ML17265A182
| ML17265A182 | |
| Person / Time | |
|---|---|
| Site: | Ginna  |
| Issue date: | 02/20/1998 |
| From: | ROCHESTER GAS & ELECTRIC CORP. |
| To: | |
| Shared Package | |
| ML17265A181 | List: |
| References | |
| EWR-5111, NUDOCS 9803120249 | |
| Download: ML17265A182 (73) | |
Text
Rochester Gas 8c Electric Corporation Ginna Station Motor-Operated Valve Qualification Program Plan Calculation Assumption Verification Criteria EWR 5111 ATTACHMENTK Revision 1
= Page1 9B03i20249 980303 PDR ADOCK 05000244 P
Table ofContents 1
il 6
7 Introduction.
Purpose Analysis ofValve Factors and Required Thrust Methodology Standard Industry Equation (Valve Factor Methodology)
EPRI Performance Prediction Methodology (EPRI PPM)..
Applicabilityto RG&E MOVQualification Program.
Acceptability ofGinna DP Tests..
Analysis ofGinna Valve Factor Test Data..
Analysis ofEPRI and Industry Data.
- Review ofEPRI MOVPerformance Prediction Program Test Results..
Review ofCommonwealth Edison Valve Factor Analysis.
Review ofTU Electric (Comanche Peak) Borg-Warner Valve Factor Test Data.
Evaluation ofGinna GL 89-10 Program Gate and Globe MOVs.
Anchor/Darling Double Disc Gate Valves.
Anchor Darling Flex Wedge Gate Valves....................................................
Aloyco Split Wedge Gate Valves.
Westinghouse Flex Wedge Gate Valves.
Crane Flex Wedge Gate Valves.
Crane Solid Wedge Gate Valves.
Velan Flex Wedge Gate Valves Borg-Warner Flex Wedge Gate Valves..
Valve Factor and Required Thrust Conclusions.
Analysis ofLoad Sensitive Behavior and Stem Coefficient ofFriction.
Load Sensitive Behavior.
Stem Coefficient ofFriction (li-Stem).
Application ofGinna LSB and Stem Coefficient ofFriction Test Results..
Evaluation ofLSB &li-Stem Test Data.
Load Sensitive Behavior Conclusions.
Stem Coefficient of Friction Conclusions.
Analysis ofPacking Load Packing Load Conclusions..
Attachments.
References..
Attachment K-1.
Attachment K-2 Attachment K-4.
Attachment K-S.
Attachment K-6.
Attachment K-7 Attachment K-8 Attachment K-9 3
3 3
,4
.4 5
.8
.11 13 13
.14 15
.16
.16
- 18
.18 19 20 21 22 23 24 25
.26 26 27 27 28
..30 32
.33
.34
.35
..36
.38
.40
.46
.48
.49
.50
.51
.54 MOVProgram Plan EWR 5111 Attachment K - Page 2 Revision 1 Date 2-20-9S
- 1. Introduction NRC Generic Letter 89-10, "Safety-Related Motor Operated Valve Testing and Surveillance" requires that the correct switch settings be established and maintained for all Safety-Related MOVs at each nuclear plant.
In establishing the correct switch settings, the NRC staff expects licensees to validate their assumptions for determining thrust and torque requirements. Validation ofassumptions should be based on the best available MOVtest data. The NRC considers the best available MOVtest data (in order ofreliability)to be:
Valve-specific data Plant-specific data EPRI test data Industiy test data The NRC has also recommended that each MOVbe demonstrated to be operable by testing itat the design basis conditions ifpracticable. Where it is not practicable to test a MOVunder sufficient dynamic conditions to demonstrate design-basis capability, engineering or statistical methods to determine appropriate assumptions for such parameters as valve and stem friction, and load sensitive behavior from other MOVs, where justified, could be used.
The importance ofadequately justifying the methods to demonstrate MOVoperability was reiterated in NRC Information Notice 97-07, "Problems Identified During Generic Letter 89-10 Closeout Inspections".
2.
Purpose The purpose ofthis document is to determine and justify interim and long term valve factors used to calculate the minimum required thrust to open and close each Ginna Station Generic Letter (GL) 89-10 Motor-Operated Gate and Globe Valve under design basis conditions. In addition, bounding values to account for Load Sensitive Behavior (Rate OfLoading) Effect and Stem Coefficient of Friction are determined and justified in this attachment.
This document willalso discuss methods for evaluating measured packing load data.
3.
Analysis ofValve Factors and Required Thrust Methodology Per reference 1, the forces that the actuator must over come to open or close a gate or unbalanced disc globe valve under design basis conditions are:
DP Thrust - this force due to the effect ofdifferential pressure across the valve. It includes direct fluid forces acting on the disc, and friction forces developed in the valve internals.
Piston Effect Thrust - the force due to internal line pressure acting on the valve stem. This force opposes stem movement in the close direction and assists stem move'ment in the open direction.
