, Ver. 2. Rnr. 0 12I22I95 Wc'ssinghousc Owner's Group y

=-7.2691 1,0 in 2IBI96 IO:20:05 AM Page 4 of5

Ql'-,- I'0'- -tt, -07L.

<e3 0 Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 Pe)

F: =20750.5'lbf s

F'ston =2775 Ibf F'vcrt'= n' h~ ~'( 'onnet up down)

~prcsiock'=

~l.cos(e) s~(e))

total 'iston vert ~Fprcslock po Fve~

6662.4 'bf F

I k -16889.1 lbf F'

15409 lbf po F to&

36185 5 lbf PRESLOK. Vcr.2. Rcv. 0 /2/22/95 Wessinghousc Owns.r's Group 2/8/96 10:20:/7 AM Page 5 of5

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 pp g5 OI-S7 APPENDIX A, Page 32 Group. AEE USER'S GUIDE FOR PRESLOK REFERENCES Bunte. Brian, "ComEd Pressure Locking Methodology and Test Program."

presented at the NRC Region 3 Workshop on Prcssure Locking and Thermal Binding, November 7; 1995.

Roark. Raymond J., and Young, Warren C., Formulas for Stress and Strain. Fifrh Edin'on, McGraw-Hill Book Company, 1975.

3.

Liberal use has also been made of a draft of a report being prepared by Mr. Brian Buntc of Commonwealth Edison Company, tentatively titled "Prcssure Locking ffhctmal Binding Report."

veci 606.wag 0207961339

hy - I'PE 9/~-o 7>

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606

'pp Q or

"~j APPENDIX B, Page l Group: AEE, Program PFlESLOK, Version 1 Revision 0 December 22, 1995 This Mathcad Program is designed to calculate the estimated opening force under pressure locking scenarios for flex-wedge gate valves using a calculational methodology that accounts for wedge stiffness resisting pressure locking forces. This program was prepared by the Westinghouse Owner's Group based upon the calculational methods developed by Commonwealth Edison.

While this information is presented in good faith and believed to be accurate, the Westinghouse Owner's Group does not guarantee satisfactory results from reliance upon such information. Nothing contained herein is to be construed as a warranty,

~ express or implied, regarding the performance, merchantability, fitness or any other matter with respect to the product, nor as a recommendation to use any product or process in conflict with any patent.

The Westinghouse Owner's Group reserves the right, without notice, to alter or improve the methods described herein.

This section of the program reads the thirteen items of input data from the plinput1.dat file.

i:= 0..12 input;:= READ(plinputl) bonnet 'Puo. Psi P up ltlPut< Psl down'nPu2'P~

t:= lnput3-in a:= lnput4 ln b:= lnput5 in length

= IP" 6'~

e.:= input deg v:= mputs E:= ulput> psl stem 'put<0 F'po '= input().lbf VF:= input>>

PRESLOK. Vcr. /, Rnr. 0 /2/22/95 ti/cs/in//bout Owmr's Group 2/8/96 9:57:10 AM Page'/ of6

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK

'roject/S.O.

No.: WOG-ZZO Calc. No.: V-EC-1606 py< H7 ol

>7 APPENDIX B, Page 2 Group: AEE Program PRESLOK, Version 1 lNPUTS:

Bonnet Pressure Upstream Pressure Downstream Pressure bonnet

'Pst P up 200 psi P d

-500 pst Disk Thickness (taken at centerline of the hub vertically) t = 1.7.in Seat Radius (corresponding to mean seat diameter)

Hub Radius (taken at plane of symmetry, perpendicular to the hub, radius of circle of equivalent area for non-circular hubs)

Seat Angle Poisson's Ratio (disk material at temperature)

Modulus of Elasticity (disk material at temperature)

R.=7 'Hl b =1.1 in e =9'dcg v =0.31 E = 2.9.10 psi 7

Static Pullout Force (measured value from diagnostic test)

Close Valve Factor Stem Diameter F

=23000 lbf po VF =0.47 D stem ='9 I Hub Length (from inside face of disk to inside face of disk) length PRESLOK, Vcr. I. Rcv. 0 12!22I95 N'csfinghousc Owner's Group, 2I8I96 9:5T:l4 AM Page'2 of6

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: O'OG-220 Calc. No.: V-EC-1606 P) ~g ~~ a7 APPENDIX B, Page 3 Group: AEE Program PRESLOK, Version 1 PRESSURE FORCE CALCULATlONS Coefficient of friction between disk and seat:

cos(e)

It:= VF 1+ VF.sin(e)

Average DP across disks:

up down bonnet 2.

