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Forwards Containment Purge & Vent Valve Operability Study, Per TMI Item II.E.4.2.Mods Being Made to Limit Valve Opening to 40 Degrees.Study Demonstrates Compliance W/Item II.E.4.2,Part 5
	ML20030C368
Person / Time
Site:	Waterford
Issue date:	08/19/1981
From:	Aswell D; LOUISIANA POWER & LIGHT CO.
To:	Tedesco R; Office of Nuclear Reactor Regulation
References
	RTR-NUREG-0737, RTR-NUREG-737, TASK-2.E.4.2, TASK-TM W3P81-1835, NUDOCS 8108260030
	Download: ML20030C368 (45)
	v • d • e

{{#Wiki_filter:LO UISI A N A j,42 OnAnONOe S1neer POWE R & L1G H T/ P O BOX 6008

NEW ORLEANS. LOUISIANA 70174 * (504) 366 2345 Ur ONdysYEO D L ASWELL Vce Presdent-Power Prodicton August 19, 1981 W3P81-1835 3-A19.09 C3)I

/ Mr. R. L. Tedesco Assistant Director of Licensing U. S. Nuclear Regulatory Commission / [ g,.. Washington, D. C. 20555

SUBJECT:

Waterford 3 SES d . p C TMI Item II.E.4.2 - Containment Cg i' go***T# n' - \\ 0* 9,/p, Purge Valve Operability Study 3s

Dear Mr. Tedesco:

4' / Thi [/ In accordance with TMI Item II.E.4.2, a containment purge and vent valve operability study was performed for Waterford 3. In accordance with the re-sults of the study (attached), modifications are being made to limit the valve opening to 40 degrees. We believe that the attached study demonstrates the compliance of Waterford to Item II.E.4.2, Part 5. Yours very truly, D. L. Aswell DLA/RMF/dde Attachment cc: E. L. Blake, W. M. Stevenson, S. Black Qool .5 I I J 8108260030 810819 PDR ADOC" 05000382 A PDR

i 1.0 Introduction i Item II.E.4.2 of NUREC-0737 delineated the NRC staff position on ensuring the operability of Containment Purge Isolation valves. Pursuant to paragraph 2 and of Attachment 1 to Item II.E.4.2, the purge valve vendor (Fisher Controls) was requested to perform a sensitivity analysis to determine operability limits of the valves. Reference 1 and its subsequent clarifications was used to identify related concerns which could have adverse impact on valve operability. These concerns are discussed below. 2.0 Response to Reference 1 (Questions are those of the clarification) 1. Question The AP across the valve is in part predicated on the containment pressure and gas density conditions. What were the containment conditions used to determine the AP's across the valve at the incremental angle positions during the closure cycle?

Response

The analyzed containment condition was a constant i4 psig and 3000F in determining the fluid conditions across the valve at all angles of rotation. (A constant 3000F was used in order to account for the long thermal time constant of the valve assembly rather than the brief peak temperature of 4140F which occurs after the valve is closed). JhP across the valve was considered equal to peak containment pressure (psig). Material properties were selected (during stress calculations) at peak containment temperatures. The effect of compressible flow in sizing Fisher butterfly valves is best explained by the following: AIR VS WATER SERVICE Whenever a Fisher butterfly valve is in a gas flow application the effects due to compressible flow are taken into consideration while determining the dynamic torque effects for each individual valve selection. This consideration is built into our valve selection procedures and requires a conscious liquid or gas decision in calculating the effective pressure drop of which the dynamic torque is a function. Fisher's philosophy concerning the effects of compressible flow on butterfly valves is presented in ISA Transactions, Vol 8, No 4, entitled "Effect of Fluid Compressibility on Torque in Butterfly Valves", written by Floyd P Harthun (Manager, Product Evaluation, Fisher Controls Co). A copy of this transaction is included as to this letter.

1 i < 2. Question 4 Were the dynamic torque coefficients used for the determination of torques developed based on data resulting from actual flow tests conducted on the particular disc shape / design / size? What was the basis used to predict torques developed in valve sizes different (especialiy larger valves) than the sizes known to have undergone flow tests?

Response

In determining allowable pressure drops across a particular butterfly valve at various angles of the disc, Fisher Controls uses classical " mechanics of materials" type equations to calculate stress levels at various worst-case locations in the valve assembly (specifically, various locations along the valve shaft). The approach to the analysis, the equations used, and the combination of the calculated stresses all make up a portion of Fisher's design philosophy for butterfly valves. This analysis approach addresses all of the different states of shear and tensile stress which are applicable to the loading conditions defined. Establishing the loads that actually exist makes up the remaining i portion of our design philosophy for butterfly valves. These loads range from easily calculated loads, such as bending due to pressure differential across the disc, to loads such as packing and dynamic torques which require a certain amount of testing combined with scaling in order to analyze all valve sizes. It is the factor of dynamic torque that produces different stresses at different disc rotations and disc geometries. Through testing and scaling Fisher has produced dynamic torque factors for incremental disc rotations for plate discs (which is the configuration for the subject valves). The model tests used to establish the dynamic torque values used in sizing were conducted using 4" and 6" test valves with various aspect ratios ranging from 2:1 to 14:1 (such as 3:1, 4:1, 5:1, 8:1, 11:1 and 14:1). The dimensionless aspect ratio (defined as the ratio of the disc diameter to the hub diameter) j was judged to be a significant parameter for evaluation of dynamic torques at various open angles. Capacity and Torque curves obtained from a typical test are enclosed (Attachment 3) to illustrate the method and general shape of the curves for type 9200 butterfly valves. 4 i

m , 3. Question Were installation effects accounted for in the determination of dynamic torques developed? Dynamic torques are known to be affected for example, by flow direction through valves with off-set discs, by downstream piping backpressure, by shaft orientation relative to elbows, etc. What was the basis (test data or other) used to predict dynamic torques for the particular valve installation?

Response

All Fisher sizing data is based on dynamic torque determination tests which were performed with uniform flow profiles and on valve discs with representative geometries. Upstream of the Waterford purge valves is only a straight run of duct with no elbows, T-connections, etc. Flow through the valve is expected to be uniform. 4. Question When comparing the containment pressure response profile against the valve position at a given instant of time, was the valve closure rate vs time (i.e. constant or other) taken into account? For air operated valves equipped with spring return operators, has the lag time from the time the valve receives a signal to the time *he valve starts to stroke been accounted for? NOTE: Where a butterfly valve assembly is equipped with spring-to-close air operators (cylinder, diaphragm, etc), there typically is a lag time from the time the operator starts to move the valve. In the case of an air cylinder, the pilot air on the opening side of the cylinder is approximately 90 psig when the valve is open, and the spring force available may not start to move the piston until the air on this opening side is vented (solenoid valve de-energizes) Selow about 55 psig, thus the lag time.

Response

l l When calculations were performed to determine the maximum allowable l open angle (provided in Attachment 1) the assumption was made that the valve had to close against peak containment pressure. i Since this (conservative) approach was taken, a time history study was not made, and therefore, valve closure rates and response lags did not have to be considered, t l 1

4 j i ) 5. Question: Provide the necessary information for the table shown below for valves positions from the initial open position to the seated position (100 increments if practical). Valve Position Min Degress-900 Predicted AP Maximum SP (full open) (across valve) (capability) l 1

Response

a J l In determining allowable AP vs angle of opening for the subject i valves, there are several considerations to take into account. j

1) Allowable AP based on the strength of the valve.

2) Allowable AP based on available torque from actuator.

3) Allowable AP based on the strength of the actuator.

The allowable AP based on valve strength is determined by a l Fisher computer program.~ The momputer program can be described j as follows. l l For a given valve at some angle of opening, the program begins by calculating the loading. This includes a hydrostatic load j on the disc, seating torque, bushing and packing torque and dynamic torque, i After the loading is determined, the program calculates stresses in the shaft, key, pin and bushing for a specific AP and compares these stresses to a material strength. This strength is based on 1.5 x "S". "S" is the allowable stress figure found in Section VIII of the ASME Boiler and 1: essure Vessel Code. S is i equal to 1/4 of the minimum tensile strength or 2/3 of the l minimum yield strength, whichever is less. For shear stresses l 0.75 S is used. I The program calculates stress and changes LP iteratively until i the allowable strength matches the stress. This determines the maximum allowable pressure drop for that angle of opening based on the stress at a single point. Therefore, this process is done for cases 1, 2, 3, 4 and 5 (as defined below) for each angle of opening. ( Case 1 - stress in the shaft at the disc hub due to bending and torsion Case 2 - stress in the shaft at the disc hub due to torsion j and transverse shear l Case 3 - stress at the pinned disc-shaft connection l I Case 4-- stress at the keyed actuator-shaft connection i l Case 5 - stress at the shaf t bushing l l

. 4 The program output shows a AP which is calculated at each point for each angle of opening, including twc 6P for case 1 (one based on maximum shear stress, one based on maximum tensile stress) for a total of 6 AP's. The smallest AP of these 6 is then repeated as allowable 6P at the bottom of the column. The actuator torque for the lowest AP (allowable LP) is also listed. Above 400 open, the allevable fP's (based on valve strength) drop below the accidenc criterion of 44 psig, as shown in Attachment 1. The required actuator torque vs angle of opening for a 44 psig drop (P =44 psig, P ambient) is shown in Attachment 1. The l 2 torque at 00 is the torque required to close the valve. This shutoff torque is 41,795 in-lb. The minimum end-of-stroke g torque output for the Bettis actuator is 48,500 in-lb. Therefore g the Bettis provides adequate torque for shutoff against a 44 psig pressure drop. The specified required torque at open angles less than 600 is torque required to open the valve further. Dynamic torques at open positions up through 600 tend to close the valve. Therefore no consideration of available actuator torque at open angle is needed. However the actuator strength must be considered for the case in which the valve is held in the open position. If the valve is held at 400 or:less the aaximum torque the actuator would be called on to supply is 46,716 in-lb (See Attachment 1). This torque is within the output rating of the actuator and would not cause damage to the actuator. As stated in the response to request #4, no time-history l study has been performed and therefore no " Predicted P" values are provided; the remaining irfrraation requested is presented 'n Attachment 1 to this document. 6. Question What Code, standards or other criteria, was the valve designed to? What are the stress allowables (tension, shear, torsion, etc) used for critical elements such as disc, pins, shaft yoke, etc., in the valve assembly? What load combinations were used?