Packing Friction - the force needed to slide the stem through the packing.
Deadweight - weight ofthe valve stem and disc (typically negligible).
Torque Arm Friction - the torque in the stem is reacted in the valve by surfaces which engage and slide. This torque reaction causes a friction load which opposes stem motion.
A MOVProgram Plan EWR 5111 Attachment K-Page 3 Revision 1 Date 2-20-98
With the exception ofthe DP Thrust, these forces can be conservatively predicted with a high degree of confidence.
Unfortunately, the DP thrust is typically the dominant contributor to the required thrust. In addition to the design basis DP, valve internal geometry and friction between the internal components significantly affect the DP thrust.
In order to accurately determine the DP thrust component a MOVtest under DP conditions with highly accurate measuring equipment has to be performed.
Due to operating and safety constraints, it is not practical to test all Safety-Related MOVs under DP conditions. Therefore, an analytical method is used to conservatively predict the force due to DP.
For consistency and to encompass the possibility ofdegradation in valve performance due to aging, the analytical method is used for all 89-10 MOVs. There are two generally accepted analytical methods to calculate required thrust, the "standard industry equation", and the EPRI Performance Prediction Methodology (EPRI PPM).
Standard Industry Equation (Valve Factor Methodology)
Historically, the required thrust to open or close a Motor-Operated Gate or Globe Valve was calculated by use ofthe "standard industry equation" and a valve factor as shown below.
Required Thrust = DP Thrust+ Piston Effect Thrust+ Packing Friction where DP Thrust = (Valve Factor)(Differential Pressure)(Orifice Area)
Since the contributions ofthe deadweight and torque arm friction are typically small in comparison to the other forces, these are neglected in the "standard industry equation." As stated previously, the DP Thrust is significantly affected by variables such as valve internal geometry and friction between the internal components. In the "standard industry equation", the valve factor is used to account for variations in friction and internal tolerances.
Some ofthe advantages ofusing the "standard industry equation" to calculate required thrust are:
~
ease ofuse
~
familiarity
~
small number ofdesign inputs which are readily available Some ofthe disadvantages ofusing the "standard industry equation" to calculate required thrust are:
~
Valve factors have been found to vary significantly from valve to valve.
~
It is difficultto ensure a conservative valve factor is selected without an adequate amount oftest data.
~
The effect ofage related degradation on the valve factor is not widely known at this time.
EPRI Performance Prediction Methodology (EPRI PPM)
More recently, the Electric Power Research Institute (EPRI) has developed improved methods for predicting the performance ofgate and globe valves under dynamic conditions. EPRI performed numerous valve tests to provide data for model development and validation. EPRI integrated the individual models and methods into an overall methodology including a computer model for most gate and globe valves and hand calculation models for certain gate valves.
The NRC staff issued a Safety Evaluation approving the EPRI PPM for predicting the thrust requirements with respect to the EPRI computer and hand-calculation models for gate and globe valves provided they are developed in accordance with the conditions and limitations contained in the NRC Safety Evaluation.
MOVProgram Plan EWR 5111 Attachment K-Page 4 Revision 1 Date 2-20-98
Some ofthe advantages ofusing the EPRI PPM to calculate required thrust are:
~
Determines a bounding value ofrequired thrust.
~
Considers the effect offlowand internal valve configuration.
~
Bounding prediction encompasses future degradation.
Some ofthe disadvantages ofusing the EPRI PPM to calculate required thrust are:
~
Requires a large number ofdesign inputs which are typically not readily available.
~
The required thrust prediction often seems excessively conservative for low temperature pumped flowvalves when compared to plant test data.
.~
The user must be trained in use ofEPRI computer sofbvare and consider limitations in the NRC SER.
Applicabilityto RG&E MOVQualification Program The purpose ofthe RG&E MOVQualification Program is to ensure the reliable operation ofMOVs in safety-related systems at Ginna Station. Therefore, it is essential that the methodology used to calculate required thrust provide a high level ofconfidence that safety-related MOVs willperform their intended functions.
Due to its ease of use and familiarity, the standard industry equation remains the preferred method to determine required thrust for GL 89-10 gate and globe MOVs. However, ifthe available Ginna test data is not sufficient to provide a high level ofconfidence that the valve factor for any particular valve is conservative, additional dynamic test data should be obtained at the earliest practicable opportunity (i.e.
Refueling Outage, work window, etc.). Ifdynamic testing can not be performed or is not desirable, efforts should be initiated to obtain valve factor data from similar valves under similar operating conditions, or procure the PPM design inputs and perform the PPM calculation at the earliest practicable opportunity.
Whether or not a valve,factor can be considered sufficient for "long term" use willbe determined based on the'following criteria:
The valve factor is based on satisfactory Ginna dynamic testing ofthe subject valve and includes a provision for future degradation.
