Text

Containment Purge & Vent Valve Operability Rept
	ML20083C619
Person / Time
Site:	Cooper
Issue date:	11/23/1983
From:	Goldman H, Zeiders R; ALLIS-CHALMERS CORP.
To:	;
Shared Package
ML20083C615	List: ML20083C611; ML20083C619;
References
	NUDOCS 8312230207
	Download: ML20083C619 (79)
	v • d • e

{{#Wiki_filter:' C Dwg. #44113-A o g NEBRASKA PUBLIC POWER DISTRICT COOPER NUCLEAR STATION CONTAINMENT PURGE AND VENT VALVE OPERABILITY REPORT PREPARED BY: [M MM OATE: // 2//8J [/)h M DATE: ll/Z 83 CHECKED BY: APPROVED BY: [ DATE: /i/z3/p3 ALLIS-CIIALMERS VALVE OPERATIONS NOVEMBER 1983 8312230207 g h g PDR ADOCK PDR P

C' / ~ ' TABLE OF CONTENTS PAGE SCOPE '2

SUMMARY

3-6 PRESStJRE RESPONSE CURVES 7--10

~

OPERATING TIMES AND CURVES 11-25 DRAWINGS AND PHOTOGRAPHS 26-36 TORQUE ABSORPTION 37-45 LOAD STRESS ANALYSIS 46-50 TORQUE ANALYSIS 51-83 e 6 f m. .-m m.. ..u..

a VALVES COVERED BY THIS REPORT ARE AS FOLLOWS: TAG NO. SIZE OPERATOR LOCATION PC-230-MV 24" MOTOR H2BC/SMB0015 LIMITORQUE WETWELL PC-245-AV 24" AIR-SPRING BETTIS 744A-SRI WETWELL PC-233-MV 24" MOTOR H2BC/SMB0015 LIMITORQUE WETWELL PC-237-AV 24" AIR-SPRING BETTIS 744A-SRI WETWELL PC-231-MV 24" MOTOR H2BC/SMB0015 LIMITORQUE DRYWELL o PC-246-AV 24" AIR-SPRING BETTIS T-420B-SRI DRYWELL PC-232-MV 24" MOTOR H2BC/SMB0015 LIMITORQUE DRYWELL PC-238-AV .24" AIR-SPRING BETTIS T 420B-SRI DRYWELL ALL VALVE ORIENTATIONS, TORQUE COEFFICIENTS, PRESSURE DROPS, ETC. USED IN THIS REPORT WERE TAKEN FROM ALLIS-CHALMERS-REPORT VER-0209 DATED 12/17/79.

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N GENcRAL OFFICE F ; '21.h ' "T' Nebraska Public Power District

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M J sser August 15, 1983 6 Mr. R. H. Zeiders Allis-Chalmers Corporation Box M-93 Yock, Pennsylvania 17405

Dear Mr. Zeiders:

Per our recent discussions, the three purge valves the NRC questioned at CNS have been radiographed. In addition, a field examination of purge valve 238AV was possibic by entering the pipeline. The results are as follows: 238AV Curved surface faces. flow i.e. seat is downstream. 231MV Flat surface faces flow i.e. seat is upstream. 246AV Flat surface faces flow 1.e. seat is upstream, f An updated curve for the CNS drysell and wetwell pressures versus time for a design basis accident is attached. It should be noted that the maximum pressure condition for the drywell is reached around 3 seconds into the accident. If you should have any questions, please contact either Mark Hillstrom of myself. Sincerely. s, ed '< V - f Kenneth J. Done Senier Mechanical Engineer KJD/ck cc: G. S. McClure w/ attachment J. D. Weaver W. H. Rushton G. Yace M. A Hillstrom File 14(16)1 r. i

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YOR K, PENNSYLV ANIA 17405/717 848 1126 YORK PLANT VALVE DIVISION OJerating Times For Purge & Vent Valves Several definitions of operating times have been associated with purge and vent valve operation.