Response

The subject 48" butterfly valves were designed according to the ASME Boiler and Pressure Vessel Code, Sections III and VIII. Allowable stresses were also taken fram the ASME B & PV Code. Loads considered in the design of these valves includes all typical pressure and flow induced loads. Worst case load combinations are used. Pressure and temperature ratings for these valves can be found in Fisher bulletin 51.4:9200 (Attachment

5).

NOTE: No requests numbered 7 and 8 were included in Reference 1. l [ c----.-

m 4 ' 9. Question For these valve assemblies (with air operators) inside containment, has the containment pressure rise (backpressure) been considered as to its effect on torque margins available (to close and seat the valve) from the actuator? During the closure period, air cust be vented from the actuators opening side through the solenoid valve into this backpressure. Discuss the installed actuator bleed configuration and provide basis for not considering this backpressure effect a problem on torque margin. Valve assembly using 4-way solenoid valve should especially be reviewed.

Response

The subject 48" vaives are equipped with Bettis spring-return actuators. This actuator design includes a vent to ambient l on the spring side of the piston; therefore, if the pressure side of the piston is vented (through the solenoid) to the same ambient as the spring side, no pressure differential will exist across the piston ao a result of the accident containment pressure. 10. Question Where air operated valv2 assemblies use accumulators as the fail-safe, describe tbe accumulator air system configuration and its operation. Trovide necessary information to show the adequacy of the accumulator to stroke the valve, i.e. sizing and operation starting from lower limits of initial air pressure charge. Discuss active electrical components in the accumulator j

system, and the basis used to determine their qualification l

for the environmental conditions experienced. Is the accumulator system seismically designed?

Response

This request is not applicable to Waterford Unit #3, since none of the subject valves are equipped with accumulators as a fail-safe feature. 11. Question For valve assemblies requiring a seal pressurization system (inflatable main seal), describe the air pressurization system anfiguration and operation, including means used to determine tnat valve closure and seal pressurization have taken place. Discuss active electrical components in this system, and the basis used to determine their qualification for the environmental i l condition experienced. Is this system seismically designed? I l l i l' I. .-r, ,. _.,, - ~ .,-.--w,.,-,_-mv. .__m,,,,... For this type valve, has it been determined that the " valve travel stops" (closed position) are capable of withstanding the loads imposed at closure during the DBA-LOCA conditions.

Response

This request is not applicable to Waterford Unit #3, since none of the subject valves are equipped with inflatable seal rings. 12. Question Describe the modification made to the valve assembly to limit-the opening angle. With this modification, is there sufficient torque margin available from the operator to overcome any dynamic torques developed that tend to oppose valve closure, starting from the valve's initial open position? Is there sufficient torque margin available from the operator to fully seat the valve? Consider seating torques required with seats that have been at low ambient temperatures.

Response

The valve actuators will be provided with internal piston travel stops to limit the actuator stroke to a maximum of 400 valve open position. This modification will not adversely affect the valve closure or seating performance. i l l I

. 13. Question Does the maximum torque developed by the valve during closure exceed the maximum torque rating of the operators? Could this affect operability?

Response

The response to Request #12 and #5 above, in conjunction with 4 the information provided in Attachment 1 adequately address this subject. 14. Question. Has the maximum torque value determined in #12 been found to be compatible with torque limiting settings where applicable?

Response

This request is not applicable to Waterford Unit #3, since none of the subject valves are equipped with torque limiting devices. 15. Question Where electric motor operators are used, has the minimum available voltage to the electric operator under both normal or emergency modes been determined and spec ~ tted to the operator manufacturer, to assure the adequacy of the operator to stroke the valve at DBA conditions with these lower limit voltage available. Does this reduced voltage operation result in any significant change in stroke timing? Describe the \\ emergency mode power source used.

Response

This request is not applicable to Waterford Unit #3, since none of the subject valves are equipped with electric motor operators. 16. Question Where electric operator units are equipped with handwheels, does their design provide for automatic re-engagement of the motor operator following the handvheel mode of operation? If not, what steps are taken to preclude the possibility of the valve being left in the handwheel mode following some maintenance, test, etc., type operation?

Response

This request is not applicable; see Request #15, above.

-g_ 17. Question Describe the tests and/or analysis performed to establich the qualification of the valve to perform its intended function under the environmental coaditions exposed to, during and after the DBA following its long term exposure to the normal plant environment.

Response

No analyses c? tests were done to environmentally qualify the subject valves.

1) Pressure-Temperature - The temperature pressure environmental conditions of 44 psig and 3000F (with a 4140F spike) fall within the design rating of the valve.

In accordance with Fishers recommendation, all elastomeric parts will be replaced every 4 years.

2) Aging-Radiation - The subject valves have EPPM seats.

Seat material degradation cannot be accurately predicted in terms of seat leakage. However, between the in-containment and the in-annulus valve is a 1" line leading into the annulus. This line will draw any leakage through the valve into the annulus to be eventually exhausted by the ESF grade Shield Building Ventilation System. Additionally, in accordance with Fisher's recommendation, all clastomeric parts will be replaced every 4 yaars.

3) Seismic - The seismic testing done to qualify the subject valves is described in Attachment

" Dynamic Test Program on Bettis T-420-SRI-M3".

4) Wind loading, missiles generated by tornadoes and explosion conditions qualification is not applicable for these valves.

5) Qualification of solenoids and limit switches will be addressed by the NUREG-0588 response presently scheduled for submittal in October 1981.

19. Question Where testing was accomplished, describe the type tes ts performed, conditions used, etc. Tests (where applicable such as flow 7 tests, aging simulation (thermal, radiation, wear, vibration endurance, reismic) LOCA-DBA environment (radiation, steam chemical) should be pointed out. I

Response

See Response 17 and Attachment #6 for details of the dynamic testing performed on the subject valves.

L 20. Question Where analysis was used, provide the rationale used to reach the decision that analysis could be used in lieu of testing. Discuss conditions, assumptions, other test data, handbook data, and classical problems as they may apply.

Response

This request is not applicable to Waterford Unit #3, since an analysis was not used ti qualify the subject valves. 21. Question Have the preventiv'e maintenance instructions (part replacement, lubrication, periodic cyc1.ing, etc ) established by the manufacturer been reviewen, and are they being followed? Consideration shoul,d especially be given to elastomeric com-ponents in valve body, operators, solenoids, etc., where this hardware is installed inside containment.

Response

The maintenance instruction have been reviewed and will be followed. F

References 1. Letter from D G Eisenhut to All Light Water Reactors dated September 27, 1979, and Clarifications f 4 -_ - _. _, _... _ _ _. _. _ _.. - _ _ _. _ _. _ _ _ _. _ _ _ _., _ _. _ _, _, _..,. ~ _ ..,______.,,_....,_,,.,____.,,_.c._

i i l l 1 1 t Attach:nent 1 - Allcwable.iP vs. Angle of Opening i Required Torque vs. Angle of Opening I I s i ~ - -,., _...

MAX. OPENING ALLOWA3LE REQUIRED ** MIN. END-OF-STROKE MAXIMUM ** ACTUATOR ANGLE .1P CLOSING TORQUE ACTUATOR OUTPU' REQUIRED TORQUE RATING (Degrees) (PSIG) (in-lb) (in-lb) (in-lb) (in-lb) 0 65 41,795 48,500 41,795 55,500 10 65 10,203 48,500 32,389 55,500 20 62 48,500 46,716 55,500 30 62 48,500 46,716 55,500 40 62 48,500 46,716 55,500 50 13 48,500 63,779 55,500 60 6 48,500 93,164 55,500 70 2 48,500 143,390 55,500 80 1.6 48,500 149,072 55,500 90 1.6 48,500 149,072 55,500

Dy namf.: torque which tends to close the valve exceeds the frictional torque in these cases.
- All required torques are based on a 44 psig drop with P = 44 psig and P - ambient.

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e__ 1 l 1 i 1 l t i l I t J ( 4 i Attach =ent 2 - ISA Transactions, Vol. 8, No. 4; " Effects of Fluid i Compressibility on Torque i; in Butterfly Valves". 5 I I I I I l 1 4 l 1 I e I r a i l 1 I 1 f 1 I I 1 J l i 1

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REPR iTED FROM Volume 8, Hamber 4 3 1969 . sg.g, "f,* A S 184 TRANSACT!0NS A publication.>f INSTAUMENT SOCIETY of \\MER!CA T ) Effect of Fluid Compressibility on Tarque in Butterfly Valves 1 FLOYD P. HARTHUN Compliments of Fisher Controls Company

l% % r $1 % %% 4( *[ h l% s 4.El li A s. Po Effect of Fluid Compressibility on Torque in Esti:erfly Valves

FLOYD P. H ARTHUN+

Forher Gm errwr Coni;'.m.s \\taruu; ton 1. Iowa > A tec9nten.e is cresented by wtNch the shai torque resulting from f'urd flow thrcugh butted!v valwes can be determ, red with reasor'ab!e accura:y for both comp essible and mcotoressible flow. First. the ge,eral torace re:at.ceship fer mcompressible flow is estabbshed Then. an effective pressure d fferential is defmed to extend th's relationship to erclude the effect of f'uld comcress:baty. The apphcation of the techn.que showea serv gecd aa<eement w in esperimer'tal test results INTRODUCTION DEVELOPMENT OF GENERAL TORQUE RELATIONSHIP THE %PPLICATION of butterd) sabes in var 100s automatic control systems requires proper actuator sizmg for The total shaft torque required to operate butter 3) edicient control. Thus, a thorough knowledge of the salves can be separated into two major comoonents' riuid reaction forces actmg on the sahc Jm is required. Extensise experimental work'" has been performed in

1. Dynamic torque-that portion i the total the past to establish a relationship to determine ttese operatin g torque attributab' : to tb. fluid reaction forces and thus determine the resultant shaft torque. The force of the dowing mediu. v.ing on the sabe general form of this relationship has been established and disc.