The valve factor for a non-dynamic tested valve is based on satisfactory Ginna dynamic testing ofat least 2 or 30% ofthe total number ofidentical valves with similar operating conditions and includes a provision for future degradation.
The design basis DP in the safety direction is 0 psid or negligible, in which case the differential pressure thrust is 0 and the value ofthe applied valve factor is moot.
The process to determine acceptable long term and interim valve factors is shown in figure 1. Ifone ofthe above conditions is not met, only an interim valve factor may be assigned, and additional action (further testing or the EPRI PPM) willbe required. It should be noted that the design basis system conditions must be similar (i.e. system fluid, flowrate, DP's) in order apply the results ofGinna dynamic test data of identical valves to non-dynamic tested valves.
In addition, close valve factors are determined based on achieving flow isolation in certain cases and hardseating in other cases as appropriate based on the leakage requirements for the subject valve.
Margin for future degradation is incorporated in selected long term valve factors that are based on Ginna test data by rounding the maximum adjusted valve factor to the next highest 0.05 value (as a minimum).
This method ofaccounting for valve factor degradation willbe confirmed or refined when results ofthe Joint Owner's Group (JOG) Program on MOVPeriodic Verification methodology become available.
For MOVProgram Plan EWR 5111 Attachment K - Page 5 Revision 1
Date 2-20-9S
the purposes ofMOVoperability assessments, itis considered acceptable to use the as-tested valvefactor for a MOVwhich has been DP tested, provided the effect ofmeasurement uncertainties on the as-tested valvefactor are accounted for.
Since a significant amount oftime is required to implement the dynamic testing, data evaluations, or EPRI PPM calculations, an interim position is needed.
For the near term, MOVdesign basis willbe based on the "standard industry equation" and conservative valve factors based on an analysis ofGinna, EPRI and industry test results on identical and similar valves. Valve similarity is based on a comparison of manufacturer, seating surface materials, operating conditions, pressure class, and valve size. Slight variations in size, pressure class, and operating conditions were considered to be acceptable when applying the test results ofsimilar valves tojustify interim valve factors.
It should be noted that less conservative valve factor values and other means are available to demonstrate short-term operability ofMOVs in this category.
The interim valve factors are considered to be conservative, and it is expected that additional dynamic testing or PPM calculations willdemonstrate this.
Hence, the interim values could become the long term values when sufficient test data is obtained to further
'ustify the values.
MOVProgram Plan EWR 5111 Attachment K - Page 6 Revision 1
Date 2-20-98
Vam has Acceptable Dynamic Test?
YES ave Identical Valves been Dynamic Tested at Ginna?
YES Select VF based on max observed group VF rounded up to add margin for degradation.
NO Valve can be Grouped using Identical Ginna Va~?
YES Select VF based on max. observed rounded up to add margin for degradation.
Use As-Tested VF, rounded up to add margin for degradation.
EPRI PPM Calculation EDP is 0 psid or negligable in the safety direction?
YES'F is moot. No DP Thrust.
Acceptable for Long Term Use Vam n be Grouped wi
'Similar Ginna Valves with Dynamic Test Data YES Use data from similar Ginna valves as interimbasis for VF.
Use Ginna, EPRI & Industry Data analysis for Interim VF.
Schedule and Implement further Action (PPM or DP Testing ).
NOTES')
In noinstance willa Valve Factor less than 0.30 be usedin Thrust Catculatrons.
- 2) The maximum as-tested valve facors willbe rounded up to provide margin for degradation.
Figure 1: Process to Determine Long Term and Interim Valve Factors MOVProgram Plan EWR 5111 Attachment K - Page 7 Revision 1
Date 2-20-98
1 8
F
Acceptability ofGinna DP Tests The available dynamic test data traces were reviewed in reference 24 to determine ifadequate DP thrust was measured to accurately determine a valve factor. Based on the review in reference 24 and Attachment K-2, acceptable test data for calculating valve factors was available on 15 gate valves and 3 globe valves.
In addition, reference 4 provides guidelines for evaluating the acceptability'of in-situ DP tests.
Figures 8-1 through 8-5 provides a minimum acceptable DP based on the valve pressure class, test DP, and mean seat area. In addition, the test DP should be greater than 33% ofthe design basis DP. The minimum acceptable test graphs (from reference 4) with the Ginna DP test data are shown in Figures 4-7 below.
Minimum Test DP for 150¹ Valves 120 100 O
ol 80 I-E E
60 ER 40 P&CU~
4~481 20 0
50 100 150 200 250 300 350 400 Mean Seat Area (sq. In.)
