ML17265A689
| ML17265A689 | |
| Person / Time | |
|---|---|
| Site: | Ginna  |
| Issue date: | 06/30/1997 |
| From: | Lyon L, Mulcahy F ALTRAN CORP. |
| To: | |
| Shared Package | |
| ML17265A688 | List: |
| References | |
| 96190-C-68, 96190-C-68-R01, 96190-C-68-R1, NUDOCS 9907010058 | |
| Download: ML17265A689 (14) | |
Text
ATTACHMENT3 PRESSURE LOCKINGANALYSIS FOR VALVE(S)871A/B Calculation No. 96190-C-68 Revision 1
Volume 1 of 1 prepared for.
Rochester Gas And Electric Co.
R. E. Glnne Nuclear Power Plant JUNE 1997 VENDOR DESIGN ANALYSIS REVIEN a
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v Aitran Corporation 200 High Street Boston, MA02110 (617) 330-1130 FAX: (617) 330-1055
'I)9070i0058 'll'ItOb22 PDR ADQCK 05000244 P
Report Record Document No. 96190-C-68 Rev. No.:
1 No. of Sheets
/2.
SUbject:
Pressure locking analyses for motor-operated valve(s) 871A/B at Ginna Station.
REVISION DESCRIPTION:
Revision 1 incorporates comments from Kalsi Engineering Inc. and revises valve data based on valve grouping data from Reference 13.
COMPUTER RUNS (identified on Computer File Index):
Error reports evaluated by:
YES N/A X
Date:
Impacted by error reports No X
Yes (ifyes, attach expla t'
Originator(s)
.A. Mulcahy Date:
g 3e 7'7 Checker(s):
DESIGN VERIFICATION:
Performed by:
Required X
Not Required Date:
Method ofdesignveriflcation:
/
Design Review Qualification Test (DatalResutts) Attd.)
Alternate Calculations (Attached)
Comments resolved by:
Design verifier concurrence:
Date:
Date:
APPROVED FOR RELEASE PROJECT MANAGER:
ENGINEERING MANAGER:
M. Eissa Date:
Date:
~~ gt)
~ Calculation Sheet
~
Sheet 1
Gale. No. 96190-C-68 By:
F. A. Mulcahy Date:
6/30/97 Rev. No.
1 Date:
6/30/97 Table ofContents Cov'er Sheet Report Record Table ofContents Analysis Summary Sheet Objectives Methods Assumptions Input Data Summary ofResults Calculation References Attachment A
.1 n
1 2
3 3
3 4
4 5
9~
10
Analysis Summary Sheet Sheet 2 Gale. No. 96190-C-68 By:
F. A. Mulcahy Date: 6/30/97 Rev. No.
1 Date: 6/30/97 Calculation Subject Calculation of required thrust to open valve(s) 871A/B under design bases pressure locking conditions at Ginna Station.
Revision 1 incorporates comments from Kalsi Engineering Inc. and revises valve data based on valve grouping data from Reference 13.
Objective of Calculation The objective of this calculation is to determine the required thrust to open valve(s) 871A/8 under design bases pressure locking conditions.
Calculation Methods and Assumptions The methodology used for this calculation is based on References 1 and 9. The methodology determines the total force required to open a flexable wedge gate valve under pressure locking conditions.
Valve Seat/Disc Coefficient of Friction = 0.477 Valve packing load is included in the static unwedging force taken from test data.
Static unwedging load taken from test data for valve 871B. Not available for valve 871A.
Design Basis And References See page 9 for a list of references used for this calculation.
Conclusions The required thrust to open valve(s) 871A/B under design bases pressure locking conditions is 4378 lbs. This is less than the actuator motor capability of 6897 Ibs, the actuator thrust limitof 14000 Ibs, and the valve unseating limitof 12533 lbs. Therefore, this valve is capable of opening under design bases pressure locking conditions with degraded voltage.
~ Calculation Sheet
~
Sheet 3 Gale. No. 96190-C-68 By:
F. A. Mulcahy Date:
6/30/97 Rev. No.
1 Date:
6/30/97 OBJECTIVES:
Determine the required thrust to open the valve(s) when the bonnet is pressurized to design basis line pressure.
METHODS:
The force required to open a flexible wedge gate valve when its bonnet is pressurized consists of several components.