Disk Stiffness Constants E'(t) 12; 1-v

p. =0.432 DPavg = 950.psi D = 1.314 10 Ibf in 7

E.

2(1~v)

Geometry Factors:

G =1.107 10 psi 7

C2.'

't 2ln C 2 =0.221 b-b a

b C3. t 1

In ~ I 4a a

b a

C 3 =0.0362 1

2 C8.= 1+ v+ (1 v)~

2-a C 8 =0.6635' 1 +-v a

I v b 2 C'9.'=

In t.

I a.

2 b

4-a C 9 =0.2169 a-L3 '.=:

4.a a 2 a

a' I

In ~ - I a

a a

L.3 =0

a. I+v a

I-v a 2 L9 '.=

-In +

1 -

a.

2, a

4-a PRESC.OK. Ver. I. Rn. 0 l2/22/95 Wc'sringhouse Owner's Group I

L9 =0 2/8/96 9:57:26 AM Page 3 of6

Qf)- ME g/ - g7(r Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No. HOG-22D Caic. No.: V-EC-1606 i'(j" av o

S'7 APPENDIX B, Page 4 Group: AEE Program PRESLOK, Version 1 Geometry Factors: (continued)

I b

b b

b a

L

'=.1~4 -5. -4 2+

~In 64 a

a a

a b

L 11 -0 01,13 I

I-v b

b a

L 17'= I I

~ I+(1+v) In 4

4 a

a b

L 17 =0.1858 Moment M:--Dpavga 9 (a2-b2) -L

.2 C

M

=-34193.2 'Ibf rb DPavg 2

2 Q b.=

(a-b )

Z.b Q b =20636.6.

Ibf Deflection due to pressure and bending:

a' DPavg a ybq.rb.C2+Qb C3

-L 11 D

D D

y i

=<.0107.in Deflection due to pressure and shear stress:

a b

K:=-0.3 2 In I ~

sa Ksa =<8178 K~-DPavg a y

t.G y

=<.002 in Deflection due to hub stretch:

P force'r-(a b ) DPavg force length "snatch 2 '2.E) y stretch ="8"

'otal Deflection due to pressure forces:

yq:= ybq ~ y<- ystretch PRESLOK, Vc'r. /, Rnr. 0 12/22/95 Wc'stinghouso Owner's Group y q =<.0131.in 2/SI96 9.57.39 AM Page 4 of6

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: 8'OG-220 Calc. No.: V-EC-1606 APPENDIX 8, Pa<<S Group: AEE Program PRESLOK, Version 1 Deflection due to seat contact force and shear stress (per Ibf/in.):

ysw' a

1.2 ln a a

b tG 7

ln ys 261 10 ibf)

Deflection due to seat contact force and bending (per lbf/in.):

3 ybw D

C2 aC9 a

L9 -

C3 wL3 C8 b

b ybw = 5.992.10 ~-

(iM)

Deflection due to hub compression:

y cmpr '=

2:n a Hub length 2:

F

-7 lit y

=-1.197 10 cmpr lbf ln Total deflection due to seat contact force (per lbf/in.):

yw:=ybw~ysw ~y~pr Seat Contact Force for which deflection is equal to previously calculated deflection from pressure forces:

F:=Zna-yq s'w-y

=+.938 10

(-.)

F.s =82848.8 'lbf UNSEATlNG FORCES FpaekIng is included in measured static pullout Force piston' stem 'onnet Fpiston 3685 9 Ibf F.~~<'.= ma sinia) (2Pb

~- P - P'~o~)

Fvert 45754.3 1bf

+preslock 'F s'(I cos(8) - sh(8))

total 'iston ~Fvert ~

preslock po F reslo I =44848 lbf Fpo = 23000'lbf F toM 109916 5 Ibf PRESCOK, Ver. /. Rnr. 0 /2/22/9$

Westinghouse Owner's Group 2IB/96 9:$7:$2 Ahf Page'5 of6

o7'g gq() o P) 5 I oi- ~7 Proprietary Class 2C APPENDIX B, Page 6 Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 'roup: AEE This page has been added to present the PRESLOK1 outputs for verification. The only change is to display more significant digits of the calcualted numbers.

p. = 0.4324202.

