ML17264A612
| ML17264A612 | |
| Person / Time | |
|---|---|
| Site: | Ginna  |
| Issue date: | 09/23/1996 |
| From: | Mull K ROCHESTER GAS & ELECTRIC CORP. |
| To: | |
| Shared Package | |
| ML17264A608 | List: |
| References | |
| DA-ME-96-076, DA-ME-96-076-R02, DA-ME-96-76, DA-ME-96-76-R2, NUDOCS 9609270305 | |
| Download: ML17264A612 (13) | |
Text
ATTACHMENT3 Design Analysis Ginna Station Pressure Lock Evaluation for MOVs 852 AGB Ginna Station Rochester Gas and Electric Corporation 89 East Avenue Rochester, New York 14649 DA-ME-96-076 Revision 2
September 20, 1996 Prepared by:
l K. I Design Engin er Date Approved by:
Independent or Lead Reviewer Date EIN 852A 852B TECHNICAL INPUT FORM KEYWORDS CROSS REF MOVs Pressure Lockin PSSL 03 EWR/
OTHER x
PCR k PROPRIETARY YES NO COMMENT SUPERSEDES Rev.
1 Page 1 of 9 9609270305 960924 PDR ADOCK 05000244 P
=
'PDR
.REVI I N TA HEET evision Number Affected Sections Descri tion of Revision 3.0 Added Design Inputs 3.5 to 3.9.
7.2
"'7'.2 7.4.2.1 7.4.2.2
'7.4.3 Added additional clarification to upstream and downstream pressure values.
Added minor clarification.
Revised calculated pressure locking force.
Revised calculated total required force.
Revised valve factor; added clarification.
7.5 7.6 7.7 Completely revised to show calculation of available thrust.
Stem factor and temp.
effects justification added.
Revised F+,
FR and added minor clarification.
Added Section 7.7.
8.0 Revised results to reflect new press.
locking force, force required and force available.
Att. A Att.
B No change.
Revised to reflect new valve disc coefficient of friction of 0.621.
Att.
C New.
Design Analysis DA-ME-96-076 Page 2 of 9
Revision 2
TABLE OF CONTENTS ECTION TITLE PAGE NO.
1.0 2.0 3.0
~Pun ose Conclusions Desi n In uts 4
~
~
~
~
~
~
~
~
~
~
~
~
~
~
~
4
~
4 4.0 5.0 Referenced Documents
~
4 5
6eo Com uter Codes 5
7.0 8.0
~Anal sis Results 5
Design Analysis DA-ME-96-076 Page 3 of 9 Revision 2
1.0 1 ~ 1 2.0
~Pur oee To perform a pressure locking evaluation for MOVs 852A and 852B based upon a maximum unseating thrust of 11,000 LBf.
Conclusions 3.0 Based upon the analysis performed in Section 7.0, the total calculated force required to overcome pressure locking is less than the available thrust.
This conclusion is based upon a maximum unseating load of 11,000 LBf.
Actual "as-left" unseating thrust values would provide additional margin.
Desi n In uts 3.1 3.2 3
3 3.4 3.7 3.8 3.9 4.0 ALTRAN calculation No. 92129-C-01, Rev.
0, August 1992.
RG&E MOV calculation for 852A, dated 8/6/96.
RG&E MOV calculation for 852B, dated 8/6/96.
RG&E Design Analysis No. NSL-5080-0002, Rev.
6.
RG&E Design Analysis No. DA-ME-96-083, Rev. l.
RG&E Design Analysis No. DA-ME-96-090, Rev.
0.
RG&E/MOVATS Testing Package M-64.1.2, dated 9/8/96, 852A.
RG&E/MOVATS Testing Package M-64.1.2, dated 9/8/96, 852B.
RG&E Design Analysis DA-EE-92-131-06, Revision 7.
Referenced Documents 4.1 4.2 4.3 NUREG/CR-5807, KEI No.
- 1721, "Improvements in Motor Operated Gate Valve Design and Prediction Models for Nuclear Power Plant Systems, SBIR Phase I Final Report Sept.
1990 April 1991.
Westinghouse Calc.
No. V-EC-1606, Rev.
0, Verification of Pressure Locking Analysis Program,Preslock, WOG-220.
(Attachment A).
Cameron Hydraulic Data, 17th Edition, 1st Printing.