- 1. Static Unwedging Load (Fpo)
From the static condition closing thrust there is a residual seat force which together with the seat angle and friction coefficient determines the unwedging force. This residual force remains ifthe wedge is "locking" (that-is the friction coefficient is greater than the tangent of the wedge angle).
The static unwedging force is taken from static test data.
- 2. Seat Contact Force (Fpreslock)
An additional force requirement comes from the bending load on the wedge halves due to internal pressure.
This force consists of a bending component, a shear component and a hub stretching component.
These forces are found using the methods found in References 1 and 9.
- 3. Differential Pressure Load (Fyert)
Because the wedge halves are not parallel a third force component results from the vertical component of the differential pressure load acting on the seat area.
This force is calculated using the methods described.
in Reference 8.
- 4. Piston Effect Load (Fpiston)
The stem end load or "piston effect" results from the internal pressure action on the stem end area.
This force helps to open the valve. This force is calculated using the methods described in Reference 8.
- 5. Packing Load (Fpkg)
The packing drag load resists stem motion. This load is included in the static unwedging load (Fpo) discussed in 1, above.
- 6. Torque Reaction Friction Load The torque in the stem is reacted in the valve by surfaces which engage and'slide.
The Torque Reaction Factor (TRF) accounts for this load. See Reference 8 for a detailed analysis of this load.
The total force to open the valve is then:
Ftotal = (Fvert+ Fpreslock+ Fpo+ Fpkg - Fpiston)/TRF ASSUMPTIONS:
1 ~ Reaction loads and the friction coefficient at the seat surfaces are equal both upstream and downstream and for opening (unwedging) and closing (wedging).
- 2. The packing load is assumed to be 0 Ibs since it is included in the static unwedging load (Fpo) taken from test data.
- 3. Young's modulus of elasticity (E) and Poisson's Ratio (v) for the steel wedge are 2.76E+07 psi and 0.3, respectively.
- 4. The static unwedging load is 2202 Ibs, taken from test data for valve 871B. Static test data not available for valve 871A.
l.
~ Calculation Sheet Sheet 4 Gale. No. 96190-C-68 By:
F. A. Mulcahy Date:
6/30/97 Rev. No.
1 Date:
6/30/97 Valve ID 871A/B
==
Description:==
SIP 1A to 1C Crossover INPUTDATA Valve Manufacturer Valve Size (Nominal)
Hub Length (L)
Hub Radius (b)
Disk Radius (a)
Disk Thickness (t)
Stem Diameter (Ds)
Bonnet Pressure (q)
Upstream Pres (Pu)
Actuator Thrust Limit Stem Factor (FS)
Velan 3 tn 0.250 in 0.813 in 1.28 in 0.750 in 1.125 in 1533.0 psig 33.0 psig 14000.0 lbs 0.0116 it Ref.
3 Disk Angle (DA) 5.0 degrees 3
Valve Type Gate 3
Pullout Force (Fpo) 2202 lbs 3
Packing Load (Fpkg) 0 ft-lbs 5
Valve Factor (VF) 0.46 3
Poisson Ratio (v) 0.3 3
Mod. Elasticity (E) 27600000 psi 2
Downstream Pres(Pd) 33.0psig 2
Motor Capability 6897.0 lbs 10,11 Valve Unseating Limit 12533.0 lbs 10,11 Torque Surface COF-P t0.50 Ref.
3 3
12 12 13 7
7 2
10,11 3
8
SUMMARY
OF RESULTS Piston Load 1524 lbs Vertical Load 1349 lbs Seat Contact Load 2113 1bs Pullout Load Packing Load Total Unwedging Load Motor Capability Unseating Limit Actuator Thrust Limit 2202 lbs 0 Ibs 4378 lbs 6897 lbs 12533 lbs 14000 lbs
~ Calculation Sheet
~
Sheet 5 Gale. No. 96190-C-68 Rev. No.
1 By:
F. A. Mulcahy Date:
6/30/97 Date:
6/30/97
- 1. Average Differential Pressure Across Disk:
Pu+ Pd.