DPavg =950 psi D =1.314 10 Ibf in G =1.107 10 psi 7

C 2 =0.2209773 C 3 =0.0361818 C 8 =0.6635194 C 9 =0.2169174 L3 =0 L9 =0 L11 =0.0113379 L 17 =0.1857616 Mrb =

1 3 18999 lbf Q b =20636.591 Ibf

-7 lil y

=-8.261.10 sw lbf ill ln' y b 5.992 10 Ibf y~>'=-1.196922'10 (iur) ill yw =+.938 10 i~)

s = 82848 814'Ibf Fpiston 3685e87 Ibf Fvca =45754.31 Ibf F.prcslock 44848.03 lbf y h =.01065772

~in Ks~=.8177681 y

=.002023039 in sq y stretch =3.8814905.10 in y q =.0130689l in Fpo 23000 lbf Ftoul I09916.47 'Ibf PRESLOK. Vcr. i. Rcv. 0 12/22/95 Wesunghouse Owner s Group 2/8/96 9:58:00 AM Page 6 of6

Proprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK ProjectJS.O. No.: WOG-220 Calc. No.: V-EC-1606

+"-.I ~~

Ot 57 sfAPPENDIX C Page I Group: AEE Program PRESLOK, Version 2 Revision 0 December 22, 1995 This Mathcad Program is designed to calculate the estimated opening force under pressure locking scenarios for flex-wedge gate valves using a calculational methodology that accounts for wedge stiffness resisting pressure locking forces. This program was prepared by the Westinghouse Owner's Group based upon the catculational methods developed by Commonwealth Edison.

While this information is presented in good faith and believed to be accurate, the Westinghouse Owner's Group does not guarantee satisfactory results from reliance upon such information. Nothing contained herein is to be construed as a warranty, express or implied, regarding the performance, merchantability, fitness or any other matter with respect to the product, nor as a recommendation to use any product or process in conflict with any patent.

The Westinghouse Owner's Group reserves the right, without notice, to alter or improve the methods described herein.

This section of the program reads the thirteen items of input data from the plinput2.dat file..

i:= 0.. 12 input,:= READ(plinput2)

P bonnet 'nput< psi P up

= inPutt. Pst P down '= mPuq Psi t:= upput. In a.:= mput4.1n v-:= Input8 E:= mput9 ps1 D st:= mput)p'ln Fpo inputt < lbf p.:= input>>

b:= u1put> In Hub ien~:= mput6'ul e:= input deg PRESLOK. Ver. 2. Rn. 0 12/22/95 Wc'ssinghousc'wner's Group 2/8/96 9:55:42 AM Page / of6

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK ProjectlS.O. No.: WOG-220 Calc. No.: V-EC-1606

~c -3 a~ 57

~ I APPENDIX C, Page 2 Group: AEE Program PRESLOK, Yersion 2.

INPUTS:

Bonnet Pressure Upstream Pressure Downstream Pressure P bonnet =1300'psi P=200 psi lip Pd ~n =500.psi Disk Thickness (taken at centerline of the hub vertically) t =1.7 in Seat Radius (corresponding to mean seat diameter)

Hub Radius (taken at plane of symmetry, perpendicular to the hub, radius of circle of equivalent area for non-circular hubs)

Seat Angle R.=7 'In b-= 1.1.in e:=9 dcg Poisson's Ratio (disk material at temperature) v =0.31 Modulus of Elasticity (disk material at temperature)

F = 2.9.10

.psi 7

Static Pullout Force (measured value from diagnostic test)

Coefficient of Friction between disk and seat:

Stem Diameter F-

=23000 Ibf po

p. = 0.432 D sum 1.9.in Hub Length (from inside face of disk to inside face of disk)

Hub Ien~ =0.6'in PRFSLOK, Ver. 2, Rcv. 0 12I22I95 Ncsiinghousc Owner's Group 2I8I96 9:55:46 AM Page 2 of6

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLQK Project/S.O. No.: FOG-220 Calc. No.: V-EC-1606

~ seo/- S7 APPENDIX C, Page 3 Group: AEE Program PRESLOK, Version 2.