i confirmed. Hewever, by using the classical fluid momen-1 Friction torque-that portion of the total tum approach, a similar relationship can be obtamed in operating torque attributable to friction in the which the torque is show n to be directly proportional to packing and bushings. i the measured vahe pressure differential for a gisen dise position. This relationship along with most of the Since each of these components is independent of the presiousiv published torque information is adequate for ther, a separate evaluation of each component arTords incompre'ssible floa. Although the efect of fluid com-the best approach to this problem. This msestigation is pressiblity on torque has $cen recognized. no useful lim ted to an esaluation of the d>namic torque com-relationsh'ip has been deseloped. The pnman o b-p nent. If the fr:ction on the valve shaft is assumed to be iectise of this investreation is to extend the estab'!ished independent of direction of rotation, it can be readil) 'orque relationship to me!ude the efect of fluid com-isolated. The torque required to rotate the valye dise is t measured m a c!ockwise and a countercleekwise diree-pressiNhtv. tion through full trasel. Since friction always oppose 3 motion the di!Terence between these salues wi!! be twice

rrnemed a e e tw is A Annui cerre-e-ee - e; w, w

%mh E., peer the actual shaft friction. 281 1%A Ir.msacn m Ibl.~ h J

The dynamic txque for hmtertly sahes n a function Combining Equations 17t it, ard it of the riuid reaenon force > actmg on the sabe dne, it would he ditheult to determme these forces by pure!) To = B/B.B BgD SP 410) anal)tical techniques. Esperimentaldeterminanon of the 4 pressares and selocity proti!cs in the immediate area of or the dise a ould aho be qu te ditticult. Ilow es er. if a control s clume is selected so the boundaries are points of know n In = K, D S P i 10. A ) pressure and selacity, an analyns of these forces can be w here made from the change m duid momentum through this control s olume-BlB:B,Ba To N. f!O-ID =- = - - 4 D P INCOMPRESSIBLE FLOW An esprentor for dynamic torque n desefored Equation (10-B)is defined as the dmiensionlew torque mumir-lncempressible tlow This torque is a function coetlicicat w hieh can be determined esperimenta:1 from 3 of the rit. reaction lerce. F.and a moment arm. D, w hich tests conducted with meompressible t!ow. n a characteristie dimen> ion of the uke dne. T = p F. D (1) COMPRESSIBLE FLOW 3 l'sme the dard momentum approach. the force. F. n Thed> namie torque fer butterdy sahens proports nal -ei. en' b. to the ma3s riow rate and se!ccity change through a selected control solume for both compressible arid F = Alal~ 12) incompressible flew li c.. Ty x Afa t't Therefore, the approach used to obtain an espressten for this torque assuming incompressible dow can be cuended to F = sum of esternal forces acting on fluid compressible ticw by re.detinmg these two uriables. 31 = mass dow rate First assume that the selocity at the sahe dne.1;. Al' = dmd s elocity change through the eentrol is proportional to th e velocity change through the control solume volume. Then. the dynamic torque can be espressed as The mass dow rate. 31. is gisen by To x 31l} till 31 = vA l' (3) The selecity at the sabe d:sc is gisen by Bs us.ng a proportionahts constant. B. the mass flow 3 Ik " {1 i rlte can'a!so be de6ned as' II2' j Af = B AlvaPF 2 (4) 3 Equations 83) and 14) are combmed to obtain the follo,v' By combming Equations Uli and (12; the dynamic torque is show n'to vary directly as the square of the mass mg esprenion for t!uid selocity : tiow rate and insersel,* with the fluid density at the vah - I' = BJaP'pj U) dise-82 The se!ocity change through the contras selume. 31'. b*1~ 3 2 in Equation (2) can be espressed in terms of the selocity at the sab e disc by use of a propornonahty constent. B, Determining the flow rate of a cornpresuble duid F = B:31l' (6) through a control salve by analytical techmques is quite ditTicult because of sabe geometry. T he major problem By substituung the expressions for mass flow rate is t estabhsh the pressure dirTerential between the sahe Equation f4: and duid selocity Equanon (5)into Equa. tion i6) the force on the uhe dne is inlet and the sena contracta. Howeser, by de6ning the l physical system in w hich the vah e n instal:ed to conform 2 F=B B AAP (7) with specifications gisen by the Fluid Contrek Insatute i 2 For a gisen sahe size. the flow area. A.for any ang!c of (FCIL'2' empirical relationships dese!eped speci6eally disc rotation. F. can be written as for determining dow rate for control sabes can be considered. Sescral such empirical relationships have i

D:

been deseloped; howeser. only one. the Unnersal Gas A=B H) Sizmg Equation '2' has been show n to accurately detine q the dow rate for any uhe con 62uration. This equation The force. F. acts upon a moment arm w hich is a function is gnen by of the dise diameter. D. Now, the dynamic terque can be f 59 o4,3P l written as $20 0 = \\ GT,C C4 sm 1 1 (141 -P i CC L i :\\ P k To = B FD H; i 3 ISA Tr.;m ;rram NthJ 282

Equation ilai can be rewritten to ebtain an equaa!ent incompressible Sow expression for mass now rate. -CC ~ gj To = K D'P sin d C4 i i _59 64.AP vi, C C:C, sin 115) .t/ = 1 Oe P i s For consemence the form of Fquanon t:41 is simpii6ed. To = K D ' A P. C5) The sine funenon in Equations I!46 and (15iis used to whwe detine the transinon between incompressible dow occur. .lh ~ s;n: 9 cg tmg at low pressure ratios t3P P l and critical flow o, = p, i l_et L '9 "4 ~5) 64 F Equation CN is de6ned as the pressure ditierential 9= IIN contributing to the dynamic torque on buttertly sahes r -c'c,y y'- "d with condinens of compressible !!ow. Rew riting Equanon il5:in the following manner - EXPERIMENTAL RESULTS .\\f = 1 Ons g:P C C:C,F II') 1 The nrst step m the expenmental esaluation was is The factor. F. n bounded bs the followme. estabitsh *he dimension!ew torque coeme:ent. K.. as :t E = sm H foe 9 < n 2 function ? sahe dise retanon as denned by Equinon (ISI ( 10- B) A test was cor. ducted on a 4an. vahe under the F = 1.0 for 9 2 n 2 followmg centrolled condinon>. By subsntuting Equanan il~l for the mass t'ow rate m

1. TM W.e was installed in a 4-m. test line w;th a Equation il3e. the dynamic torque for a gnen sabe mimmum of 12 pipe diameters of stratght pipe gnen b) upstream.

pip tC C, sin 9):

2. The pressure taps aere located accordmg to FCI i i ^

119' To x specir: cations and attached to the test lme

d according to specineatien, m the AS.\\lE Pow The only parameter in Equation (10) that cannot be av.1 Tes t Cedc/ *'

readily ontained is the density at the sahe J:se, p,. 3 Water at ambient temperature was used as the Assuming that the change in the ratio of fluid den 3ity at t!owing medium. the vahe inlet to rluid den 3ity at the sahe dise with

1. The inlet pressure and outlet pressure were held mereasing pressure ratio is small relathe to the total constant.

change in mass Sew rate. the torque expression can be 5 The test was conducted at a low pressure ratio simphned m the fellowmg manner : 13P P = 0.0SSi to ensure incompressible riow. i To x PgC C: sm 6)2 C0i i Therefore. for compressible Dow : ~ f fl l l l l l 30 To = K P tC C: sm d) C1) i i l j j For small salues of pressure ratio (SP'P ) Equatien Cli 28 [ i reduces to the incompressible torque relationship gisen j l i j by Equation (10- A). 2.t f i As SP P ~ 0 I p; i y sm 6 = 9 (radians) } l l l l l [\\ I l l I' I',[ '\\ To = K 159 64) aP C2) i f' r' j i l l l 4 The espression in Equation (22) is equivalent to the expression in Equation (10-A): 8 f l l l l j K q5464)23P = K D aP I 3 i .t K: * [$9 C3) b O0 10 20 30 a0 50 60 70 80 90 By substitunng the e.pression m Equation C3) for the ANGLE OF ROTAilCN. DEGREES coeMeient A.: in Equ; tion Cil. a general expression for dynamic torque for cocnpressib e dow is obtained usinF Figure 1. Dimensioniese toenue coef ficient. 4-in. butterfly the dimens:onless torqae coemezent estanhshed for valve incompressibfe flovv: P, = 100 psig. P =.s10 psi. 283 /S 4 Tra naane iW A..h 4

180 720 j j l I I j i i . loo 64C o-TEST DATA l o-TEST DATA - WAIERli l i l 4-T =K.DtPl l a. 'i TKh't 140 l j soc gp, } 3 l3 s 120 l3 j as ?- l l l g o-EST DATA - air fc g l - 100 e 400 y0 i 2 32C a o O I I O l l ' c\\ O' l l l J f\\ $ 2' j ./ i 1 3 40 l l l: 4

E 160

? l l i h b j l yli j 1 I ! g-f' ) E* I I 0 10 20 30 40 50 60 70 80 90 0 10 20 30 40 50 60 70 80 90 ANGLE OF ROTATION. DEGREES ANGLE CF POTATON. DEGREES Figure 2, Dynamic torque vs. angle of disc rotation, 4-in. Figure 4. Dynamic torque vs. angle of disc rotation,8 in. butter ly valve, comparison of experimental results with butterfly valve, comparison of experimental results with d calculated torque, incompressible flow: P, = 100 psig, calculated torque, incompressible flow: P = 100 psig, AP = 5 psi. AP = 5 psi. Torque measurements were made at selected mere-ment betw een mea 3ured torque and the torque calculated ments of disc rotation 80-909. A transducer, consisting using this coeMeient. of a steel bar with strain gages attached. was fixed to tne The next step was to serify that the torque coe:ficient vahe shaft and used in conjunction with an oscillograph is indeed applicable to other vahe sizes provided geo-I to measure and record the shaft torque. The data from metric similarity is reasonably well maintained. The this test w ere used to determine the dimensionless torque results on Figures 3 and 4 again show ser3 good agree-coemeient plotted as a function ofdisc rotation on Figure ment between measured torque and calculated torque

1. The curses plotted on Figure 2 show excellent agree-for two 8 in. valves.

720 360 l l c-k:KfD'AP l l[ c40 320 l 4-fEST DATA 560 280 INCOMPRESUBLE' i[Y FLOW l DYO i s-4BC ,. 240 i 1 9^ ^' 400 200 0 32 s,0 ll !Y \\- N' I /Y! l 20 3 I i 1 11 li

1 i

160 ^0 b' i DM / i 0 0 10 20 30 40 50 60 70 80 90 0 10 20 30 40 50 60 70 20 90 + ANGLE OF ROTATION. DEGREES VALVE FRE55URE DROP AP. PSI Figure 3. Dynamic torque vs. angle of disc rotation,8.in. Figure 5. Dynamic toresue vs. watve pressure drop, 4-in. butterfly valve, comparison of emperimental resuits with butterfly valve, 60* disc rotatson, comparison of emperi-calculated torque, incompressible flow: P, = 100 psig mental results with calculated torque, compressible flow: A P = 5 p ai. P, = 214.4 psia, flowing medium = air. 15.4 Tramas : n l'd.n k 4 284 .-,.4,

f l i i l 90

400, SC 360 l

l l o-TEST DATA l l l f i e-TEST DA A i 32C I i ,' fl l C-T =K,DhPklNCOMPRE551$LE)[l\\ i 7C I% OP ^ o a a3 c\\ a,7 = K /Dh o, l l['! jk E l l l l I / 3 f 50

~

e 24C II l !/ l\\ E l l l ! l/i u 40 200 l !/ l e} l i i / j j O u 30 $ 160 h 8 i z 2C - 12C I I 5 f [! l 9 I l ! [p.