~EPRI LINE g TEST MOVs Figure 2: 150¹ Class Valve DP Tests MOVProgram Plan EWR 5111 Attachment K - Page 8 Revision 1
Date 2-20-98
o 200 150 100 50 Minimum Test DP for 300¹ Valves
~ Qim/
g QSFlg 0
50 100 150 200 250 300 350 400 Mean Seat Area (sq. in,)
EPRI LINE g TEST MOVs Figure 3: 3004 Class Valve DP Tests Minimum Test DP for 600¹ Valves 1000 900 800 o
700 g
600 500 E
E 400
'c 300 200 100 0
0 50 100 150 200 250 300 350 400 Mean Seat Area (sq. in.)
~EPRI LINE g TEST MOVs Figure 4: 6000 Class Valve DP Tests MOVProgram Plan EWR 5111 Attachment K-Page 9 Revision 1
Date 2-20-98
Minimum Test DP for 1500¹ Valves 1400 1200 D
1000 E
800 E
600 Cg 400 QTQQ
~871 744AIB 20 40 60 Mean Seat Area (sq. In.)
80
~EPRI LINE g TEST MOVs Figure 5: 1500¹ Class Valve DP Tests From figures 4 through 7, the DP tests of 4663, and 9629A did not meet the EPRI minimum acceptable test DP. Valve 4663 was tested at 56 psid (59% ofthe design basis DP). The minimum EPRI test pressure for 150¹ class valves'is 60 psid, which is a mere 4 psi more than the test pressure for 4663.
Since the design basis DP for 4663 is only 95 psid and the test was performed by use ofa system alignment similar to the design basis condition, the 56 psid DP test is considered to be acceptable for use on 4663. However, the results willnot be used to assess the performance ofother valves.
Valve 9629A was tested at 87% ofthe design basis DP, however, the EPRI acceptance criteria was not met.
A review offigure 5 indicates that the design basis condition of95 psid is also below the minimum EPRI criteria. Therefore, the test results for this valve are considered to be acceptable, since it reasonably approximated the design basis condition.
Allother Ginna DP tests deemed acceptable in reference 24 were performed at greater than 33% ofthe design basis DP and met the minimum EPRI test DP criteria.
MOVProgram Plan EWR 5111 Attachment K-Page 10 Revision 1
Date 2-20-98
Analysis ofGinna Valve Factor Test Data Reliable DP test thrust data for calculating valve factors was available on 15 gate MOVs (two ofwhich were a DD gate). With the exception ofMOVs 3504A/3505A, all tests were performed with low temperature water in the system.
DP test data was also available for the Fisher, balanced disc globe valves (9701A/B) and Rockwell Stop Check Valves (3976/3977).
Table 1 and Figure 2 summarize the available Ginna open and close valve factor test data for gate valves. The mean and mean+ 2 sample standard deviations (mean+
2 sigma) values we'e calculated for the available Ginna gate valve factor data. The results ofthe analysis and the distribution ofthe Ginna Valve Factor data is shown in figure 3.
MOV Valve Manufacturer Valve Pressure Class, Size &Type Open Valve Close Valve Factor Factor 857A Anchor/Darling 300¹, 6x4x6" DD Gate 0.34 0.44 857B Anchor/Darling 300¹, 6x4x6" DD Gate 0.39*
0.39*
814 Crane 150¹, 6" FW Gate N/A 0.84 4663 Crane 150¹, 6" FW Gate N/A 0.41 4615 Crane 150¹, 20" FW Gate 0.45 0,52 4616 Raimondi 150¹, 20" FW Gate 0.33 0.39 4664 738A 738B 871A 871B Crane Crane Crane Velan Velan 150¹, 10" SW Gate 150¹, 10" SW Gate 150¹, 10" SW Gate 1500¹, 3" FW Gate 1500¹, 3" FW Gate N/A 0.28 0.35 0.22 0.46 0.64 0.26 0.23 0.29 0.28 9746 Westinghouse 2035¹ 3" FW Gate 0.38 N/A 3504A 3505A Anchor/Darling Anchor/Darling 600¹, 6" FW Gate 600¹, 6" FW Gate 0.29*
0.41 0.23*
N/A 9629A Borg-Warner 300¹, 4" FW Gate 0.30*
0.27*
Valve Factor values are from Attachment K-l,with the exception ofthose with an asterisk (*).
Values with an asterisk (*)are from Ginna DP test evaluation Data Sheet for the subject MOV. Allthrust values were obtained from the same data trace, and these values have not been adjusted for measurement error.
Table 1: Ginna Gate Valve Factor Test Data MOVProgram Plan EWR 5111 Attachment K-Page 11 Revision 1 Date 2-20-98
0.90 0.80 o
070 u.
