ML19331C672

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Evaluation of 42-Inch Containment Isolation Valves for Zion Station 1 & 2, Revision 1
ML19331C672
Person / Time
Site: Zion  File:ZionSolutions icon.png
Issue date: 07/28/1980
From: Deardorff A, Gerber D, Martin J
NUTECH ENGINEERS, INC.
To:
Shared Package
ML19331C671 List:
References
64.802.0010, COM-0709-01, COM-0709-01-R1, COM-709-1, COM-709-1-R1, NUDOCS 8008190333
Download: ML19331C672 (36)


Text

,

g-ID 01 NF0mVKTON ON _Y COM-0709-01 Controlled Copy No.

REVISION 1 i

64.802.0010 1

EVALUATION OF 42-INCH CONTAINMENT ISOLATION VALVES FOR ZION STATION, UNITS 1 & 2 l

0 Prepared for:

COMMONWEALTH EDISON COMPANY E

Prepared by:

NUTECH E

t 1

MdA6 asA s. Desda D. A. Gerber, P.E.

J[BIMa[ tin,P.E.

Project Engineer Project Manager j

7 l} /Y D

/

Date:

7/26/8C A.'F.DeaIdorff,P i

Engineering Mana lIl N

N

" " * " " "3

REVISION CONTROL SHEET

SUBJECT:

EVALUATION OF 42 INO1 CONTAINMENT REPORT NUMBER:

COM-0709-01 ISOLATION VALVES FOR ZION STATION, UNITS 1 6 2 D.A.

Gerber.P.E.. Senior Engineer M

NAME/ TITLE INITIAL b

T.

Lem, Analyst 7~< 4,

NAME/ TITLE INITIAL 1

A. Fife,P.E., Staff Engineer NAME/ TITLE INITIAL l

NAME/ TITLE INITIAL

)

NA.AE/ TITLE INITIAL PRE-ACCURACY CRITERIA hh'

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PRE-ACCURACY CRITERIA PAGE(S REV PARED OECK OIECK PAGE(S)

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ABSTRACT A stress analysis was performed by NUTECH to evaluate j

stress level margins in critical components of the 42-inch butterfly valves manufactured by the Henry Pratt Company and used as containment purge isolation valves at Zion Nuclear Power Station, Units 1 & 2.

The purpose of this evaluation was to determine the worst l

case stress level margins existing in the critical load-carrying structural members of the valve during a closing event under design basis Loss of Coolant Accident conditions.

I The evaluation consisted of an analysis of stresses in the l

valse shaft, pins, key and actuator arm.

This analysis was performed using, as the loading condition, valve shaft torque values calculated from values in the Henry Pratt Company report, Reference 1.

The results of the stress analysis indicate that the worst case stress level margins

)

in the valve load-carrying structural members are acceptable.

It is concluded from this analysis effort that the critical internal components of the Pratt 42-inch butterfly valve

]

will retain structural integrity if subjected to the flow induced loads resulting from a postulated design basis Loss of Cootant Accident when used as a containment purge isolation valve at Zion Station, Units 1 & 2.

COM-0709-01 11 nLitech j

T TABLE OF CONTENTS Page ABSTRACT 11 LIST OF TABLES iv LIST OF FIGURES iv

1.0 INTRODUCTION

1.1 2.0 COMPONENT DESCRIPTION 2.1 3.0 STRESS ANALYSIS DESIGN CRITERIA, LOADING CONDITIONS AND ANALYTICAL METHODS 3.1 3.1 DESIGN CRITERIA 3.1 h

3.2 LOADING CONDITIONS 3.1 3.3

/NALYTICAL METHODS

'3. 3 4.0 RESULTS 4.1

5.0 CONCLUSION

S 5.1

6.0 REFERENCES

6.1 APPENDIX A - NUTECH Stress Analysis of 42-Inch Butterfly F1 ho 64.8$2 0006 a

3

1 COM-0709-01 til nutech A

T LIST OF TABLES Table Title Page 3-1 HENRY PRATT COMPANY TORQUE VS. VALVE DISC ANGLE 3.7 RESULTS 4-1

SUMMARY

OF STRESS RESULTS 4.2 DI LIST OF FIGURES El rig m m ie Page 4

2-1 SRETce ez ee1TeR,Lx AL e 2.2 l

'3-1 CONTAINMENT PRESSURE VS. TIME 3.8 3-2 TORQUE VS. VALVE DISC ANGLE 3.9 l

3-3 AVAILABLE TORQUE IN SYSTEM 3.10 l

l l

COM-0709-01 iv l

Revision 1 nutech 03 1

g.