E I

y >/' yl f l g, l l i !/[ IN ? 0' T ~.n A_ 0 10 20 30 40 50 60 70 80 90 t --g'eV' N ANGLE OF ROTAT!CN. DEGREES 0 F gure 6. Dynamic torque vs. angle of disc rotation,4.in. butterfly valve. comparison of esperimental results with ANGLE OF ROTAT:ON. DEGREES calculated torque, compressible flow: P, = 114.4 psia, AP = 5 psi (.1P/P, = 0.0444), flowing mediurn = air. Figure 8. Dynamic torque vs. angle of disc rotation, 4 in. butterfly valve, comparison ef test results with calculated It should be noted that discs in the two 5-in. vahes torque, compressible flow: P, = G4 4 psia, AP = 30 psi were of substantially ditTerent gecmetric shape. L~ sing (^#l#' ) * ( * 'i'i** ' "* * ) ** i" 9 "*d i"* =

i'-

f' the ratio of disc diameter to hub diameter as an indicator. these ratios were 4.56:I and 3.55:I for the sabes used to similar to the disc in the 4-m. test sah e used to establish obtain the data for Figures 3 and 4. respectnelv. The the torque coetricient K,. ditierence in torque magnitude for these sahes 'with a The extension of the dynamic torque relationship to -l 5 psi pressure di'Terential shown in Figures 3 and 4 is include the etTect of fluid compressibility is accomplished i the result of this difTerence in zeometrv'. The disc in the by deSning an efective pressure di:Terential as show n in 3.in. vahe used for the test in F'ieure 3 Eas acometrically Equation 125). The cunes on Figure 5 show the transition ~ from incompressible flow to critical flow with mereasing penure ra r e set at & h rotanon. 18 0 l Here again there is sery good agreement between the i 16 0 terque calculated using Equauen 124) and the experi-

KDhF, j

mental results. The incompressible torque curve is also 3 I 14 0 shown on Figure 5 to emphasize the etTect of :!uid a-TgDh P,i l -l compressibility. i e i The curves on Figures 6 through S are prestnted to a3 120 Z o - TEST'DATj j f. compare experimental results with torque calculated MO I usmg Equation (24) for full 90* dise rotation. At low uj l l l pressure ratios, the torque using air as the flowing i O ~ I medium is essentially equal to the torque for incorn. 80 l k pressible flaw (Figure 6). As the pressure ratiois increased. l l I I the etTect of fluid compressibility becomes more pro-o g 60 1 nounced as shown in Figure 7. Once critical flow has k 40 been attained, no further increase in torque is realized l j ) by increasing the vahe pressure ditTerential as shown on c: l IIS"f'S-2 LJ \\ ~ Ce-r i CONCLUSIONS 0 10 20 30 40 50 60 70 80 90 ANGLE OF ROTATION.CEGREES / hniq ueispresented w hich ean be used to determine Figure 7. Dynamic torque vs. angle of disc rotation, 4.in. butterfly velve, comparison of experimental resu6ts with accuracy. The basic torque relationship deseloped for i calculated toeQue, compressible flow: P, = 64 4 psia. incompressible fl0w is ettended to include the edect of AP = 10 psi ( AP/P, = 0.1?S), ffowing mediurn = air. Iluid compressibility. The method presented is des eloped j e> e % j 885 ILt Tra nam.n s Gl. & N,>. 4 i 1 J

uung the Unisersal Gas Saing Equation to deane an V, = Prenarc J4erential a.iectmg dy nam;e ferque erkerne pressure delferential for the tranution from e = Flo. raie inwnpremue mair,d mcompressible flow to critical flow. Application of this C' " M* * " "

P""' N# "d '#

method show s excellent agreement with esperimental T - Absolate temperaturt,R test results r, = o> namie torque. :n 16 I = FLd seixity. ir-i p, = Fluid demory at untream prem.re tap 15 m ' NOTATION

'd " FI*d d'") ' dh ' di "' '

4 = F10* area, m 2 B,. B. 8,. 8, = Cen, rants.,( proportiena:n> REFERENCES C, = C, C. C - Certection fauor fer ur.atien in $;wme tie.:t rano i KeMer. I C. and Saumann. i F hn aary I@ Aeraay um.s C, = Gas sinng coe&ient Wdel Tees on 14urterdy Vahes " E4cher.58 m % = < 9 C, = Ffos coet% cc.t Re. ommer:Jed 5isniarv 5:ar.'a Js h>r 'tra me.~< ni P.ees.re r >- n C = N. rninal s abe Jume:er. m Dere m..rgre Centr.il Fair e i J >= Capaan.195 4 Flaid Centrak / = Force. :b instaute ine.. pqer FCI $s.: G = Specide grasJ3 3 Baren J F. and Schader. C a OcteNr 1%4 "The Ibekpmect A, = thmens enico 'orcue :whent e(a 1;naersai Gas 5.2:1g Eauation for Contral \\ ah es " IV4 Tr..ns Af = \\ tass km ra'e. ;o s 1 3:2-314 P, = 1niet prenare. rsu s Fi. = treasurement leurumen rs a n.1 ty,nar.::u s L"p a nnt to me .ir = Vahe presst.re Merentui. p i 4 S IIE Fwr Teu Co. i A5 Nil report PTC 19 5. 4-1959 i 15.4 Trartsactwns l'ol. 3. h 2 286

I s - Capacity and Dynamic Torque Curves Determined in Fis' r Lab. Tests for 6" Type 924) Butterfly Valve. i l I J - e - =. .-,+ -c

PROBLEM on DATE r - 2. n FISilER CONTROLS COMPMY REPORT 15 vs FIGURE 1 FLOW VS TRAVEL CHARACTERISTIC BODY SIZE G" DESIGN /TYPF Moo NF BODY DWG. N t GM - R SEAL CONSTRUCTION SEAL D E HEASURED PROTECTOR RING DIA. PROTECTOR RING DWG. ~7 r o I ATEr icAto SALL/ DISC DWG. F - M Dxno W.- A BALL / DISC TYPE - VALVE FLOW DIRECTION: GNORMAL GREVERSE O WATER TEST BODY INLET PRESSURE > loo PSIG BODY PRESSURE DROP 2 PSI ^ = 1W AVERAGE Cv t AIR TEST .n BODY IHLET PRESSURE PSIA BCDY PRESSURE DROP AVERAGE Cg = 100 .....+.... + t.,...-... , +.. -.. .....J......... . - ~...... m.......................r..............._.._...- .....-,r.... ......+........ .................. +............. _... ..........u... t. .+......... +..._........... t.....t..........~.+.......,.........,.... 2.. t.........., ....+ ..l........_.....-._... J........+o.... 4. .._.t....._ .......t. +...,..-.,.. 4...... . ~. .++.a.. .t........+...........................-.. ................................a... .+... 90 ....., p: :.....t..,..... .....__.;......... =. - - .4........+...... +. .........-..,..........n... ..r..... ..*,...t ...............r..................t.._...................................._.. 8 0 . + + u,+4 + o. n-. +,. + + + p++ + + +. A. 6 ,w+ . m...,. ... _.g....,......, 4.+-,... m ..... -... _...~. ..u. 4,........,.b.., 4,+,5.u. .+ + ..+. .+ A. ,4,. i .,,o..,. QS+,.4+++ .u b.. .g....+.1,. .p++.+.;+. .+....5.,p. ++++ .o* ,....,. u..+. .++6&6++..o.+++&+.+..+e+++.+ ..+.,+. 4 6. 6+e 4.. +++++ +.g ,.5,9 .+IL..,6,..-..... e,.+*,. 4 4. ....s+ ,.+ +..s

+4
. +

.u+9 + 4 ..+++,.+++-o,..-.-,.*..u..$.......*....T,+.-*.-"w'T+..6 -m....-.* ..-t w;. w. .++... .,,.o w.. 4+ .1,1+n+...m. >+++,++..+4 +.._.. 6.++,+...L,... ++.,.++++.[++,.-,+-+4.+++++.h..u.+fo,,m.,,.,.. as + >,+++.....v.n.... ..+. .4.+,.. .,+,1 .,++++n. L. 4 w 4 + +++ ,t + .++..+k..,..+. 4 4++. ...A. p o+*.,+.,-..I . 4++4n ++ .,&+++ .u. .u++-++++,.,.r++.e.+< +6++,. +t.+.- ++.++w . - +. +. +. + - w+& ou .+,-u+ +...+... .-u.,.o. u. + n. 96++++.+ ,+o ,+++e....+.+,-u.-.++ .I ~ t++o +4, +-+ .-o..+ v., p +,o + t + +- & ++++H

++ ****
+.

++++++4.v,..

+*.++.**

+ ..n.6++++++u + ' * + - + + .,+,4+*, . + n.& + + +. + 6..+ u + o.++.++++++ o.+... **... .'+.,4,.+. ++ .+ .u.L u.,+- v +.+.4.....,.+++.+... +++++.4 .+ +.,..+.++ o,..,,,. .. + .+w4.w.++o.o.*+n+4+,..-++-+%...-.u..**..+.6.. 70 +o ^*. + - +.. 4+ u +-.1..-,- -.o*. .. - ++: * .*+++ .o.t++p+ +nt.++e+ "++++++t**++I*,6+ ++,+++ ++ " ++'++.+.**+.