0.60 0.50 OAO 0.30 R 0 Q
0.20 0.10 1
2 3
4 5
6 7
8 9
10 11 Valve Type Open VF Mean Valve Type Key
~
Close VF Mean+ 2 sigma 300¹, 6"x4"x6"A/D DDG 2035¹, 3" West. FWG 150¹, 6" Crane FWG (AllSteliite) 150¹, 6" Crane-Chapman FWG
~ 150¹, 20" Crane FWG 150¹, 20" Raimondi FWG 7
8 9
10 11 150¹, 10" Crane SWG 15ll, 10" Crane SWG 15M¹, 3" Ye!an FWG 300¹, 4" Borg-Warner FWG 600¹, 6" A/D FWG Figure 6: Ginna Valve Factor Test Data for AllGate Valves (Various Manufacturers) 10 8
C'o 7
o 6
o 5
a.
4 K
2 ean = 0.
Mean + 2 sigma Value = 0.651 Data from 15 Gate Valves IA c5V CS Cal co Ci C5 Valve Factor Range ED C5A Figure 7: Distribution ofGinna Gate Valve Factor Test Data (AllData Points)
MOVProgram Plan EWR 5111 Attachment K - Page 12 Revision 1 Date 2-20-98
Based on the available test data, the mean valve factor for a Ginna Gate valve was 0.380, and the Overall Mean+ 2 sigma valve factor was 0.651. Figure 3 and the statistical values are provided for comparison to figure E-25 in reference 5 only. The maximum observed valve factor was 0.84 for 814 in the close direction.
Analysis ofEPRI and Industry Data Review ofEPRI MOVPerformance Prediction Program Test Results Some ofthe more important findings identified during the EPRI MOVPerformance Prediction Program were (summarized from reference 5):
EPRI Gate Valve Findin s:
~
In ambient water, apparent disc friction coefficients (similar to valve factor) increase with stroking under DP conditions until a plateau was reached.
The amount of rise and the number of strokes required to achieve stabilization vary considerably from valve to valve. Initial disc friction coefficients ranged from 0.1 to 0.3 and stabilized friction coefficients ranged from 0.1 to 0.6.
The number of strokes required until stabilization was achieved ranged from less than 50 to 900. The largest variation in stabilized friction coefficient occurred with small (less than 6"), low pressure class (150/f and 300/f class) valves.
~
For pumped flowconditions, apparent disc friction coefficients decrease as temperature increases.
~
Apparent disc friction coefficients decrease as differential pressure increases.
~
For pumped flow conditions, deformations of cantilevered guide rails can occur at high flows (greater than 30 fps).
~
The required opening thrust for a gate valve can be increased by the Bernoulli effect, which is due to reduced pressure under the disc near the closed position when the fluid velocity is relatively high.
~
Under cold water pumped flow conditions, the apparent disc friction coefficients to fullyopen or reach initial wedging during closing range from 0.1 to 0.7 with the following exceptions for valve types in use at Ginna:
Mechanisms associated with the internal disc wedge for Anchor/Darling double disc valves can result in apparent disc friction coefficients greater than 0.7 for opening and greater than 0.9 for closing at low DP. The highest apparent open valve factor for a double disc gate valve was 0.80 and the highest close value at hard seat was >1.05 and 0.50 at flow isolation (from reference 6).
For Borg-Warner valves, parasitic thrust effects can result in apparent disc friction coefficients between 0.7 and 0.9 at low DP.
The maximum EPRI apparent disc frictioncoefficient of0.70 exceeded the bounding stellite 6 to stellite 6 coefficient offriction for flat on flat contact of 0.61 in reference 4. This was due to disc orientations other than flat against the seat.
Possible orientations include tipped on the guides, tipped on the guides and downstream seat, tipped on the guides and upstream seat, and tipped on both seats. Ifone ofthese other orientations were encountered during the test, the apparent disc friction coefficient could be greater than 0.61 based on the contact load and edge sharpness.
The EPRI PPM hand calculation methodologies for Anchor/Darling Double disc and Aloyco Split Wedge Gate Valves were developed and validated based on the test results ofonly one" valve ofeach type in the fiow loop test program.
MOV Program Plan EWR 5111 Attachment K - Page 13 Revision 1
Oate 2-2O-98
L!
1
.~.ti r ~ ="
EPRI Globe Valve Findin s:
Depending upon the details of the valve design, the load from the DP across the valve applies either to the seat area or the guide area. Ifa valve factor based on the seat area is used for a valve in which the guide area is the key area, the thrust required can be significantly underestimated (i.e. by as much as a factor oftwo).
~
Ifthe appropriate area (seat or guide) is used in determination of valve factors, valve factors for incompressible floware in the range from 0.9 to 1.1.
~
For hot water blowdown with two-phase, flashing flowthrough the valve, side loading on the globe plug can result in increased thrust requirements; the corresponding guide-based valve factor can exceed 1.4.
Review ofCommonwealth Edison Valve Factor Analysis A review ofthe Valve Factor "White Papers" prepared by Commonwealth Edison (references 11 through
- 14) was also performed. The ComEd analysis included data from both the EPRI test program and in-situ data from ComEd, and other utilities. The analysis excluded MOVs with low DP loads (< 4000 Lbs) on the basis of large measurement uncertainty. The primary grouping criteria used by ComEd was that valves from the same manufacturer with the same disc design can be analyzed together.