/3

1.0 INTRODUCTION

I In References 2, 3 and 4, the Nuclear Regulatory Commission requested Commonwealth Edison Company to respond to generic c(

concerns regarding containment purging during normal plant operation and provided guidelines for operability of 6

containment isolation valves used for purging.

These operability guidelines included:

l 1.

Demonstrating that the containment isolation valve I

actuators have sufficient tcrque capability to stroke the valves from full open to full closed within the technical specification time limit against design basis Loss of Coolant Accident containment pressure.

2.

Ensuring that the valve structural elements have sufficient stress margins to withstand the concomi-I 1

tant loads imposed while closing.

}

1 h

The. containment purge isolation valves at Zion Station, Units 1 & 2, are butterfly valves manufactured by the Henry 1

Based on the hydrodynamic torque results in Pratt Company.

Reference 1, it is apparent that these butterfly valves l

tend to close under the postulated flow conditions.

In order to address the second operability guideline, an analysis effort was conducted to evaluate the stress COM-0709-01 1.1 Revision 1 nutech g

3 margins inherent in the valves under the postulated flow conditions.

Analysis of the critical load-carrying components of the valve was performed utilizing as input the maximum torque values from the Reference 1 Henry Pratt Company report adjusted for postulated containment pressure.

The analysis was comprised of a simplified stress analysis considering bending, shaar and torsional shear loadings.

Stress margins were calculated for the

)

load bearing components utilizing standard stress allowables.

EI This report, prepared for Commonwealth Edison Company, presents the results of the stress analysis performed on

]

the Zion Station, Units 1 & 2, 42-inch containment isola-tion valves and provides verification of acceptable stress level margins in their critical internal structural components under a postulated design basis Loss of Coolant Accident.

The report summarizes the stress analysis design criteria, loading conditions, methods and results.

l APPENDIX A is the NUTECH stress and hydrodynamic torque analysis.

1 0

01 13 COM-0709-01 1.2 g

nutech L

3 2.0 COMPONENT DESCRIPTION The valves used at Zion Station, Units 1 & 2, for contain-cent purging are 42-inch offset asymmetric disc butterfly valves with external pneumatic / spring (air to open/ spring to close) valve actuators (shown on Figure 2-1).

These Pratt 42-inch valves are constructed with a carbon steel body, a 4-1/4 inch diameter type 3'04 stainless steel shaft 7

and sintered bronze bearings.

The valve is mounted in

]

horizontal runs of pipe with the shaft vertically oriented.

The actuators are aligned horizontally and are attached to the valve shaft through a lever arm which is 7

keyed to the shaft with a cold drawn steel key.

The valve mJ disc is attached to the valve shaft with two 1-1/2 inch tapered stainless steel pins.

')

Each plant uses two of these valves in series in the

~

containment purge line.

Of each pair, one valve is located inside containment and the other one is located outside containment.

They serve the function of containment j

isolation valves.

In the postulated event that these valves are open for purging and a design basis Loss of Coolant Accident occurs, these valves must be capable of closing within the technical specification time limits and h

provide containment integrity.

I l P COM-0709-01 2.1 nutech g

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AIR CYLINDER b

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SKETCil 0F BUTTERFLY VALVE FIGURE 2-1 j

D MllIOCb COM-0709-01 2.2 3

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T 3.0 STRESS ANALYSIS DESIGN CRITERION, LOADING CONDITION AND ANALYTICAL METHODS The stress analysis of the valve is presented in APPENDIX A.

The design criterion, loadings and analytical methods used are presented below.

3.1 Design Criteria The purpose of the analysis was to analytically determine that the stress levels in the valve load-I carrying structural members were within limits that l

would preclude yielding for those members as the valve is closed against a flow rate generated by a postulated design basis Loss of Coolant Accident.

This criterion would ensure that during closing, the active valve parts would not deform.

3.2 Loading condition The loading condition considered in the stress

]

analysis of the butterfly valve included hydrodynamic torque and valve actuator restraining force.

Dead weight and seismic forces were considered to be negligible.

]

Torque loading of the valve shaft was based on the torque values provided by the Henry Pratt Company in Reference 1, as reproduced in Table 3-1.

These COM-0709-01 3.1 nutech 3

I torque values were proportionally adjusted for containment pressure, as described in the.following paragraph.

The Reference 1 hydrodynamic torque values were calculated using a containment pressure of 42.7 psia, the maximum postulated containment pressure at the end of the valve closing stroke.