Design Analysis DA-ME-96 076
-Page 4 of 9 Revision 2
Date 08 20 96
4.4 4.5 5.0 Mechanics of Materials, Beer E Johnston, 1981.
Westinghouse Fax, I. Ezekoye (Westinghouse Owners Group) to D. Markowski, dated 8/8/96.
Assum tions 5.1 This evaluation is based upon an assumed maximum unseating thrust of 11,000 Lbf.
This value will be confirmed via procedure M-64.1.2 during testing of 852 A/B.
6.0 Com uter Codes 6.1 Microsoft Excel version 5.0 was used to develop the spread sheet for the pressure locking calculation based upon, Ref. 4.2.
Spreadsheet was verified as shown in Column "Verification", (Attachment B).
7.0 7.1 7.2
~Anal sis The methodology for calculating the total force required to overcome pressure locking is based upon Reference 4.2 (Attachment A).
This document includes definition of terms and applicable equations.
Input Data:
Bonnet Pressure (PENNEY)
= 2250 psi (Based on Design Input 3.4)
Upstream Pressure (P~)
= 30 psi (Based upon Design Input 3.6, slightly conservative, actual calculated value approx.
31 psi).
Downstream Pressure (Pd,
) = 0 psi (conservative, worst case Rx completely blowdown)
Disk thickness (t) = 1.536 in.
(Design Input 3.1)
Seat radius (a)
= 2.789 in, (Design Input 3.1)
Hub radius (b)
= 1.500 in.
(Design Input 3.1)
Seat Angle (8)
= 54 (Design Input 3.1)
Poisson's Ratio (v) = 0.3 (Ref. 4.2 typical)
Design Analysis DA-ME-96-076 Page 5 of 9 Revision 2
~
Modulus of Elasticity (E)
= 2.9 x 10'si (Ref.
4.4, App. B, Steel Typical)
~
Unseating Thrust (F~
) = 11,000¹ (Assumed maximum, to be verified by testing, Section 5.1)
~
Open Valve Factor (VF) = 0.66 (Based upon Design Input 3.5)
~
Stem Diameter (D
) = 1.75 in.
(Based upon Design Inputs 3.2 and 3.3)
~
Hub Length (Hub Length)
= 0.4375 in.
(Based upon field measurement of spare disc in stock) 7.3 Spreadsheet Verification 7.3.1 7.3.2 Attachment B, Column "Verification" provides the verification of the correctness of the spreadsheet for calculating the total force.
The equations from Ref. 4.2 were used to develop the spreadsheet.
7.3.3
~
~
The example from Ref. 4.2, App. A, Pages 22-25 was used to verify the spreadsheet.
7.3.3.1 The inputs were used in the spreadsheet and a line-by-line verification of the results was performed.
7.4 Calculation of Total Force Required 7.4. 1 7.4.2 7.4.2. 1 7.4.2.2 The applicable data for valves 852 A/B, from Section 7.2, was inputted to the spreadsheet.
The input and results are shown in Column "V852A" and "V852B" of Attachment B.
The calculated pressure locking force was determined to be 23,681¹.
The total required force was calculated to be 38,790¹,
(FR).
7.4.3 Discussion of calculation of Coefficient of Friction (w)
Design Analysis DA-ME-96-076 Page 6 of 9
Revision 2
Date 08 20 96
The methodology of Design Input 4.2 is based upon calculation for the coefficient of friction (p) as follows:
p = VF 1+VF sin 0
where:
VF = the closing valve factor (0.66 for both the closing and opening direction per Design Input 3.5).
8 = Seat Angle (5 degrees)
If a valve factor of 0.66 is used with the methodology of Design Input 4.2, the appropriate coefficient of friction of 0.621 will be applied to the Total Required force calculation for the open direction.
As indicated in App. A, Pg., 13 of Ref. 4.2, p is calculated using the closing valve factor.
As indicated in Ref. 4.5, the decision/recommendation to base p on the closing valve factor (in Ref. 4.2) was that test results generally indicated more stable data was obtained for the closing direction than for the opening direction.
The coefficient of friction (p) is dependent upon the materials in contact involved.
p is independent of the direction the valve is operating and therefore would be the same for both the'opening and closing directions.
The equation for p, in Ref. 4.2 is based upon equation 2.1a of Ref. 4.1 (algebraically manipulated).