PRESSURE FORCE CALCULATIONS Average DP across disks:

up" down "g '=

bonnet 2

Oisk Stiffness Constants E..(t)

12. I - v DPavg = 950.psi D = 1.314'10 ibf in 7

?.(I+ v)

Geometry Factors:

I 'b:

a C2.'= I ~ 4 t Z..ln 4

a b

G =1.107 10 psi 7"

C2 =0.221 b

b a

b C.3.-- + I ln +.I 4a, a

b a

C 3 =0.0362 I

b 2 C 8.= I+ v+ (I - v)~

2.

a CS =0.663 b-I ~v a

I--v

b. z C'9 '.=

In ~

1 2.

b 4

a C.9 =0.2169 a

a a

a.

L.3.==

~1 In + I 4a a

a a

L.3 -0 2

L9 =

h +I-L9 =0 PRESLOK. Ver. 2, Rcv. 0 /2/22/95 Wcssinghousc Owtu:r's Group 2/8/96 9:55:58 AM Pog<3 of/s

- H =-- g/ - g 7/,

~

Proprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK.,

Project/S.O. No.: WOG-220 Calc. No.: V-EC-1606 ss~r APPENDIX C~ Page 4 Group: AEE Program PRESLOK, Yersion 2 Geometry Factors: (continued)

I b

b b

a L:=I+4 5 4. - 2~

ln 64 a

a a

a b

I 11 =0.0113 I

I

~ I+ (I+ v)

~ln I

I-v b

b a

17'= 4.

4.

a a

b L.17 =0.1858 Moment M:= - Dpavg a'

.(,2 b2) - L 2

C rb '

2 b

17 8

M b = 34193 2 Ibf rb DPavg 2

2 gb.=

(a -b) 2:b lbf Q b =20636.6-Deflection due to pressure. and bending:

a DPavg a yh '= Mrb.C2+ Q b

-C 3 L 11 D

D D

y b

=<.0107 in Deflection due to pressure and shear stress:

a b

K:=-0.3 2 In I ~

Sa-'

a K.sa =<.8178 Ks~DPavg a y~ =%.002 in Deflection due to hub stretch:

P force.= m (a b ) DPavg "stretch '

force Hub length (2:E) y tr h

3.8815 10 in Total Deflection due to pressure forces:

y q

.:= y< ~-y sq - y stretch PRESLOK. Vcr. 2, Rcv. 0 /2/22/95

~

Ncstinghousc'wner's Group y

=.0131 in 2/8/96 9:56:/2 Ahf Pagt 4 of6

gQ 0F. -'1!

$ '/L ke.d 0

~

Proprietary Class 2C Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. Noel WOG-220 Calc. Noel V-EC-1606

!pq ~/ o/ S7 APPENDIX C, Page g

~

Group: AEE Program PRESLOK, Version 2

'eflection due to seat contact force and shear stress (per lbf/in.):

ysw '=

a a

12.In.a a

t.G

-7 ill y

=-8.261.10 sw lbf Deflection due to seat contact force and bending (per Ibffin.):

a3 ybw'=

C2 C8 a.C g-Lg b

a-C3

+ L3 b

yb 5992 10 Ul' lbf ln Deflection due to hub compression:

y cmpr '='.z.a Hub length ebz e

-7 In y

=-1.197 10 clllpr Ibf Hl Total deflection due to seat contact force (per lbf/in.):

yw'= ybw "sw~'ycmpr Seat Contact Force for which deflection'is equal to previously calculated deflection from pressure forces:

yq F:=2@a-s'w UNSEATlNG FORCES FpacI6ng is included in measured static pullout Force K"

z" piston '

stem 'onnet y w

+.938 10 w 'f)

F-s =82848.8 Ibf F piston

'3685 9 Ibf

.2..

+vett '

tn

~ (

bonnet np

+down)

F~ =45754.3 Ibf F rcslock' Fs'{icos(e) sin(e))

k=44848 lbf total 'iston ~

vert ~

prcslock po F total 109916.5 Ibf PRESLOK. Ver. 2. Rev. 0 12/22/95 Wcsringhousc'wner's Group F

=23000.lbf 2/8/96 9:56:25AM Page'5 of6

Proprietary Class ZC Verification of Pressure Locking Analysis Program PRESLOK Project/S.O. No 'OG-220 Calc. No.: V-EC-1606 APPEND1X C, Page 6 Group: AEF This page has been added to present the PRESLQK2 outputs for verification. The only change is to display more significant digits of the calcualted numbers.