To be more realistic, the Zion Station containment pressure-time curve (Reference 5) was used to determine containment pressure versus valve disc angle during the val.ve stroke (The containment pressure-time characteristics are shown in Figure 3-1.). This method yields the relationship between hydrodynamic torque and valve disc angle represented on Figure 3-2.

Figure 3-2 was determined by scaling torque values from the Reference 1 values on the basis of containment pressure and Mach number as follows:

3 Torque = C py 9 (Reference 6)

T with CT = Torque coefficient p

= Density of air V

= Velocity of air at minimum area in valve COM-0709-01 3.2 kevision 1 l

a

I D

= Diameter of valve opening

]

4 Assuming, that air is a perfect gas gives:

Torque = C (M

)D3=C PM YD,

2 3

T T

)

Ratio of specific heats Y

=

P Containment pressure

=

Universal gas constant R

=

T Air temperature

=

M

_.. number Ratioing the Reference 1 torque values (subscript P) to the actual torque values (subscript a) yields:

3 2

(Torque)p (C

YD)p (pg )p T

3 2

U #9"*)a (C

YD),

(PM )a T

31nce CT, Y and D are constant for this comparison:

2 l

(PM )

l (Torque)a =

x (Torque)p 2

(PM )p l

For the maximum hydrodynamic torque case, at a valve

(

disc angle of 15 from full open, the postulated containment pressure is 28.8 psia, which yields a 1

l Mach number of 1.0 at the valve disc edge.

There-l fore, the maximum hydrodynamic torque is determined 1

]

as follows:

)

COM-0709-01 3.3

I Pp = 42.7 psia P

= 28.8 psia a

Hp =

1.0 H,= 1.0 (Torque)p = 166,710 inch-pounds (Reference 1) 2 28.8 x 1.0 ) (166,170) = 112,077 in pounds.

(Torque)a= ((42.7 x 1.0 )

2 (tending to close valve)

. Conservatism was introduced by analyzing the upstream valve for flow forces while assuming the downstream valve and piping were not connected.

7 Valve actuator force wg, conservatively calculated

]

based on the assumption that the valve actuator torque balanced the flow induced hydrodynamic torque generated in the valve at each valve disc angle.

The valve actuator is comprised of an air cylinder / spring 3

I combination.

The spring is attached to a piston inside the air cylinder and forces the valve closed l

when there is no air in the cylinder.

To open the valve, the cylinder is pressurized with air such that the air pressure on the piston overcomes the spring 1

force.

Upon a containment isolation signal, the air l]

in the cylinder is bled out through an orifice thus P.

permitting the spring to gradually close the valve.

If the flow induced hydrodynamic torque is positive C0H-0709-01 3.4 Rcrision 1 nutech g

l

7-4 this closing torque.

If the flow induced hydro-dynamic torque is negative (to open the valve), the effect is to compress the spring.

The lower curve in

]

Figure 3-3 represents the torque available from the spring force which can resist this opening torque.

Since the upper and lower curves envelope the calculated hydrodynamic torque, during a postulated 7

design basis Loss of Coolant Accident, the valve will

]

close at the normal operating rate governed by the initial air pressure, orifice size and spring constant.

3 3.3 Analytical Methods

]

The butterfly valve was analyzed to determine the stress level margins in the valve load-carrying active components during the postulated flow condition.

I The analysis consisted of determination of bending, torsion and shear loads on the valve shaft, key, pins and ectuator arm at the critical valve disc angle of 15 from full open.

Bending and torsional moments J

l and shear forces were calculated at the actuator arm attachment, upper and lower bearings and the pins.

a COM-0709-01 3.5 g

nutech I

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n-I The maximum shear stress due to combined bending, torsion and shear was then calculated and compared either to an allowable of 1/2 yield strength, or to a value developed from the maximum. distortion energy theory (Reference 7), to generate safety factor values.

T i

a D

B C

a d

u O

COM-0709-01 3.6 nutech J

l

I TABLE 3-1 HENRY PRATT COMPANY TORQUE VS. VALVE DISC ANGLE RESULTS VALVE DISC ANGLE DYNAMIC TORQUE (Degrees from full open)

(inch-pounds closing valve) 0 82,968 5

124,156

]

10 148,095 15 166,170 20 148,392 25

-134,665 30 125,752

]

35 111,806 40 98,875 45 81,055 50 62,171 44,218 55 60 28,230 65 16,611 i

70 11,147 75 5,638 q

LA 80 3,347 l]

85 1,181 l

90

- 42,025 d

nutech

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COM-0709-01 3.7 I

IT TABLE 3-1 HENRY PRATT COMPANY TORQUE VS. VALVE DISC ANGLE RESULTS VALVE DISC ~ ANGLE DYNAMIC TORQUE (Degrees from full open)