DPA= q-1533-2 DPA=
1500.0psi 33+ 33
- 2. Disk Stiffness Constants:
(Reference 1, Table 24)
E x (t) 27600000 x ( 0.750 )
D 12x (1-v
)
12x(1- 03
)
1,066,277 Ibf in G
27600000 2x (1+v) 2x(1+.3)
= 10,615,385 psi
- 3. Geometry Factors:
(Reference 1, Table 24) 1 C2=
x 4
2 1- (b/a) x (1 +2x In(a/b))
C2 =
0.0578 x
b 4a 2
(b/a) + 1 2
x In(a/b) + (b/a) 1 C3 =
0.0065 1
C8=
x 2
2 1 + v + (1 - v x (b/a)
C8 =
0.7909 b
C9=
x 2
(1 + v)/2 x In(a/b) + (1-v)/4 x 1 - (b/a)
C9 =
0.2540 L3=
x 4a 2
(a/a)
+ 1 2
x In(a/a)
+ (a/a)
L3 =
0.0000 a
L9=
x a
2 (1 + v)/2 x In(a/a) + (1-v)/4 x
1 - (a/a)
L9 =
'.0000 1
L11 = x 64 4
2 1 + 4 x (b/a)
- 5 x (b/a)
- 4 x (b/a) x 2
2 + (b/a) x In(a/b)
L11 =
0.0006 1
L17 = x 4
4 2
1-(1-v)/4 x 1-(b/a)
-(b/a) x 1+(1+v) xln(a/b)
L17 =
0.0532
~ Calculation Sheet
~
Sheet 6 Gale. No. 96190-C-68 Rev. No.
1 By:
F. A. Mulcahy Date:
6/30/97 Date:
6/30/97
- 4. Moment (Reference1, Table 24, Case 2L)
Mrb =
2
-DPAxa C8 x
x (a-b
) -L17 C9 2
2 2ab Mrb =
-206.9 Ibf Qb=
DPA 2b x (a-b) 2 2
Qb =
905.2 Ibf/in
- 5. Deflection Due To Pressure And Bending (Reference 1, Table 24, Case 2L) 2 3
4 Ybq =
(Mrb x a x C2)/D + (Qb x a x C3)/D - (DPA x a x L11)/D Ybq = -9.254E-06 in
- 6. Deflection Due To Pressure And Shear Stress (Reference 1, Table 25, Case 2L) 2 Ksa =
-0.3 x 2xin(a/b) -1+ (b/a)
Ksa =
-0.0938 Ysq =
(Ksa x DPA x a
)/(t x G)
Ysq =
-2.901,5E-05 in
- 7. Deflection Due To Hub Stretch (from center of hub to disk) 2 2
Pforce=
pix (a - b )xDPA Pforce x L Pforce =
4624.1 Ibf Ystretch =
2 pixb x2xE Ystretch =
1.0086E-05 in
- 8. Total Deflection Due To Pressure Forces:
Yq =
Ybq+ Ysq - Ystretch Yq =
-4.8355E-05 in
~ Calculation Sheet I Sheet 7 Gale. No. 96190-C-68 By:
F. A. Mulcahy Date:
6/30/97 Rev. No.
1 Date:
6/30/97
- 9. Deflection Due To Seat Contact Force And Shear Stress (per Ibf/in):
(Reference 1, Tahle 26, Case 1L)
-1.2 x (a/a)'x In(a/b) x a Ysw =
txG Ysw =
-8.7896E-08 in/Ibf/in
- 10. Deflection Due To Seat Contact Force And Bending (per lbf/in):
(Reference 1, Table 24, Case 1L) 3 Ybw= -(a /D) x (C2/C8) x (a x C9)/b - L9 (a/b) x C3
+ L3 Ybw =
-3.7679E-08 in/Ibf/in
- 11. Deflection Due To Hub Compression (per Ibf/in), (from center of hub to disk):
2xaxpixL Ycompr =
pixb x2xE Ycompr =
1.7562E-08 in/Ibf/in
- 12. Total Deflection Due To Seat Contact Force (per Ibf/in):
Yw =
Ybw+ Ysw-Ycompr Yw=
-1.4314E-07 in/Ibf/in 13.
Seat Contact Force For Which Deflection Is Equal To Previously Calculated Deflection From Pressure Forces (per Ibf/in):
Fs =
2 x pi x a x (Yq/Yw)
Fs=
2720 Ibf
~ Calculation Sheet Sheet 8 Calc. No. 96190-C-68 By:
F. A. Mulcahy Date:
6/30/97 Rev. No.
1 Date:
6/30/97 14.
Torque Reaction Factor (TRF)
Ii, ASS.
TRF=1-I':.