p = 0.4324202 DPavg =950 psi D = 1.314'10 lbf in 7

G =1.107 10 psi 7

C 2 =0.2209773 C 3 =0.0361818 C 8 =0.6635194 C 9 =0.2169174 L3 =0 L9 =0 L 11 =0.0113379 L 17 0.1857616 M rb =

4 3.18999.lbf Q b -20636.591-Ibf

-7 Ul ysw = 8.261 10 Ul y

=-5.992. 10 bw lbf 7'l y

=-1.196922 10 clllpr lbf Ul

'w

=W.938 10 lbf Ul F'82848.814 lbf F piston 3685 87 lbf Fve~ =45754.31 lbf F.pmslock = 44848.04. lbf y b=<.01065772 in K sa =.8177681 y sq =.002023039

~in y stretch y q =<.01306891.Ul

~ r Fpo 23000 lbf

+toul 109916.47 lbf PRESLOK, Ver. 2. Rn. 0 /2/22/95 Wesringhouse Owner s Group 2/8/96 9.56.33 AM Page 6 of6

Ilnput

'P-bonnet IP-Up

,P-down tt a

b b/

I-hub theta rheta-rad poison e

dstem Fpo Vf TEST 1005 380 350 2

4.36 1.25 0.286697248 0.5 5

0.087266461 0.3 27600000 1.875 15409 0.52 V852A 2250 30 0

1.536 2.789 1.5 0.537827178 OA375 5

0.087266461 0.3 29000000 1.75 11000 0.66 V852B 2250 30 0

1.536 2.789 1.5 0.537827178 0.4375 5

0.087266461 0.3 29000000 1.75 11000 0.66 NOTES Bonnet pressure (psi)

Upstream pressure (psi)

Downstream pressure (psi)

Disk Thickness (in)

Seat radius (in)

Hub Radius (in)

Seat to Hub Radius Ratio Hub lenght (in)

Seat angle (deg) rad Poisson'atio (disc material)

Modulus of Elasticity (psi)

Steam Diameter (ln)

Static Pollout Force (Ibs)

Valve factor mu dpavg D

G C2 C3 0.49556189 640 20219780.22 10615384.62 0.178106699 0.031121901 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 0.621725137 Coeff. of Friction between disk &seat 2235 Average DP Across Disk (psi) 9623853.574 Disk Stiffness Constant 11153846.15 Disk Stiffness Constant 0.08798395 Geometry Factors. Roark, Table 24 0.011950404 Geomet Factors. Roark, Table 24 Input P-bonnet P-up P-down t

a b

b/a I-hub theta rheta-rad pol e

d.

Fpo Vf TEST 1005 380 350 2

4.36 1.25 0.286697248 0.5 5

0.087266461 0.3 27600000 1.875 15409 0.52 V852A 2250 30 0

1.536 2.789 1.5 0.537827178 OA375 5

0.087266461 0.3 29000000 1.75 11000 0.66 V852B 2250 30 0

1.536 2.789 1.5 0.537827178 0.4375 5

0.087266461 0.3 29000000 1.75 11000 0.66 NOTES Bonnet pressure (psi)

Upstream pressure (psi)

Downstream pressure (psi)

Disk Thickness (in)

Seat radius (in)

Hub Radius (in)

Seat to Hub Radius Ratio Hub lenght (in)

Seat angle (deg) rad Poisson'atio (disc material)

Modulus of Elasticity (psi)

Steam Diameter (in)

Static Pollout Force (Ibs)

Valve factor mu dpavg D

G C2 C3 CB C9 L3 L9 L11 L17 Mrb Qb yb Ksa ysg Pforce ystretch yg 0.49556189 640 20219780.22 10615384.62 0.178106699 0.031121901 0.678768359 0.278864492 0

0 0.006870736 0.152622843

-5264.98814 4466.4576

-0.00039041

-0.4742557

-0.00027177 35079.47536 0.000064731

-0.00072691 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 0.751240326 0.28371542 0

0 0.001498148 0.079290058

-2503.37374 4118.748145

-8.8120 E-05

-0.15890822

-0.00016125 38818.28608 0.000041424

-0.0002908 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 0.751240326 0.28371542 0

0 0.001 49S148 0.079290058

-2503.37374 4118.748145

-8.8120 E-05

-0.15890822

-0.00016125 38818.28808 0.000041424

-0.0002908 Coeff. of Friction between disk &seat Average DP Across Disk (psi)