.+o

++++Hu*+r+++6+++t+**4*++H.++++e*+-++&.+++ +*-.t,+.&-++.4 ,,,+..&,..++.,.4.-+ + +.. +,. '.. + + +...+,.. .,..,4t...o t+++ .+ o,6o*+. 4+,, + +, (y ++ .+ o4 ,-o. o ' ..++++ m,.+ +n+p++++4-++ +++ + + + n. p, k+ + -

4. u + + + + 6 +.4..,*+

w+k..,..+.. ++..t..+ .+++ . e i ++ ++ + m*. + ..r.+.,.~.,.+..,..,4.L...+,.s.o,+..,yr.~++.-..o..tu..n. t,... i-,..

m., + s v

. r. + o.*+'Te m..-++++vi. ~.. .w ,~. 3: 4.++>++++,, +. s..+ -,++%,,,,+,. .......t ..o..+. ,+, ,+-+ .,,,,,o,. o +u r++.+ -++, .......-,,. +..... + .4 u o ++ ++++.+4. ",**+'*u*6*++++- H".4,+t,,".+++ p+h,.t,**.,.++e+t++4.+*"+,+.t,t.*.*.-++6+,+."..u .**+ .+*+ ..+. 6,4. ,.++ +++ +,t J gn +.. 44 .+..+ ++++.+ ++,+,, " +;+_ ,+..*, + t.. ,+>,+++++t++++$++4++ +++t.+w.++.+..4,$+.+,.+s++++..4,.+++++++.+.e..-++.,4-.,.

: *+-.

++ +-, - ^+ - -- W vv + 't,**s+.+-. +, +++.t++++e. + .**+.-+e$+,+.+++v<

,+ +++

t+ +.*+.. +.o.,f*4,+tH.e .+6.&.+.4++t.m.t.+.+,+&,,,+ +. + e u,*,++++.,...,,...t+++++,t+.., . + +, +. J 4*++t+t.+^+ e+..++ .,t, +.- ...'...o,+.. -.. *.., -+ 4 ++.++.+, ..+..,*+y-+..,64.. ....,d+ ....+....+,.. 6 4 +.e,...u. .+-+..4,,t4.up,.u.u+++.,*..+.-.- + w+ o,* o+ 4,+,6.* .+,..+.4.+,.,. +. + .. - + H , +. o,+.+. ..t.<+. , & + + + u. u+ +, +4 - -, + + + +++

+t+++

+++ +.6 .+, e+,t.,+. +. ..+ t....6.+..**+ n ++ + + + + + -. + + + + e.++,e+++ 4e.. +++.4-+n-*4.++++n+.e.A+ ++ +++ Q .+ ++ +..+1-t++ .+o++ 6u.. + +....... .. +..., + + +++o,...

u...t.,....-w..,w

.+. f, CM ++++++, + +.. +t ,++++4.-..+++++++. .+ n.+,e+++.t.. 4-, ,..n++...++.+..o..,+. .+m, +. ..*++.+n. + + + +, I Wv o % u,4,+ ++ w .++ .+.++ + +, *.. - +.+. ..+... ++.. ++. , +...,........,. .+.,..+. ++ +++e+

++++,..+..+.4++

....+. 14. .+. ++.+*-*., m .+..*.+++ *+++ 6.. 1 O .++++++r,.e....,t+++* ..++, F.4,. ..++...,.,.+4 .+ o 4. t u 4+..,A,+,.4..... 4.-,...,.....+++.+ ++.. -,++++. -.s ++++. + .++. . + + + y 4 y + +. 4. +, {,+, ++ +. - ~. ++ I. ,.1. +. u,.++ ++.++.++.&.t.+.,+o....m..+.t.-4..ej..+w+6.. 4 .&+. .+..+,,++ -.et. ++. l .. +. p e. + +.,4.. +.. - +., + + v.+tt+++.*6.,.+.,+.+,4.-.++~. .l. .++ .++ .o..I ,+ g o++.4....+. +,.. ,t..+.,.. + ...+ Z ++++94.+++. o+ m.+ ,+.. 4., .i +.+.+ 6,+ .++..s+.u.... ..4.+...+6,t-. ++.,.+..o...++++,..A ,r + e, . + + +,,., . +..+,. .I. .. +.. .+++. I,* +..~.+r+++.......-.+.+,,4,++,, ...,+ y m I.....+.+....._.... .+..+6.

t=..

64 e,+ O l}0 ...w +...+, 1....,, +

.6 t.+,

++ + +. + + ,+.:+ i.- ..,*,t+**,&

4. 4. ++ ++ ).

.,. l. s

4... +, +... t++4.,+++t..,,+,+..,.......,.+.+.1t.o,++,+.e......

. 6+..4 ++t +6.,+.+.e...,, q. 4 v +..t. .+ .+. +....,+,++.,4* u + e. + 4. 6,.. + 6, + + + l o, + ++ r 4..+

e.. t,...p+,,.4.~

.+..+ g ++>,.u, 6,+ u+ .++t*.,+. ...++. t 4... L.aJ ~*,+n+.++4..,,*.n.++,s.. . +.,, + - + .+++. t. s.a t. +,. .+ e<+.-

- *.t.-+...+..t +..,..+,.

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_ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ - Fisher Bulletin 51.4:9200, July 1976; "9200 Series Butterfly Control Valve Bodies for Nuclear Service". P

9200 Ser ies Butterfly H5HE.i[ n contrai vwe smus Contw& for Nuclear Scr vico F isher 9200 Senes vaes are uffset-d.sc butterfiy vaives w ith in ad,ustat io e a s t om+-r T-nru

eat suitah!c

, m.-. ~.. s Wren edy sinopot sLtof f requoements. Thm valves n f" g ohe_n usul.is nudear servmo s ahes for oe 'off appbcattns [ \\ f f v u.h as containment esolanon and fcr thrc ttbnq cr on of f Hsw r annol of c om p e.n e n t cnoang wa'er or a u m i!ia r y t 'r. = flu s i. , si J ;,# (%s yn criter a for pressure rerasnmg campon n's of 9200 i j i Sm es v a h, e s rrv et the wprements nf the ASME - m [ atvasony f iamencaa Soc mty of Mechanic 3i Engmeersl Go er and a cruaroa q avaitants witw ~ 4, v Pressure Vessel Code Sectiors lit vW VIH, and the va'.e \\ "S[,$',j t% f / assembhes can tie f arn.shed with tne ASMf pasmc na t N uoesis ea f.' stama syrnt of u ncar r-a f f(. t I The standrd plate 4 teel or cast steel 9200 Senes wafer- \\, ~ '~ m'e v#ve es msta :ed between ptehne flanges. An optional hf p.! I rfgp' '? 4{ s teel sing!e ftange stWe bod / s avaeb8e w th a ppelme i ' 8"'b '6 -/. f'3nge en ore enr1 and a buttwe'd;ng connection on the nr,, ie

l

-{ cdher end or weh a buttweld n j connact;on on born ends. 9,, (( j ;.,,/ " ) Iris opt onal const'uction can be welded directly to a L: *, n a c, conta ment sessel wall. f 4, r. (g s.s Iben saNet are avadab'e in 4 inch ttrmn 96-inch l Wes for process ter peratures to 400'F and. d=pand;ng upon s te, pressu e drops to 150 psi. r FQu:e 1. 3200 Senes Spe.nfecatsoa B 1 Valve Featurea s:e m:h Twe e55 Actuator i i I e Comphance with Nuclear Code and Other Regthements-F, sher Controls Company holds the ASME Certdicate of Authorizat.on to use the ' f & stamp sy mbol on these valve bo4 asserr bhes. M ASME requirements for e Exceuent Shutoff without Excessave Seating Torque-- Class 1,2, and 3 nuclear scrv ce vatves, as well as spec,ai c f f sr !.t st design anews J sc7 nrg con:act around 300 customer assemb!y, cleanmg, pain tin g, and p ackagin9 de q"e, s of d!sc circurr %nca Elestemer T or.g is fie'd req Jerements, can be met. In addition, comphance of valve a f ust % so th it <hoM! caq tue m y r t m ne.1 w.thcut ancf actuator assembbes with spectf+ed sewroc and environ-ens,sive d,rsT-ring ir te*fe renc e and as:,cciated high mental critena can be documented w th seismic analys:s wat.ng i a gna Refuc ed necrferen;e a'so mirirnges T nng r calculat.ons and/or actual test results ere to pm!c.g T.nng hfe e Economical-Standard plate steel construction recoaes sess extens.e nondestructr.e exarr:rbtrons than cas c ons r xteon. redacinq cest and Jehvery time S t a n.ta rdu ed v uve 'actu itor seo comt>ina tior s ensure e Reduced LeaOOff Pipmg Requirements-Sites su bcient actuator 5:nwe: wh<bs reduc no e'tuator select'on throi.ah 2 4.nt ne; oc., vane sh.ift packing on one 5,de of i % d w e nnly. On'y Cr.e %3k n!' connect o to D;pe l f.me 3nd On(UmPr'tanon (051 and dela( I

B ulletin 51.4 9200 Ptgs 2 Specifications / 5 ~ / l AMASLIC0ElG8BA-3200 series specificat on 0-1: C0h5TRilCT10h B ody,* Disc,8 and Retaining i ' il0lls AND B00f SIZES Offset-disc butterf:y control valvo MATER'R$ 8 Ring : a Steelplate fASME SAS15 body with adjustable e!astomer GR 70) or u other matonais avail. I T-ring seat contained between the able upon request retaining ring and valve body as Shaft: 17 4PH stainless steel shown in figure 2. Valve shaft (ASM E SA564 GRS30 H1075) sealed with packing on actuator side Taper Pins: Same material as shaft and with a blank-off plate on the Blank-Off Plats' (Through 24-inch other side. Availab'e in a 4, a 6 Site Only): 316 stainless steel u 8, a 10. e 12, a 14, a 16, a 18. (ASME SA240 GR3:6) a 20, and a 24 inch sites Diank Off Plate Bolting (Theough D200 Series Specification C-1: 24-inch Size Only) l Offset-disc butterf v contrci valve Sands;' Steel (ASME SA193 GR body with ad;ustable elastomer B8M) j T-ring seat contained between the Nets:# Steel (ASME SA194 GR 8M) retain.ng nng and the valve disc T. Ring: e EPDM (ethylene-face as shown in fegure 3. Valve propy!cne) or a nitrite u Vitond is shaft sealed with packeng on both also available for ocn-nuclear apph-sides. Available in a 30 through cations a 96-inch sizes in 6-inch Retaining Ring 0-Ring (Through I increments 24-inch Site Only): Et!?M j (ethylene-propylene) j M STRE FWh Mr W bm & Glank Off Plate Gasket (Through