(inch-;iounds closing valve) 0 82,968 5

124,156 10 148,095 15 166,170 20 148,392 25 134,665 30 125,752 35 111,806 40 98,875 45 81,055 50 62,171 55 44,218 60 28,230 65 16,611 70 11,147 75 5,638 80 3,347 l

85 1,181 90 42,025 y

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IlYDR0 DYNAMIC TORQUE VS. VALVE DISC ANGLE FIGURE 3-2 l

COM-0709-01 39 l

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.RE STR AI N I N G TORQUE -

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200,000-8 x

100,000-(3 0

10 20 30 40 50 60 70 80 90 l

VALVE DISC ANGLE (DEGREES FROM FULL OPEN )

-100,000-TORQUE AVAILABLE TO '

CLOSE VALVE FROM SPRING l

(ZERO PRESSURE IN CYLINDER)

M,1 AVAILABLE TORQUE IN SYSTEM FIGURE 3-3 l'

COM-0709-01 3.10 nutech Revision 1 l

7 4.0 STRESS ANALYSIS RESULTS The stress and safety factor values from the stress analysis, Appendix A, are presented in Table 4-1.

The

)

critical location in the valve was determined to be the shaft at the upper valve disc-to-shaft pin, where the stress level was conservatively calculated to be 977. of the 7

allowable.

-4 7

7 7

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og 7

4 3

COM-0709-01 4.1 3

nutech t

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TABLE 4-1

SUMMARY

OF STRESS RESULTS 3

STRESS PERCENTAGE OF ALLOWABLE (ksi)

SHAFT:

]

SHEAR STRESS AT KEY 7.63 51%

SHEAR STRESS AT UPPER BEARING 12.47 83%

97%*

SHEAR STRESS AT PINS 16'.79 KEY:

SHEAR STRESS 9.37 62%

h COMPRESSIVE STRESS 14.99 50%

PINS:

SHEAR STRESS 7.13 48%

I ACTUATOR ARM:

l BENDING STRESS 5.25 18%

0

]

  • BASED ON MAXIMUM DISTORTION ENERGY THEORY SHEAR STRESS l

ALLOWABLE OF 17.31 KSI.

l COM-0709-01 4.2 nutech g

l 3-1

]

5.0 CONCLUSION

S The stress analysis of the Pratt 42-inch butterfly valve demonstrates that the loads and stresses imposed upon the active load-carrying components during a valve closure L

under a postulated design basis Loss of Coolant Accident

]

event are within acceptable limits.

The stress margins are sufficient to ensure no significant deformation of the rr active valve parts will occur when the valve is used as a containment isolation valve in the Zion Station, Units 1 and 2.

The loads used in the stress analysis were based f

upon results from the Henry Pratt Company.

]

]

7 7

lO A

tl ru O

I COM-0709-01 5.1 L*

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6.0 REFERENCES

P il 1.

J. E. Sirovatka (Henry Pratt Company) letter to Commonwealth Edison Company, " Commonwealth Edison, Zion Nuclear Plant, P. O. 241329, HPCo Ref. D-28504",

7 dated April 18, 1980.

a 2.

Nuclear Regulatory Commission letter from Mr. A.

.]*

Schwencer to Mr. Cordell Reed (Commonwealth Edison Company) " Containment Purging During Normal Plant Operation", dated November 29, 1978.

3.

Nuclear Regulatory Commission letter from Mr. Darrell G. Eisenhut to All Light Water Reactors, " Containment Purging and Venting During Normal Operation -

3lE Guidelines for Valve Operability" dated September 27, 1979.

4.

Nuclear Regulatory Commission letter from Mr. A.

]

Schwencer to Mr. D. Louis Peoples (Commonwealth Edison Company), " Containment Purging and Venting During Normal Operation", dated October 23, 1979.

]

5.

" Figure 14.3.4-6, Pressure-Temperature Curve, Zion Nuclear Power Station, Final Safety Analysis Report".

6 6.

T. Sarpkaya, " Torque and Cavitation Characteristics of Butterfly Valves," Journal of Applied Mechanics,

]

Transactions of the ASME, Number 60-WA-105, December 1961, pp. 511 - 518.

7.

Robert C. Juvinall, Engineering Considerations of Stress, Strain and Strength, McGraw-Hill Book Company, 19 Edition pp. 65-69.

D 3

Al N

y COM-0709-01 6.1 Revision 1 mi i

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3

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]

APPENDIX A

]

N' TECH Stress Analysi.s of 42-Inch Butterfly Valve

~3 m

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