The analysis ofdata to the grouping criteria did not consider effects such as valve orientation, service condition, and material condition. The ComEd Analysis also concluded that the valve factor decreased as valve size increased.
The
- ComEd "nominal" valve factor was based on a best-flt straight line ofthe test data. The ComEd "bounding" valve factor line was based a two sigma confidence bound on individual valve factors for all valves within the group. In addition, ComEd determined a "conservative group" valve factor line which excluded the valve to valve variability due to unusually low values.
For valves at ComEd which were not DP tested, a valve factor approximately 0.10 greater than the nominal valve factor was used in MOVthrust calculations.
ComEd uses a bias and random method to calculate MOVthrust requirements, and the use ofthis method equates approximately to adjusting the nominal valve factor values by 0.10 in the standard equation.
The results ofthe ComEd analysis for valve types in the Ginna GL 89-10 MOVProgram are summarized below:
. Anchor/Darlin Double Disc Gate Valves reference 11 The nominal "wedge bottoming" (flow isolation) valve factors for Anchor/Darling Double Disc Gate Valves in cold water applications ranged from 0.48 for 3" valves to 0.35 for 12" valves. The conservative group "wedge bottoming" (flow isolation) valve factors in cold water applications ranged from 0.72 for 3" valves to 0.59 for 12" valves.
The ComEd analysis determined that the hard seat valve factor could be as much as 1.6 times greater than the flow isolation valve factor ifthe valve is installed with the upper wedge on the high pressure side (preferred orientation) and 2.05 times greater ifthe valve is installed with the upper wedge on the low pressure side.
A nominal "wedge bottoming" valve factor for high temperature applications was 0.35 and the bounding valve factor was 0.45. For hard seating (which ComEd referred to as disc spreading) with the upper wedge upstream, the nominal valve factor for high temperature applications was 0.45 and the bounding valve factor was 0.55. For hard seating with the upper wedge downstream, the nominal valve factor for high temperature applications was 0.60 and the bounding valve factor was 0.70.
MOVProgram Plan EWR 5111 Attachment K-Page 14 Revision 1
Date 2-20-98
Crane Wed e Gate Valves reference 12 For 150¹ and 300¹ class Crane Flex Wedge Gate Valves in cold water applications the nominal valve factors ranged from 0.75 for 3" valves to 0.38 for 20" valves. The conservative group valve factors ranged from 0.96 for 3" valves to 0.60 for 20" valves.
Bor -Warner 300¹ class Flex-Wed e Gate Valves reference 13
~
ComEd test data was not available, therefore, data from EPRI and the Perry Station was reviewed.
The nominal valve factors ranged from 0.42 for 3" valves to 0.46 for 20" valves. Due to an insufficient amount ofdata, the bounding ComEd valve factor was 0.65 based on the maximum EPRI disc to seat coefficient offrictionof0.61 adjusted for a 5 wedge angle. This method was not considered acceptable for use at Ginna.
Velan 1500¹ Flex Wed e Gate Valves reference 14 For 1500¹ class Velan Flex Wedge Gate Valves, the nominal valve factor was 0.595 and the bounding valve factor was 1.067. It should be noted that a sufficient number ofdata points were not available to generate regression curves for the high pressure Velan valves.
Review ofTU Electric (Comanche Peak) Borg-Warner Valve Factor Test Data Valve factor data from Comanche Peak in reference 15 was also reviewed. Comanche Peak tested 3 groups (total of 16 valves) of4" Borg-Warner Flex Wedge Gate valves under DP ranging from 95 to 2878 psid. The valves were 150¹, 900¹, and 1500¹ pressure class. The maximum statistical valve factor for any 4" Borg-Warner Flex Wedge Gate valve group (based on mean+ 2 sigma) was 0.64 and the highest observed valve factor was 0.62.
MOVProgram Plan EWR 5111 Attachment K-Page 15 Revision 1
Date 2-20-98
',pi 1
e a
r
Evaluation ofGinna GL 89-10 Program Gate and Globe MOVs In accordance with the methodology in Figure 1, identical gate and globe valves in the Ginna GL 89-10 program with similar design basis system conditions were grouped together to ensure that a bounding valve factor for a given valve type was selected.
The final values are shown in Attachment K-6. A discussion of each ofthese valve types is given in the following sections ofthis report.
Anchor/Darling Double Disc Gate Valves 6"x 4"x 6" 3000 Class Anchor/Darling Double Disc Gate Valves (Group AD1)
There are seven valves ofthis type (shown on drawing 11497) in the GL 89-10 program.
The wedges, and seating surfaces are all hardfaced with Stellite. Per reference 16, valves 857A/B/C are not required to be leak tight, and flow isolation was the functional requirement in the close direction. Valves 860A/B/C/D have a defined leakage criteria, and hard seating was the functional requirement in the close direction.