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8 ~ four ffange boft holes (see figu os I and 4) for snstaffation between gasket of 304 stain'ess steel and a es s two pipeline flanges p r Crm' ) 187-1 and laminated, > raphite iEND CONECTIN 4 Through 24-Inch Sires: Mate (Grafoil') packing l STRi$ with ANSI Class 150 (B 16.5) Bushings: a Graph.tedmpegnated raised facel'anges bronze (bushing 2) or a alley G a i 30 Through DG-Inch Sizes: M ate (bushing 3) with a ANSI Class 125 (016.1) Bushing Retainers end Retainer i fiat face flanges (through 72 inch Tube: 310 stainless steel size only), e AWWA C207 l'ar.ges, Packing Follower: Stco8 I ). or a MSS SP-44 flanges Packing Lantern Rings and War.hers: 316 staintess steel i MIIEfM Kli - 4 Through 24 inch Sires: Compat- ' Packing Box Studs and Nuts: IPE3SNE' able with ANSI Cbss 150 pressure / Steel i' tamparature ratings for tempera. Thrust Coi!ars [ tures from +20 to + 100*F 838#' 888888'8 88 I-I/2 #8'A88 (IA'8'M 1 I 30 Through 90-inch Sires: a 7g

l&hre Vahe Sire): Cadmium-pfsted psig for temperatures f,om +20 to

'stael clamp @ps co'lars with brass ..y I +400*F (in accor iance with ASME warhers between collars and. Code Case 1 G 78. approved bearing surfaces 0 December 16, 1974) or a higher ~ 3A8/8 h '78f I 1/2 /*A'C ( Drocte celbrs pinr'ed to valve shaf t pressures upon request Actuator Mounting Bracket: . Fabricated Steel , M PRil559( SI utof f (O Degrees of Dice "M' - Rota tion) OPitAffYE With EPDM T-Ring: +20 to 4 Ferens$15I re Liss 150 psi TEMPERATIM' ' + 300* F JJ T3evege #1/=h 3 ries 75 psi With Nitrife T-Ring: +20 to FlowinD: See taue 1 + 200* F [ , o w.en - . ~

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L r m. _c.7=.L , mm,,,,, 2- .. m,_ i ~_ _,__.__.,_.c_ ,..,,._.,_.___._,,___m.

~_ -_ Bullstin 51.4:9200 1 Pags 3 Specifications (Continued) i With Viton T-Ring: +20 to ACTUATOR /VALnt e Push-down-to-open (extending +400*F (Do not use with water ACTION actuator stem opens valve) or over 180*F or steam) a Push down to close (extending i actuator stem closes valve) i' ACTUATOR TOROUE See table 1 REQUIRED MATihG FLANGE Compatible with welding-neck and FLOW DIRECTION Flow is permissible in either direc. j tion, but valve is normally installed with T-ring retaining ring facing CODE CLASSNICATICNS Valve body, disc. and shaft com-downstream ponents designed in accordance with aliowable stress levels as FLOW COEFFicitNTS See Fisher Catalog 10 specified 'n ASME Boiler and Pressure Vessel Code, Sections lil SliUT0FF Fisher Class VI (less than one bubble and Vill i CLAS$1FICATION per minute using air at a pressure drop of 150 psi for 4 through Vafve body essemblies available as l 24-inch sizes and 75 psi for 30 nuclear code Class 1,2. or 3 valve j through 96-irch sizes) with ASME "N"-stamp symbol d l DISC ROTATION e Clockwise to open or a counter-clockwise to open (when viewed TESTING REQUIRfD All nondestructive examinations I from actuator side of valve) through (NDE) required for Class 1,2, and 3 l 90 degrees of disc rotation. nu: lear-service valves can be furr:shed; for current list of NDE requirements, see Fisher Catalog 11 ACTUATOR N0UNTUIC Fa bric a.ted actuator-mounting s bracket is used to mount Fisher ~, Type 480-15, 481-15, 656 and PACKING B01 TYPE Leak e tw e packing box with 864 actuators. Style 4 adjustable nc emate leaboH I linkage, shown in figure 1, as used connecdon with Fisher actuators for travels of I 4 inches and less and valve shaft diameters of 1-1/2 inches and less. VALVE SHAFT See figure 7 i Fixed linkage is used for longer DIAMETERS travels and larger valve shafts. Actuator can be a perpend.cular to APPROIIMATE WElCliTS See figure 7 i (standard) or a parallel with pipe-i line (adaptor required for paraMc! mountmg of actuators requiring a 0?T10N Single fiange steel valve body with mounting bracket) with actuator to e full set of fiange bolt holes on a right (standard) or a left of vahe one end and buttwelding-end con-(when viewed from valve inlet) nection on the other end as shown m figure 2 or with a a buttwelding With perpendicular mounting in end connection on both ends. hontontal pipeline, actuator can Flanged end connecticn available as extend e above (stardard) or a noted in "End Connection Styles" below pipeline. With parallel above; buttweld.ng end connection mounting, actuat :9 can extend B available per a ANSI B16.25 or upstream or a d umstream. e as specified I L 1 'd d .r, ,.m.,.-_ ___,-,._-,._,..,_m__-.,,_-.,_,,__.m .r_, m. c

_ __ - -. - _ _.. - ~ . _ = - Culletin 51.4 9200 j Pags 4 t l J ~s / f Ai40 $'4G18 f 4 A ~ l = Atve soo.%GE yy',D'*['** ' aa=G t. 7 \\ } rowenessiow nino \\.

/ - vateseoor 8' ' AN '**

_ ' ~ 1._- ADJusTI4r} / SE T ECREW l j! l _ ~i[ ^ l . _ _ _/ / C 'Z__ 1_ Z T_1 '___ _1-^' # I

1

' N. '~-**"'*# j [ '__f I { 1- ~' 7 ( s i gP ( ~r t s*h ~ r1 i A ]1l @h b s.. j ir w s ) i 'd C' J. W n. 9 h a N3m' ; i n s I,, 4 ,.'s g' / 3 g C 048PRi sseog - ( t AihG 'S g ~.

-- V At% E D'sC

\\ 5 j \\ De %t* S FC P Vt lT *4 g k4.-' 'e A.JJif tf e% 5 5t f SC#tw ~% gg y,q,gg mi4G StatW 8tfAih 4G RahG A04Ulf aNG j St f SCRFW U RE tat %8hG pang SCREW J j i figure 2. 9200 Senes Specification B 1 Valve figure 3. 9200 Senes Specification C-1 i T-Ring Details (Optional Single.Flangel Valve T-Ring Details { Buttwe! ding End Construction) [p cisc ,m f--r nae asumma ame G iid[.N, j/-asaa opp com>senom c -stA.n.a.,cre etArs 1 i em OtA% A oFF @ 4' / + 1 w <", gl a4e A. d.s. w.msmg2 y ._..o...._, / r^ca'** aa* .m., p, ,. w g vj4hfqw$. , e ;. w r4 - m rgh.-- g 7 -ha151E rg \\ etAre sotraoG , \\,*F1(.,.,, StA%E CH 0007 @ s r.=>= a e N# ** rn,m.i.u.nu==annar. LY) eastsuu a a> m.ns is,rvaina e Pant ou a.ancee nemousa [ amca st .c.meano.n o.an. n. a n e. me. u.ncw mes mercmcAnov u onu. mor t seo on 30 RCst oR & AAGr4 $r2E5 (SPfe:FicAYs080 44 '5 figure 4. 9200 Series apesJicat;crt 6-1 Valve Body Valve and Actuator

The torques in the *' Actuator Torque Required ~

I CB!ectIOn column of the table are the maximum torques encountered when the disc is being closed (or opened) against the shutoff (0-degrees of Note d:sc rotation) pressure drop shown in the table. Pressure drops shown for open disc angles Valve and actuator selection can be made from (60 or 90 degrees) are the maximum f!owing table 1 for 4-inch through 72-inch valves, drops that the torques in the " Actuator Torque pressure drops to 150 psi (depending upon Required" cdumn will permit. (Where necessary, valve size), and process temperatJres from maximum pressure drops shown for open angles { &20tn +400*F (depend ng upon elastomer have been hmeted by strength capabihties of (' T-ring matenal selected and apphcation). construction matenals) i 1l

i B ullotm 51.4 9300 1 Page 5 i 4 1 8 j Table 1. Valve and Actuator Selectwn M AXIMUM PRE SSURE VALVE D ROP IPSl; ACTUATOR VALVE BHATT OPE R ATIVE BUSHING TOROUE PECOVVENDED ACTU AtOR I Of AME TER TEMPf R ATURE TYFE# R E Q'O TYPE AND SilE (IN C H E S) Openmg (Degrees) (INCH POUND $l O 60 I 90 j 2 150 49 7 16 3 410' e 56 5.ie 40 w. 35 ng w.r, Y 4 gg 3 150 59 1 21.5 525' 656 Si 40 w ' 35 a : sar%* l 2 15) 36.4 12.1 925' 056 S se 60 w 33 ps g m* 6 34 3 150 46.1 150 1250' F56 S.re 60

35 p+g wr: %*

2 150 30 5 10 1 1820' 656 S za 60 w 35 rs9 sure%* 8 3 150 434 14 2 2575' 480 15 S.ie 40 w 80 con s#oh' I 2 150 24.7 81 27808 48015 5.ie 40 w 80 ceg suns,' N 3 144 16 0 81 3960 48015 S.ze 60 w Bo os a se. coy i 2 150 22.7 76 4425' 48015 Size 60 w 60 rs=q e.rp%* j 9,j ,,4 3 150 270 90 6550' 490 S#,80