Disk Stiffness Constant Disk Stiffness Constant Geometry Factors. Roark, Table 24 Geometry Factors. Roark, Table 24 Geometry Factors. Roark, Table 24 Geometry Factors. Roark, Table 24 Loading Constant. Roark, Table 24, Case 1L Loading Constant, Roark, Table 24, Case 1L Loading Constant, Roark, Table 24, Case 2L Loading Constant, Roark, Table 24, Case 2L Moment Facto, Roark, Table 24 Unit Shear Force, Roark, Table 24 Bending Deflection due to pressure (in)

Shear deflection, Roark Table 25, case 2l Shear Deflection due to pressure (in)

Force acting on Hub (Ibs)

Hub Deflection due to Hub Force (ln)

Toal deflection due to Pressure Forces (in) ysw ybw

-3.0788 E-07

-6.01 23E-07

-5.0551 E-OB

-9.5966E-07

-1.21 16E-07

-8.9183 E-OB

-1.8700 E-OB

-2.2904 E-07

-1.2116 E-07

-8.91 83E-OS

-1.8700 E-OB

-2.2904 E-07 Deflection due to seat cont. force and shear stress (per Ibf/in) deflection due to bend. (per Ibf/in)

Deflection due to Hun Compression (per Ibf/in)

Toal deflection due to contact Force (per Ibf/in)

Fs F-piston F-vert F-prlock F-total 20750.5253 22248.507 22248.507 2774.971198 5411.884127 5411.884127 6662.37102 9520.295264 9520.295264 16871.02311 23681.46854 23681.46854 36167.42294 38789.87968 38789.87968 Seat Contact Force (Ibs)

Piston Force (Ibs)

Reverse Piston Force (Ibs)

Pressure Lock Force (Ibs)

Total Unseated Force Ibs

e

I P

P P

t 1005 380 350 2

4.36 1.25 0.286697248 0.5 5

0.087266461 0.3 27600000 1.875 15409 0.52 ub eta eta-rad ison I-th fh P

e dstem po n ut TEST

- onnet P

- own V852A 2250 30 0

1.536 2.789 1.5 0.537827178 0.4375 5

0.087266461 0.3 29000000 1.75 7816 0.66 V852B 2250 30 0

1.536 2.789 1.5 0.537827178 OA375 5

0.087266461 0.3 29000000 1.75 7386 0.66 NOTES Bonnet pressure (psi)

Upstream pressure (psi)

Downstream pressure (psi)

Disk Thickness (in)

Seat radius (in)

Hub Radius (in)

Seat to Hub Radius Ratio Hub lenght (in)

Seat angle (deg) rad Poisson'atio (disc material)

Modulus of Elasticity (psi)

Steam Diameter (in)

Static Pollout Force (Ibs)

Valve factor u

pavg C2 C3 0.49556189 640 20219780.22 10615384.62 0.178106699 0.03112'I 901 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 Coeff. of Friction between disk &seat Average DP Across Disk (psi)

Disk Stiffness Constant Disk Stiffness Constant Geometry Factors. Roark, Table 24 Geomet Factors. Roark Table 24 put

~bonnet

-up

-down n

P P

P t

a b

b I-t P

/a hub heta rheta-rad o son TEST 1005 380 350 2

4.36 1.25 0.286697248 0.5 5

0.087266461 0.3 27600000 1.875 15409 0.52 V852A 2250 30 0

1.536 2.789 1.5 0.537827178 0.4375 5

0.087266461 0.3 29000000 1.75 7816 0.66 V852B NOTES 2250 Bonnet pressure (psi) 30 Upstream pressure (psi) 0 Downstream pressure (psi) 1.536 Disk Thickness (in) 2.789 Seat radius (in) 1.5 Hub Radius (in) 0.537827178 Seat to Hub Radius Ratio OA375 Hub lenght (in) 5 Seat angle (deg) 0.087266461 rad 0.3 Poisson'atio (disc material) 29000000 Modulus of Elasticity (psi) 1.75 Steam Diameter (in) 7386 Static Pollout Force (Ibs) 0.66 Valve factor m

d D

G C2 C3 avg 8

9 3

9 11 17 fb b

M Q

yb y

y y

Ksa sq Pforce stretch sw ybw F-piston F-vert F-prlock F-total 0.49556189 640 20219780.22 10615384.62 0.178106699 0.031121901 0.678768359 0.278864492 0