Per EWR-5080 R/8, the 857A/B/C valves are required to open against 225 and 251 psid. The 860A/B/C/D MOVs are required to open against 283 psid and close against 98 psid.The design basis flow rates for these MOVs was <15 fps.
Six ofthe valves were DP tested in the open direction, two ofwhich (857A/B) had measured DP thrust values high enough to accurately calculate valve factors. Four ofthe valves were DP tested in the close direction, two ofwhich (857A/B) could be used to calculate valve factors.
Therefore, sufficient Ginna test data was not available to formulate a long term valve factor basis for all ofthe MOVs.
Based on the maximum observed valve factor for 857A&B, a conservative value of0.50 should be used as the long-term valve factor for 857A&B.
The low DP load during the close DP tests of 860A&Dwas most likelythe result of low flowthrough the
'/i"containment spray test return line. The opening tests for these MOVs was performed with approximately 220 psid across the disc when the valves were closed. This DP should have been sufficient to produce a DP load similar to the design basis opening DP of283 psid, regardless ofthe flowrate. The shape ofthe open DP thrust traces for these MOVs indicates that the valves were effected by DP and line pressure, but the magnitude ofthe DP load was not much greater than the static opening loads. In fact the response to opening against DP for 860A and D was nearly identical as shown in Attachment K-2. Since the opening DP thrust for 860A/D were very low, and the test should have produced a DP load similar to the design basis, the use ofa 0.50 interim valve factor based on the maximum observed valve factor for 857A&B is considered to be acceptable.
In order to furtherjustify the 0.50 value, MOVs 857C, and 860A-D should be DP tested at the next practicable opportunity. Due to restraints ofthe containment spray system, only the open DP test of860A-D is expected to produce a measurable DP effect.
10"x 8"x10" 300ff Class Anchor/Darling Double Disc Gate Valves (Group AD2)
There are two valves (704A/B) ofthis type (shown on drawing 11500) in the GL 89-10 program. The wedges, and seating surfaces are all hardfaced with Stellite. Per reference 16, none ofthe valves are required to be leak tight, and flow isolation was the functional requirement in the close direction.
The required closing MEDP for these MOVs was only 33 psi at low flow rates (50 gpm and <15 fps).
Ginna station DP test data was not available on identical valves. The smaller A/D DD Gate valves tested at Ginna yielded a maximum valve factor of0.46. The size differential between these valves and the 6"x 4"x6" MOVProgram Plan EWR 5111 Attachment K - Page 16 Revision 1
Date 2-20-98
e
valves was too great to consider the valves to be similar. Therefore, an EPRI PPM calculation should be performed to determine the required thrust for these MOVs.
10" 3000 Class Anchor/Darling Double Disc Gate Valves (Group AD3)
There are three valves. ofthis type (shown on drawing 11502) in the GL 89-10 program. The wedges, and seating surfaces are all hardfaced with Stellite. Per reference 16, none ofthe valves (850A/B, and 856) are not required to be leak tight, and flow isolation was the functional requirement in the close direction.
Per EWR-5080 R/8, the 850A/B valves are required to close against-30 psid and open against 225 psid.
The 856 MOV is only required to close against - 6 psid, which is considered to be negligible. The design basis flow rates for these MOVs were 50 gpm and <15 fps.
Valve 850B was DP tested against 42 psi in both directions, and no significant DP effects were evident in the data. The design basis close DP condition was not considered to be much more severe than static conditions. The size differential between these valves and the 6"x4"x6"valves was too great for the valves to be thought ofas similar.
Since the 850A/B MOVs have to open against a significant DP, an EPRI PPM calculation should be performed to determine the required thrust for these MOVs.
The closing DP under design basis conditions was negligible for 856 and there is no safety-related function to open. Therefore, a valve factor is not needed to calculate the required thrust for the valve to perform its safety related function.
10"x 8"x10" 15000 class, Anchor Darling Double Disc Gate Valves (Group AD4)
There are two valves ofthis type (shown on drawing 11663) in the GL 89-10 program.
The wedges, and seating surfaces are all hardfaced with Stellite.
Per reference 16, none ofthe valves in this group (841 and 865) are required to be leak tight, and flow isolation was the functional requirement in the close direction.
Ginna station DP test data was not available to form a basis for the valve factor. These valves are the SI Accumulator Tank Shutoff Valves. Per EWR-5080 R/8, the MOVs are normally open with the power removed during plant operation and are required to close for recovery from a SGTR. Under this scenario, the required closing DP is negligible with a line pressure of700 psi. The DP for opening and closing these MOVs was conservatively selected as 33 psi based on the minimum threshold value in EWR-5080 R/8.
Since the closing DP under design basis conditions was negligible and their is no safety-related function to open these valves, the opening and closing valve factor are not considered to be ofcritical importance.