Some clarification is in order: a. DELAY TDIE The amount of tima between the initiation of an event and the beginning of valve closure. During this time, the event is sensed by appropriate equipment, the valve is signaled to close, and closure just begins. b. MAXIML'M TECHNICAL SPECIFICATION TIME For a particular operating plant, the maximum time allowed for all valves to close after the initiation i of an event. This includes delay time. c. NORMAL NO LOAD VALVE OPERATING TIME Valve closing time with the valve in a.go flow - no pressure condition. Delay time is not con-sidered. d. VALVE OPERATING TIME - LOCA CONDITION The time it would actually take for a valve to close l during a LOCA. This time is affected by the type of operator and the opening or closing tendency of the disc. The most conservative approach for determining this time is to use: (1) the Technical Spec time plus a factor if the disc tends to open or (2) the normal no load operating time plus a factor if the disc tends to open, whichever is greater. Longer closing times are conservative, however, only if the valve is closing against an increasing pressure ramp. Each valve must be evaluated on an individual basis considering operator capability and pressure ramp characteristics. R. H. Zeiders. November, 1983 A L LIS C H A LM E R S CO R PO R A TIO N 1/5280 u

m NPPD rech. Spec. c/o. sing time /f second's. Stroke Time Used In Analysis Valve 230 MV Valve closing time used in analysis - 14 seconds Actual approximate valve closilg time - 4 seconds For closing times longer than 14 seconds, torques could increase about 10% posing no problems for operator or shaft ratings. Valve 245 AV Valve closing time used in analysis - 14 seconds Actual approximate valve closing time considering disc tendency to open - 9 seconds For closing times as long as 21 seconds, torques could increase by about 10% posing no problems for operator or shaft ratings. Valve 233 MV Same conservatism as 230 FFJ. Valve 237 AV Same conservatism as 245 AV. Valve 231 MV Valve closing times used in analysis - 4 seconds and'14 seconds Actual approximate valve disc closing time '4 seconds For closing times longer than 14 seconds, torques descrease because of decreasing pressure ramp. Valve 246 AV Valve closing time used in analysis - 9 seconds and 14 seconds Actual approximate disc closing time considering disc tendency to open - 9 seconds For closing times longer than 14 seconds, torques descrease because of decreasing pressure ramp. Valve 232 MV Valve closing time used in analysis - 4 seconds and 14 seconds Same conservatism as 231 MV. Valve 238 AV Valve closing times used in analysis - 6 seconds, 9 seconds, and 14 seconds Same conservatism as 246 AV. 1/3295