0 0.006870736 0.152622843

-5264.98814 4466.4576

-0.00039041

-0.4742557

-0.00027177 35079.47536 0.000064731

-0.00072691 4.0788 E-07

-6.0123 E-07

-5.0551 E-08

-9.5966 E-07 0.621725137 2235 9623853.574 11153846.15 0.08798395 0.011950404 0.751240326 0.28371542 0

0 0.001498148 0.079290058

-2503.37374 4118.748145

-8.8120E-05

-0.15890822

-0.00016125 38818.28608 0.000041424

-0.0002908

-1.21 16E-07

-8.9183 E-08

-1.8700 E-08

-2.2904 E-07 20750.5253 22248.507 2774.971198 5411.884127 6662.37102 9520.295264 16871.02311 23681.46854 36167.42294 35605.87968 ss (per Ibf/in) 22248.507 Seat Contact Force (Ibs) 5411.884127 Piston Force (ibs) 9520.295264 Reverse Piston Force (Ibs) 23681.46854 Pressure Lock Force (Ibs) 35175.87968 Total Unseated Force Ibs 0.621725137 Coeff. of Friction between disk 8 seat 2235 Average DP Across Disk (psi) 9623853.574 Disk Stiffness Constant 11153846.15 Disk Stiffness Constant 0.08798395 Geometry Factors. Roark, Table 24 0.011950404 Geometry Factors. Roark, Table 24 0.751240326 Geometry Factors. Roark, Table 24 0.28371542 Geometry Factors. Roark, Table 24 0 Loading Constant, Roark, Table 24, Case 1L 0 Loading Constant, Roark, Table 24, Case 1L 0.001498148 Loading Constant, Roark, Table 24, Case 2L 0.079290058 Loading Constant, Roark, Table 24, Case 2L

-2503.37374 Moment Facto, Roark, Table 24 4118.7481 45 Unit Shear Force, Roark, Table 24

-8.8120E-05 Bending Deflection due to pressure (in)

-0.15890822 Shear deflection, Roark Table 25, case 2I

-0.00016125 Shear Deflection due to pressure (in) 38818.28608 Force acting on Hub (Ibs) 0.000041424 Hub Deflection due to Hub Force (in)

-0.0002908 Toal deflection due to Pressure Forces (in)

-1.2116E-07 Deflection due to seat cont. force and shear stre

-8.9183E-08 deflection due to bend. (per Ibf/in)

-1.8700E-08 Deflection due to Hun Compression (per Ibffin)

-2.2S04E-07 Toal deflection due to contact Force (per Ibf/in)

I p II a

ATTACHMENT4 Rochester Gas and Electric Ginna Station Gate Valve PIJTS Investigation Altran Technical Report 94108-TR-01, Att.D Sheet:

17 Valve No. 0720 Safety Class:

1

==

Description:==

RHR PMP DISCH TO LP B System: RHR EIN:

0720 Size:,10 Valve Disc Type:

FLEX Op Type MOV Reference PE>ID:

1247 Coordinate:

I-2 Normal Position:

CLOSE BuildingLocation:

RC Elevation:

235 Room:

CC03 System Design Temperature:

400 System Design Pressure:

600 Normal Ambient Temperature:

120 Accident Ambient Temperature:

286 Valve Function:

Hot Leg B RHR return. (Ref. EWR 2512 isometric 354-03)

Initial Screening

1) Is valve 0720 a member ofthe ASME XIIST program?

2) Is valve 0720 a member ofthe GL 89-10 program?

3) Does valve 0720 have an active safety function to open based upon the IST program?

4) Does valve 0720 provide a non safety function to open which is important to plant operation?

Ifyes explain: Required for cool-down.

5) Does valve 0720 requires further PIJI'B screening?

Yes Yes Yes PIJI'B screening

6) Is rapid depressurization ofadjacent piping possible?

Ifyes explain: Assume Valve 721 leaks. LOCA.

7) Is valve 0720 susceptible to heating from adjacent system fluid?

Ifyes explain:

8) Is valve 0720 susceptible to heating Rom the ambient environment?

Ifyes explain: High LOCA temperature.