0.50 x.0116 0.107 0.9457 where:
li,
=
Coefficient of friction for torque reaction surface t
FS
=
Stem factor, ft r,
=
Disc radius, ft 15.
Disc/Seat Coefficient of Friction VF x cos(DA) 0.46 x cos(
5.0 )
V, 0.4774 1 - VF x sin(DA) 1 p.46x sin(
5.p )
where:
=
Valve factor (opening)
=
Disc angle in degrees p,
=
Disc/seat coefficient of friction S
16.
Unseating Forces Fpo =
Fpkg =
2202 Ibf 0 Ibf Fpiston =
(pi/4) x Ds x q 2
Fvert =
sin(DA)*[(pix a ) x ( 2 x q - Pu - Pd) ]
Fpreslock =
2 x Fs x (iL x cos(DA) - sin(DA))
Ftotal =
(-Fpiston+ Fvert+ Fpreslock+ Fpo+ Fpkg)
TRF Fpiston =
Fvert =
Fpreslock =
Ftotal =
1524 Ibf 1349 Ibf 2113 Ibf 4378 Ibf
Calculation Sheet Sheet 9 REFERENCES Gale. No. 96190-C-68 Rev. No.
1 By:
F. A. Mulcahy Date:
6/30/97 Date:
6/30/97 Ref. No.
Title List ofCalculation References Used For 871A/B Rev. No.
Rcv. Date 1
Young, Warren C., Roark's Formulas for Stress &Strain, 6th Edition, McGraw Hill, 1989:
Altran Technical Report No. 94108-TR-OI, Investigation OfPressure Locking/Thermal Binding Altran Calculation No. 90170-C-03, Valve Thrust Calculation for 3" Velan Gate Valve MOV871A &B 11/1/94 4
Velan Valve Drawing 88405-1 5
Velan letter, Seat Diameters For Various Valves: Altran PO No. APO-96190<
6 EPRI MOVPerformance Prediction Program Topical Report, TR-103237, Final Draft, 9/21/94 7
Marks'tandard Handbook for Mechanical Engineers, Ninth Edition 8
NP-6660-D, Application Guide for Motor-Operated Valves in Nuclear Power Plants, EPRI, March 1990 9
Commonwealth Edison Pressure Locking Methodology presented at Summer 1995 MOVUsers Group Meeting 10 Altran Calculation No. 91190-C-44, Analysis ofThrust And Torque Limits For Motor-Operated Valve 871A 11 Altran Calculation No. 91190-C-45, Analysis ofThrust And Torque Limits For Motor-Operated Valve 871B 12 WfVIRNumber 9221428 and 19404023 13 RG&E EWR 5111, Motor Operated Valve Program Plan 9/26/68 10/3/96 3/1/90
~ Calculation Sheet Sheet 10 Gale. No. 961 90-C-68 Rev. No.
1 By:
F. A. Mulcahy Date:
6/30/97 Date:
6/30/97
~ ATTACHMENTA PROJECT QA RECORD C/g I 90 YIKLk!M SSO hfcArthur, V/l/e Sl-Laurenr Quebec, Conodo f/4TIX//.
DATE: Oct. 03, 1996 FROID: Bertll Nllsson PHONE: (514) 748.7748 ext 241 FAX: (514) 342-2311 REF:
BN410421 PAGE:
1 OF 1 FAX:
617430-1055 TO:
Altran Corp.
ATT.:
Steve Greer C.C.
SUBJECT:
Your P.O. ¹APO.961904 Vetan Ref.: P941 243-K Per your request we ara pleased to provide following informationregarding Seats:
1)
Drawing 884054 Tag No. 0871A & B O.D. of Stellite: 2 3/4" I.D. of Stelllte: 23/8" Wa'lelway bore: 21/4n 2)
Drawing 88701-3 Tag No. 0852A 8, B O.O. of Slellite: 5 3/4" I.O. of Stellite: 5 3/16" Waterway bore: 5 1/16" We trust this information meets with your acceptance.
B. Nilsson Vdon /ne.
g/S5 \\vnnf Avcnuc Monucnk rb~bcc Cnnah HeM /Td CERTIFIED TO ISO 9001 QUALlTYSTANDARDS Velan Vobe Coip.
Avcnnc
'C'~ekr lndwsninl Park WiQbtnn. Vcnnonc U.SA.
0549$