80 r s.a swoh' 7

65 5367 480 M Site 60

60 pq wwV 14 1 1 4 3

140 19 5 64 7950 E64 S d 6 a 20 w 90 rs.y s%p s* 2 150 t8 9 63 7785' 480 5.ie 80 a 30 p.g wrn J t6 1 12 J 150 22 5 75 11.900' 86 4 S,re' 6 = 20 w 80 t s.9 sa.uY 2 150 15 7 50 10.550' 864 5.se* 6 = 20 n 80 r+q u poY ,g ,.7 3 129 15 0 49 15.950 864 S.re* 1 = 20

80 es. > suppl,'

, g 2 0 d3 304 0 2 M 16 5 54 WW $64 sie* 6 = 20 w 80 m wa V 20 134

a.,qe t. pm g -

3 148 18 0 SS 20 550 864 S.re* b e 20 w Po ps o s.wch' +20 to +2c04 2 150 150 49 20.700 864 5.ie* 8 a 20 n 80 rsg sarcY V%n r RN 3 137 150 49 33.170 864 S.se* 10 m 20 a 60 s 5 4 64rY 20 to - 400 ' F 2 75 65 2.1 17.732' 864 Sire

8 a 16
80 rw scrW

~9 y 3 3 75 62 20 27.932 864 S se' 8,20 w 90 rw wr# f 2 75 63 20 28.830 564 S.d 8 = 20 w 80 psq suo# 3B ' 1 ', 3 75 59 2.0 46.S30 864 S re* 10 4 2 4 w 80 psq w. W,' j / 2 75 55 1.7 40.020 e64 S s? 10 a 20 m 80 PM sed y y, 3 75 52 17 64.770 864 Sve* 12 = 20 w 40 rsa 54.pY s 58U5 8H S # 12 a 20

W M g W,'

43 3 i 3 75 51 t7 97.750 Con'act F sher Represertc..e 1 2 75 53 17 83.555 Contact F. sher Rer e ertan.e 54 3 l'2 1 75 50 16 141.600 Cc,rtatt F ster Rep oser.tawe 4 2 75 48 15 103.585 Co, tact F. sher Pmesertame 60 312 3 75 46 15 175.660 Contact Fisbee Rep es, r. tam e 2 75 47 15 137.570 Cor'xt Festvr Re:.resertawe 66 4 I 3 45

4. 5 1.5 237.320 Centact Fest er Aerrasentit we 2

75 47 15 180.130 Contact F< sher Rectesen%e i y 49 3 15 45 15 313.630 Ccriart F.d er Peree' *o'U.*e l ,s....~..avs.,,,,,,...~~,p.n---.4 ..ww sa+o. %,s i e y w. p.. m o... e < ~ m v.,< a s asi is o e,s m.* a n a s. w v.t a u e... a 2 sm2 e..e v.ien .n .,.s v -.-. -u i c s o' r. 4. ~1 i g.,,,,. m.e,%..- m ~,.a w y v. v.. e w..% c,u.ne ee ,--c,.. ~- ~ w m..a.,s.... m ~. .. c,~w

s,.....w, e i m m a t.e w. a>.m

- e .~..#. +..% 4 ..v. r, w~.#. e. y, w <>..r.o.,or..sisn.y. % A!! pw sure drops shown are within the strength table. In addition, other actuator types, such as electric capabihtie; Of the rnatena!s shov..) m the and spr;ng-return pneumatic rotary actua* ors are also Specificat.ons" table. available m recommended combinations with 9200 Senes valve bod.es. All combinations m tablo 1 are predetermined Af ter deterrnmmy the proper valve size using Fisher Catal'a to have suffiaent torque output at the stated operatmg 10 and the string nomographs or shde ru e, refer to "ble l condi!40ns. Check the maximum allowable pressure drop at t.. appro-pnate open ang'e (either 60 or 90 degreest to be certain it equais or exceeds that which witl be encountered en service. Selection from among the recommended comb < nations reduces documentation cost and postbehty of delay. Contact ~ Pecommended Fisher actuator types, s+ies, and operating the Fasner saws representative if other combinations are preswres for e.xh *.efection are shown at the r>ght of the reqwred.

l Guit:tm 51 4 9200 Pays 6 / r LG% T As%VI % r W At t N A .I p I / \\ VN I x y y ___. N d /\\ ~ COYPO%t % T

i ACif M C00t tgG 0:4 L A% f WAf g a I

N.?-, / O V / A N /1 PN*N V"N V .% h D8 CC%fA %VF%f4f5%ft Du f % Pt CO% f As%*M %Y nf 55f t - ^ = C OJi &% f,L MP Mf A T C UN T A % *M % I iS 14 A h0% Ntat facnA%5fA f 4 0 s* A%4 f 4 b At h l 5 watef$ %ORY Ati v 6506 A'dV% % Athf% %DasMat( t CL Agg (t A 55 ) was sig N,uVatt y (t a$$ 2 a V ai 6Is C# 3 n A.

E 5 F,gure S. Typical Apphcations for Class 1. 2, and 3 Nuclear-Service Vahes Shoan in a Compone nt Cooling System t-- L o% r Ai% wt %' watt

- c o% F Ai% Vi% f 4 At L 4 \\ s%%'DE N OU f 5'hf s% % 31 h 0 v f $.C.E CO%f A6%YE NT CO%f A 4 Yt % f sL 55tt C D N ' en %VI N T C C %f As%VE%T bel &EL %ES%tL %E %%f L $f A%DA#o West a STYLE e20o sta es v At s b k i d*A A } b % 44 \\d pr,, g,%, e t A%u g rips t %: # L A%cf -- i L e>>ru%e e A%cr at.vf Wa to.%c e so ca%%ec t os suitvseto ws eso co%%fcnc% L-- sut ras toi%G e No co4%ectio% 80tN Ilivl5 8Utt alltf 3101t!i45:04 Cat tiot Butt attDt310 (f Ostthiitti naa CCuta:nwf at otti Figure 6. TupicalInstallations for Single-Flange 9200 Serres Valves wittr One Buttweld.ng End Connection and Ore Flanged Connection (Being used as Isolation Containment Valves in Ventilating Air System) l n g,t all ati Q n speufied when the valve was ordered, or a fin!d re-ad;ustment of the T ring may be required to attain the The actuator will be mounted on the vafve en the orientation desired shutoff capability. T-ring adiustment is provided specified when the unit w3s ordered. This orientation is by a compression nng and adjusting set screws as normally setected based upon the desad mounting posttion show-sn figures 2 and 3. m the pipel:no, ava.lst.le space at the point of enstall *in, etc. Flow through the valve can be in either direction, but the valve is normally insta1ed with the T-ring retain.ng rey For 30 inun and larger vah,e sees. factory seat leak testing facio I downstream. For 30-inch and larger sues, it may be j must tm performed w tn the valve in the same position as is deured to inst 0 :he va've such that the 1-rmg retaining ring j intem ded for the actual installation. For these farger faces the nerest manhole or other pipehne access point. vo in tt o s3me position as was This will facibtate T ring inspection and maintenance. s ve s. enst el t he-v al

Bulletm 51.4 9200 Page 7 I LETTE RE D DIMENSION V A LV E ABLE DIAMtTER WEIGHT OF Silt A 0 C E' F S OR FLANGE ASSE M BLY (POU NDS) 4 4 u0 o 50 8 $0 6 2:a 3.26 S. 8 3 64 70 ti 6 00 7 50 10 50 6 25 3.75 3-4 b 56 100 8 8 00 9 00 10 50 6 25 3.75 1 7 81 130 to 19 00 10 00 12 00 6 25 3 75 1 9 81 175 12 12 00 12 00 I a 00 7 62 4.75 1 1'4 11 50 120 14 13 25 13.00 15 50 7 62 4.75 114 13 00 375 16 15 25 14 50 17 50 7 f2 4.75 142 15 12 475 18 1700 15 00 19 50 7 62 5 00 1-1/2 16 75 520 20 19 un 17 On 20 50 8 75 5 50 134 18 88 685 24 23 00 20 m JT T 8 75 6 00 2 22 75 1040 w a t-. . s--.w .. u. e.,. t e.,... w -.n m i s. s e o, ne.., t.e4 iw om- .ii vsasuna t? As MF p LO%% LilO N I 4 p l (( [\\s__E-g-- 3 x r-- y I, l l

1

(~ / / \\, ef '- l< -/ ~' n> t 1 A 1 lj! - Fa i 4 os f s tb s ? E ) 9\\ s '_ q \\ \\EM NJ ( l f N'ML/ i k i / 'w d u_ w.. _p. __--t.---- +e + +, by ne 7. Dimensions (Inches) The 9200 Senes vanes are suppl.ed with a d,sc travel stop. 6 Pressure Drops If the v6e body and actuator have been c dered separately a) Ptnge of flowing pressure drcps or if the actuator his been rencsed for maintenance, be b) Maximum at shutoff certain that proper rotat,cq d.recteon sal be or,ta'ned from

7. Flow 9ates the actuator befata insta'Img.

a) %nir'um control led flow b) Normal flow ? If sprat-wound bne fbnge gasLets are to be used with the d htmum flow 4-inch through 24 it ch s res, ce certam the gaskets cre of

8. Masirnum allowable leakage rate a tge and size that v. ill not overbp the cap screw or 9 Spenfy the posit on in which the va!ve wi'l be insta4ed adjusting strew hwes m the T-ring retairyng ring. Under le q,.a;ve in hontontal pipehne with vaive shaft horizontal).

l'oe f:ange bclting compressico, spiral-wound QJuets Can Seat le3k testirl Will be performed Wah the valve in the be damaged by the cap screw or ad ustirg screw holes. same positron as is intended for the actu31 insta' tat:on. t

10. Nuctear-code class and all nuclaar and special rea".ements

11. Line size and schedule Ordering Inf ormation Valve Body information Application Refer to the Specifications" cn page 2. Rev.ew the desenp-When ordenntL specify:

tion at the right of each specification and in the referencer

1. Type cf Appicatico tab,e. Indecate the chosce wherever there is a telectron to al Throtti.ng or on 'off b) Reducing, re' ef, or back pressure