Results Valve 0720 is susceptible to pressure locking:

Valve 0720 is susceptible to thermal binding:

No Evaluation Summary:

This valve's safety function is to provide containment isolation. The only time it is opened is to perform a normal cooldown during which time the conditions required to produce PLffB are not present. Rapid depressurization and elevated ambient temperatures are a result ofa LOCA. Prior to a normal, cooldown system heat from the RCL willunlikely reach this valve because it is isolated from the RCL by valve 0721.

Historically there have been no problems in operating this valve.

9) Is further corrective action required?

No

Rochester Gas and Electric Ginna Station Gate Valve PLITS Investigation Altran Technical Report 94108-TR-01, Att.D Sheet:

18 Valve No. 0721 Safety Class:

1 Reference PEcID:

1247

==

Description:==

RHR PMP DISCH TO LP B System: RHR EIN:

0721 Size:

10 Valve Disc Type:

FLEX Op Type MOV Coordinate:

I-1 Normal Position:

CLOSE BuildingLocation:

RC Elevation:

235 Room:

CC03 System Design Temperature:

650 System Design Pressure:

2485 Normal Ambient Temperature:

120 Accident Ambient Temperature:

286 Valve Function:

Hot Leg B RHR return. Valve cannot open above 410 psig via RC pressure interlock(Ref. 2512 isometric 354-03)

Initial Screening

1) Is valve 0721 a member ofthe ASME XIIST program'?

2) Is valve 0721 a member ofthe GL 89-10 program?

3) Does valve 0721 have an active safety function to open based upon the IST program?

4) Does valve 0721 provide a non safety function to open which is important to plant operation?

Ifyes explain: Required for co'ol<own.

5) Does valve 0721 requires further PIJI'B screening?

Yes Yes Yes Yes PL/TB screening

6) Is rapid depressurization ofadjacent piping, possible' Ifyes explain: LOCA

7) Is valve 0721 susceptible to heating from adjacent system fluid?

Ifyes explain:

8) Is valve 0721 susceptible to heating from the ambient environment?

Ifyes explain: High LOCA temperature.

Results Valve 0721 is susceptible to pressure locking:

Valve 0721 is susceptible to thermal binding:

Yes No Yes Yes Yes Evaluation Summary:

This valve's safety function is to provide containment isolation. The only time it is opened is to perform a normal cooldown during which time the conditions required to produce PLEB are not present. Rapid depressurization and elevated ambient temperatures are a result ofa LOCA. Prior to a normal, cooldown system heat from the RCL willunlikely reach this valve because it is located more than 20 feet away and below from the RCL. Historically there have been no problems in operating this valve.

9) Is further corrective action required?

No

ATTACHMENT5 re-opening DP less than 'the DP occurring initially.

Re-closin after Inadvertent 0 enin Since the valves are not required to close, re-closing is not required.

Valve Reduced Voltage MOV 1815 A B 0 enin Valve receives signal to open on SI.

Therefore, opening voltage is associated vith operation during load sequencing due to SI.

OV 1815 A B Closin Valve may close during SI sequence if a SI pump fails to start.

Therefore, closing voltage is associated with operation during load sequencing due to SI.

Pressure Lockin and Thermal Bindin These motor-operated gate valves have double discs

and, therefore, are not susceptible to thermal binding.

These valves serve as suction to SI Pump C from the RWST.

The only pressure available to these valves is the static head from the RWST, therefore, these valves are.not susceptible to pressure locking.

6.2.5 MOV 878 A/B/C/D 878 A/C are SI pump discharge to hot legs.

They are normally closed with AC power removed.

878 B/D are SI pump discharge to cold legs.

They are normally open with AC power removed.

Since 878 B/D are in their safety-related position (open) with AC power removed, the valves can not be inadvertently closed from the control room.

Should the valves become mispositioned as a result of some test, status lights in the control room. and valve alignment check would prevent this condition from going unnoticed for extended periods of time.

Therefore, 878 B

& D vill not be included in the GL 89-10 Program.

Since 878 A

& C are in their safety-related position (closed) with AC power removed, the valves can not be inadvertently opened.

These valves are also not required to be open for a transient.

RV nozzles are relied upon to prevent boron precipitation.

Status lights and valve alignment checks prevent extended periods of operation with mispositioned valves due to testing.

Therefore, 878 A

& C will not be included in the GL 89-10 Program.

DESIGN ANALYSIS EWR f5080 Page 11 REVISION 6 JULY 19, 1996