VF cos 0
p sin 8
.621
=.66 cos(5)
(.621)(sin 5)
This discussion reflects the results of Design Input 3.5, in that a disc coefficient of friction of 0.621 will be utilized in the calculation.
7.5 Available Thrust 7.5. 1 From Design Inputs 3.2 and 3.3 the stall thrust can be determined as follows:
Design Analysis DA-ME-96-076 Page 7 of 9
Revision 2
Date 08 20 96
- 7. 5. 1. 1 Stall Thrust =
~
~
where:
MT UR =
PE =
AF =
FS Name Plate Motor Torque (60 ft-lbs)
Unit Ration (60.15:1)
Pullout Efficiency = (0.40)
Application Factor (1.0)
Stem Factor (0.019 ft) [see below]
Stem Factor:
The Stem Factor of 0.019 was the result of actual valve
- testing, Per Design Inputs 3.7 and 3.8.
Valve 852A results indicate a Stem Factor of 0.018, Valve 852B results indicate a Stem Factor of 0. 019.
Three (3) tests for each valve in the open direction were performed.
The 0.019 maximum value will be used for this analysis.
Stall Thrust =
60 60.15 0.40 1.0 0.019 7.5.1.2 Stall Thrust = 75,979 lbs.
I Reduction for Reduced Voltage Per Design Input 3.9 the applicable reduced voltage factor for the 852's is 75<.
7.5.1.3 7.5.1.4 Available Thrust Fp, = 75,979 (R.V.)
75J979
( ~ 75)
F+ = 42,738 lbs.
Temperature Effects Since the 852's are required to open within seconds of an accident, this is not sufficient time for the valve actuator to heat up.
Therefore, a reduction for Temperature Effects will not be applied for this analysis.
Design Analysis DA-ME-96-076 Page 8 of 9
Revision 2
7.6 Acceptability II
.'. Since F (42,738/) is FR (38,790g) the 852 A/B MOVs would be able to overcome the calculated pressure locking forces and perform it's safety-related opening function.
7.7 Margin Discussion From Design Inputs,3.7 and 3.8, the actual "as-left" unseating thrust values are as follows:
852A:
7816 lbs.
852B:
7386 lbs.
If these values are inputted to the total force calculation the required total force decreases as follows:
852A 35 I 606 lbs.
852B'5,176 lbs.
8.0 8.1 These results are shown on Attachment "C".
'esults The force due to pressure locking was calculated to be 2386811.
8.2 8.3 The total required force was calculated to be 38,790'.
The available thrust was determined to be 42,738g, since this exceeds the required force (38,790/),
the 852 A/B MOVs would be operable under all expected
- loads, including pressure locking considerations.
This result is based upon a maximum unseating thrust of 11,000/.
An actual measured unseating thrust of less than 11,0001 would provide additional margin, as discussed in Section 7.7.
Design Analysis DA-ME-96-076 Page 9 of 9
Revision 2
Date 08 20 96
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Westinghouse Bectric Carparatian Energy Systems'ox 355 Pinsourgn Pennsvlvania 15230 0355 ESBU/WOG-96%50 February 13, 1996 To:
WOG S&EE Subcommittee Representatives (1I 1A)
PLTB Task Team (1I 1A)
Subject:
Westinghouse Owners Group Verification of Pressure Lockin Analysis Pro ram - Preslok rMJHP-6050 Attached for your information in cornplction of Action Item 2 from the January 4 & 5, 1996 PLTB Task Team meeting is Verification Of Prcssure Lockin Analysis Pro m - Preslok.
The verification included:
a.
a review of the ComEd model and the associated equations for applicability.
b.
a review of thc assumptions to assure that they are reasonable.
a comparison of the MathCad sample problem solution with a hand calculation solution.
an update of the Preslok Users Manual to rcQect comments obtained during the January.5; 1996 WOG PLTB Task Team meeting.
The verification confirms that the Presiok MathCad model correctly performs the ComEd pressure locking open load calculation, however, it does not compare thc calculated results with the test results.
This aspect willbe covered by ComEtL Phase direct questions or comments to Ikc Ezckoye, ~W at (412) 374-6643.
- Regards, S.A. Binger, Jr Project Engineer Westinghouse Owners Group SAB/ygs attachment Steering Committee (1L, 1A)
WOG Primary Reprcscntatives (1L, 1A)
Licensing Subcommittee (1L, 1A)
Operations Subcommittee (1L, 1A)