2. Control'rd f'uld Fnclude chemical Pnalys's of fluid if posible)

Actuator and Accessory Information 3 Som:fic grav tv of controned fb c 4 Fla d temperatt.re (norma' ard min rnum and max. mum Spec:f v the (1esned actuitor type and sein from it e appro-pnate vtJdtor bu%tro. Also re'er to the spec f c actuator a r +.c.py e m and axessory bucetms fer add.tional erdenng information 5 Ranae af t'omng w pressures

i j " Dynamic Test Program on Bettis T-420-SR1-M3 for EBASCO Services, Inc., i Agents for Louisiana Power and Light, Waterford Steam Electric Station, Unit No. 3". l l r I I i 1 l I I L

CvSrcMER carer No. NY-4234s3 FIS H"'9 C O'N"'R DI*S U' (W' *W"' V SELLER ORDER NO. 4D230-27 thru 32 and 7C62/-CD, FT & CC CONTINNAI. I!!VIS;ON AGENT ORDER NO. 026M-55143 and 001-70350 DYNAMIC lEST PRCGRAM ON BETTIS T4:C-SRl-M3 ACTUATOR FCR E3ASCO SERVICES, :NC. AGENTS FOR LCCISIANA PCWER AND L:GHT , '. *~~~ ?;> h.:\\ XATERFCRD STEAM ELECTRIC STAT:CN ' T-U! UNIT NO. 3 t, J ,,.....-~...,.a. +.. ~ K.. s

.: .._s-=.====,==. 1 p.

s,, 9 ,. :. - -.. '.. b u. < . _ -.-,--:. ~n # : 's,'" ' ~ La

j. A'.;

- r. W' },'..-- ; '.. " >, 'q.<.,.,,' Rc --w::'< DATE: June 29,1979; Revision 1: Septe:::her 16, 1979 W0 PREPARED BY: Eric P. Ringle, Ho]ect Engineer j i REV: EXED BY: c& f fl Carl D. Wilson, Manager, re3:ing and Analys:s s.. A APPROVED BY. pi:~hard E. Hoccer, Manage: Of Eng:neering

FISHER CONTROL.S COMP).::T Co.wixm.u. Dn imo:. ( k 1 TABLE OF CO.'.* TENTS i CONTENTS PAGE 1.0 In trod u c ti on................................................... 1 2.0 Test Ass mptions............................................... 2 3.0 Scope of Qualificacicn 4 } 4.0 Test Procedure................................................. S 5.0 Test Photographs 8 1 f i 4 t l f i s o i I i

e l FISHER CONTROLS COMPANY I r co.m.w mi. Dmme.x 1 (' 3 l \\ 1.0 - T.".'R0DCCTION l l Fisher Controls Company hac ccmpleted a dynamic test program on a Bettis T420-SR2-M3 Actuator to demonstrato its ability to per:orm during a seismic event. This test report is being submitted to qualify some identical and similar anaa-8 cars on Ebasco Purchase Order NY403483. This report is written to meet the sei =ic requirement.3, under dynamic testing, in Ebasco Specification LOC-1564.109A. In adc:ition, Fisher controls Company will qualify the Bettis T416-SR3-13 Actuator with this test. The bas:s of this cross qualification lies in the sim larines of the two actuators. It can be demonstrated that the test actuator (T420-SR1-M3), by being larger in both si:e and weight, is a worse case condition when compared with the 741o-SR3-M3 actuator, thus qualifying them both. Both actuators are models in the Bettis T-4 series of spring-return actuators. The differance is in the overall size and torque capabilities. The two digit number Ecliowing the T-4 in the actuator model number represents the si:e of the piston uscd in the air stroke. The T416 has a 16" diameter piston and the T420 has a 20" diameter pistcn. The SR number refers to the size of the spring used in the return stroke. The SR1 in the T420 actuator is larger in size and weight than the SR3 in the T416 actuator. The M3 on the model number refers to the attached handwheel, which is identical on both. In summary, due to the differences noted above, the T420-SR1-M3 actuator is larger in. size (79-3/16" as c mpared to 74-1/16") and weight (805# as compared to 615d) when compared to the T416-SR3-M3 actuator. It is clearly a worse case condition when seismic loadings are considered and brackets of equal design are used.

. m } Lp r,a b Ch..-,a. O.,,.o; Ll g.. ;.;..,,,,.,. p ~ 2. C o m : :y.~ \\ D" u ~ 2.0 TEST AS5:NPT:ONS The ces: was conducted to qualify many si=ilar actuator / valve ccmhinaticns. There-fore, the test was not conducted for any one customer c: valve type. Sc=e assump-tions were made to brcaden :he scope c! the qualifica:icn. Those which a!!ect Ebasco will be explained in this section. The test in questicn was pe:fc:med without the total valve assembly. The bracket and actuator were mounted on a test fixture in place of an actual valve bcdy. Jusci-fication for this is based on Fisher Ccncr:1s' experience in past dynamic tests. In all tests completed, we have never found a case where binding in the shaf:, due to deflec: ions in the valve body or disc, has a!!ected the actuator's ability to s::cke the valve. When stroke time is measured, it rem.1 ins constant under seismic :cading. It is our opinion that the valve itself will not a!!ect the actuaccr's ability to function, there!cre, we conclude it reascnable to only verify tha: the torque cutput (,? c! the actuator will not vary unde: seismic icadings. ,y

ualificatica of accessories will depend on the particular custcmer's requirements.

In Ebasco's case, we are dealing with Namco limit suitches and Asco solenoid valves. The limit switches will be qualified by analysis.

t is our intent to mount all limit switches on the idle end of the valve body, oppcsite the actuator.

An analysis of the mounting bracket will be submitted showing tha t the resonant frequency of the switch bracket will exceed 33 Hertz, and the resulting stresses will be within Ebasco's specified limitations. As a supplement, Narco's qualification report 'ill be submitted for qualification. l, miu m is a

FISHER CONTROLS COMRiNT runi.v.m.u. n:visto." To qualify the Asco, an accelercmeter was located in the approximate mounting location of the solenoid valve to record the actual loadings it m uld see. Read out frce this accelerometer showed that the increased response due to the flexible constructicn did not exceed the g-levels to which Asco has previcusly qualified their equipment. Therefore, Asco's qualification is still valid, and we will submit that report for qualifica tion. a l i I I 1 . 7

FISilElf t'ONTitOLS COSIPANY Cos71NENTAL Div!wl0N 3.0 - SCOPE OF QUAL:FICATION 2his report applies to the folicwing item and tag numbers: l VALVE CONTINENTAL EBASCO EBASCO VALVE ITEM NO. ITEM NO. TAG NO. S::'E l TYPE AC"T]A TOR i 4D230-27 2HV-B15CB 4D230-28 2HV-3151A 4D230-29 2HV-1 '.52A Bettis 6 43" '220 . T420-SR1-M3 4 4D230-30 2HV-B2533 s 4D230-31 2HV-B1543 l 4D230-32 2HV-B155A 3HV-B2173 Bettis 7C627-DD 21 42', 9220 3HV-3218A

420-521-M3 l

3HV-3223B Bettis 7C627-FF 23 30" 9220 3HV-B224A 7416-SR3-M3 3HV-B226A Bettis 7C627-GG 24 36 9220 3HV-B2273 T420-SRl-M3

FISIIER t'ONTROLS ('f DIP.iN Y ('t INTINI[NT.\\ L DIV! wit aN 4.0 - TEST PROCEDi:RE 1.0 TEST SPECIMEN: 1.1 Specimen

Description:

A Bettis Type T420-5Rl-M3 Pnuematic, Spring-return Actuator, identical to the actuatc: supplied on Ebasco Item Nu~.he: 6, was used in testing. Speci-men is shcwn in Photograph fl. 1.2 Specimen Haunting: The specimen, mounced on a fabricated bracket (Ph ' acgraph d 3), was attached to a Fisher designed and fabricated =cencing fixture (Photograph t4) and the fixture, in turn, was fastened to a seis.~.ic simulator table. The fixture included a short piece of shafting, instru=ented with strain gauges, to verify the torque cutput of the actuator. The speci=en was oriented such that its longitudinal axis was colinear with the longitudinal axis of the test table. A The specimen was rotated 90 degrees in the horizontal plane, !c: the second axis of tests. 2.0 EXC::ATICH: 2.1 Sicultaneous Biaxial Excitation: Each horizontal axis was excited separately, each one simultaneously with the vertical axis. The horizontal and vertical inputs were tested in the in-phase condition.

FISIIER l'OHHOLS ('iDIP.iN Y l'mTINENT.M. DtV!sION 2.2 Resonant Search: A low level biaxial sine sweep, with a minimum input of.2 g's in each test axis was pe":ormed to establish resonances. The tests were perscrmed cver a frequency range of 1 H:. to 40 H. at a rate of one octave per minute. A rescnance is defined as a response order of magnitude greater than or equal to tuc. 2.3 Sine Bea: Yests: The specimen was subjected :o biaxial sine hea ces:s at the frequencies determined in the resonant search. The input acceleration was a mini =um of 1.0 g's hori:=ncal and.67 g's ver:ical, as specified in Ebasco's specifica-ticn. The specimen was operated throughout :he sine bea: :ests to ensure operability. A regulated air source with a minimum of 35 PSI, was supplied to the actuator to operate actua ct in one direction. The internal spring was used for the return stroke.

he sine heat test consisted of ten oscilla-tions per heat, five heats per test frequency with a two-second pause between beats.

3.0 INSTRLi.vENTA TICN 3.1 Excitation Control: A control accelerometer wac mounced cn the table near the base of the test fixture (Photograph 42). 3.2 Specimen 1.cceleration Response: Four (4) biaxial piezo-electric accelerometers were located cn the specimen during tes:ing. Placemen: of accelerometers is shown :n photograph al.

1 l 1 Firil!ER t'ONTI!OLS ('O.\\li'.i.N Y ( 'O NTI N13T.11.1)iVI*IO.N j 4.0 TEST RESULTS 4.1 Sine Sweep Test: Resonant !:equencies were iccated at 25 liz., 31 Hz., 3: H:,, 34 H:., 35 Hz., and 40 Hz. during thh sine sweep test. 4.2 Sine Sea: Tes t : The actuator operated successfully when subjected to sine beats at the fre-quencies determined above. The specimen suffered no physical damage. f i e se -}}

W3P81-1835, Forwards Containment Purge & Vent Valve Operability Study, Per TMI Item II.E.4.2.Mods Being Made to Limit Valve Opening to 40 Degrees.Study Demonstrates Compliance W/Item II.E.4.2,Part 5

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SUBJECT:

Dear Mr. Tedesco:

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