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YOR K, PENNSYLV ANIA 17405/717-848 1126 YORK PLANT V ALVE Dhfl510N TORQUE ABSORPTION RATING OF VALVE OPERATORS Operators for quarter turn rubber seated valves in air service must be sized to overcome the greatest combination of bearing friction torque (T ), rubber seating torque (Ts) and dynamic torque (Td).
3 Bearing friction torque is usually expressed as: 2 Tb = 4.71 D dfP where Tb = bearing friction torque (ft-lb) which acts to oppose valve shaft rotation D = valve diameter in feet d = valve shaft diameter in inches f = bearing friction coefficient between the valve shaft and bearing surface P = pressure drop across the valve in psi Rubber seating or unseating torque is expressed as: T =CD2 where s s T = seating or unseating torque in foot-pounds s Cs = coefficient of seating or unseating torque from test data Dynamic torque is expressed as: 3 Td = C D P where T Td = dynamic torque in foot pounds CT = coefficient of dynamic torque from test data ALLi$ CHALMERS COR POR A TION 2/4569 -...=..
ys '(~ As the valve reaches the seated position goir.g from opened 'to ' closed (approximately the~1ast 5*-8*'of travel) the operating torque is the sum of the seating torque and bearing torque. This is a maximum at the closed position: T =.Ts+T. Dynamic torque has little or no in-os h fluence at this point since flow is essecrially stopped. During thefinitial part of the closing stroke (from 90* to 10*) dynamic ~ torque and bearing torque determine.the operating requirements. Depend ' ing on valve geometry, orientation and upstream piping'and flow conditions, the valve. disc may tend to close or tend to open. This can cause the following conditions: 1. The disc tends to close because of dynamic torque and ' bearing torque opposes this tendency. Tod = Td-Tb is the torque that must be overcome by the valve operator. If Tb > T, the operator must be d able to overcomefthe absolute value of T -T - If d b Td > T, the operator then acts like a brake and lets b the disc close at a certain rate. 2. The disc tends to open because of dynamic torque and bearing torque opposes this tendency. If the operator ic acting to close the valve then: (_ Tod = Td+Tb The operator must overcoma the dynamic N-torque and the friction torque. Electric motor operators used to open or close butterfly valves typically supply torque to the valve shaft at a speed ranging from 0.1 to 3 RPM. These operators can be broken into 3 basic parts: 1. An electric motor usually 1,800 RPM. 2. An intermediate gear set (spur gears and a worm set) that decreases. motor speed and increases torque. 3. A final worm gear set that is "self-locking" and further reduces speed and increases torque. This is the part of the operator that attaches to the valve shaft. The torque absorption capability of this type of electric motor operator is the output torque rating of the unit which is based on the capability of the " weakest link" in the train (i.e. the electric motor, the inter-mediate gear box or the final vorm gear set). The direction of the torque that must be applied to the valve shaft has little effect on the gears or motor. If the valve shaft torque opposes the direction that the operator is running, the gears and motor are loaded in a normal manner which is, in fact, how these operators are sized. r Of9?do
8Y f If the valve shaft torque' acts in the same direction that the operator is running, the operator is then acting as a brake letting the disc close in a specified amount of time. When this situation occurs, the load actuclly seen by each gear set and the motor is less than for the reverse condition. This reduction of load is caused by the reversal of the friction component in the gearin3 A good analogy is the difference in torque required to raise a scissor type jack as compared to lowering it. The electric motor operator only develops torque as required to overcome external loads applied through the valve shaft. Except for slight friction loads, the internal components of the electric motor operator are not preloaded and only build-up loading in proportion to external torques applied. The same condition is not true for an air cylinder spring return operator such as the Bettis T-series. This type of operator (with spring to close) stores energy in the form of a compressed spring or springs during the opening stroke. The air cylinder, piston rod, and various other components must be designed to overec=c the increasing spring force and produce an additional specified operating torque during the opening stroke. In the open position these components remain loaded because the spring is com-pressed. When closing, stored energy from the compressed spring can be converted into torque if there is resistance to the closing motion from thu valve shaft. If there is no resistance from the valve shaft, no torque is produced and the internal parts that connect the spring to the piston are gradually unloaded over the full stroke to some preload point. ( If, during the closing stroke, the valve shaft applies a torque in the direction of closing, this torque is additive in the form of additional force to the components between the sprini,"and the piston. The torque absorption rating of this type of operator is the sum of the spring torque plus the additional specified torque developed during the opening stroke. All components in the operator are designed to withstand the forces developed by this combined torque. These torques can be seen graphicall'y in Figure 7A*/. dfh O' b Oct. nas ( 2 /11 !. !.
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s / LOAD STRESS ANALYSIS-CRITICAL VALVE PARTS The following shows a worst case condition of 1 LOCA torques imposed on critical valve parts. Note i that all stresses are well below allowable. t Stress. calculations as a result of seismic loads were submitted for these valves in the form of Allis- } Chalmers Report VER-0093 in 1972. i Although LOCA and seismic loads and stresses have not been combined in this report, examination of the separate reports' indicate very conservative results. I 1 1
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ML20083C619

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Dear Mr. Zeiders:

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ML20083C619

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