Therefore, a valve factor is not needed to calculate the required thrust for the valve to perform their safety related function, and any reasonable value is acceptable for use in thrust calculations.
3" 15130 class, Anchor Darling Double Disc Gate Valves (Group AD5)
There are two valves ofthis type (shown on drawing W-882777) in the GL 89-10 program.
They are the PORV Block Valves and are subjected to high temperature, steam service.
The seating surfaces are hardfaced with Stellite, and the wedge contact surfaces are stainless steel without hardfacing. Ginna station DP test data was not available to form a basis for the valve factor.
The valves in this group (515 and 516) have a leakage limitof 10 gpm. Per reference 26, this can be achieved at flow isolation. The difference in pressure class and operating conditions between these valves and the 6"x4"x6"valves was too great for the valves to be similar. A preliminary EPRI PPM calculation
., MOVProgram Plan EWR 5111 Attachment K - Page 17 Revision 1 Date 2-20-98
has been performed for these MOVs. Since these valves can not be DP tested, this EPRI PPM calculation should be reviewed, approved, and used as the long term required thrust methodology for these MOVs.
Anchor Darling Flex Wedge Gate Valves 6" 6000 Anchor Darling Flex Wedge Gate Valves (Group AD6)
There are two valves (3504A and 3505A) ofthis type (shown on drawing W-7820110B) in the GL 89-10 program.
They are the Steam Admission to the SDAFWP Valves and are subjected to high temperature, steam service. The seating surfaces are hardfaced with Stellite. Per reference 16, none ofthe valves in this group are required to be leak tight, and flow isolation was the functional requirement in the close direction.
Both ofthe valves were DP tested in both directions. With the exception ofthe close stroke for 3505A, the test data could be used to calculate valve factor. Therefore, sufficient Ginna test data was available to formulate a valve factor basis that is acceptable for long term use. It is recommended that a close DP test be performed on 3505A to verify the adequacy ofthe value selected in Attachment K-6.
Aloyco Split Wedge Gate Valves 3" 1500 class, Aloyco Split Wedge Gate Valves (Group A1)
There is one valve (313) ofthis type (shown on drawing E-45216) in the GL 89-10 program.
The seating surfaces are hard faced with stellite.
Per reference 16, valve 313 has a defined leakage limit, and therefore, hard seating was the functional requirement in the close direction.
MOV313 was DP tested again'st 62% ofthe MEDP (93 psid) in the close direction, and no significant DP effects were evident in the data. The adjusted close valve factor was 0.14. However, per reference 24, the measured DP load was too low to calculate a reliable valve factor. The MEDP for opening these MOVs is 33 psi based on the minimum threshold value in EWR-5080 1V8. A review ofEWR-5080 R/8 indicated that the MOV is normally open and is not required to stroke to the open position during a design basis event.
Hence, there is no design basis safety function to open, and'the opening valve factor was not considered to be ofcritical importance.
The valve is required to close against an MEDP of 150 psid.
A preliminary EPRI PPM calculation has been performed for this MOV. It is important to note that the hand calculation model for Aloyco Split Wedge Gate Valves was validated based on testing ofa single 4"150 Lb. Class Valve under several DP conditions. A review ofTable 4-3 in Reference 7 indicated that the ratio ofthe measured thrust to hard seat and the PPM predicted thrust to hard seat (using the default friction coefficients) ranged from 0.09 to 0.21. In other words, the PPM calculation ofthrust to hardseat overestimated the actual measured thrust from 4.76 to 11.1 times. This is considered to be an excessively conservative prediction, especially when compared to the test results for 313. Therefore, the EPRI PPM prediction for hardseating was not considered to provide a reasonable prediction ofthe true thrust to hardseat MOV313.
Additional analysis to determine thrust requirements for flow isolation and disc hard-seating was performed by Kalsi Engineering (reference 26). The intent ofthe analysis was to review the excessive conservatisms applied by the EPRI methodology and incorporate realistic conditions ofMOV313 thus providing a more accurate diagnosis ofrequired thrust values needed for hard seating. A total ofnine different load cases were analyzed for various conditions. Conclusions yielded that MOV313 willclose and achieve a hard-seating condition under the present torque switch setting.
Seat coefficient offriction of.35 is a reasonable bounding value.
MOVProgram Plan EWR 5111 Attachment K-Page 18 Revision 1
Date 2-20-98
I
The open and closed valve factors were calculated for the EPRI MOVby use ofthe test data in Attachment 2 ofreference 7 and the equations in Attachment K-3 ofthis report. Per the Attachment K-3 calculations, the EPRI open valve factors ranged from 0.17 to 0.26 and the close valve factors based on the thrust to hard seat ranged from 0.17 to 0.66. The high valve factors to hard seat (0.45 to 0.66) were all encountered when the valve was stroked against approximately 275 psid. Ofthe EPRI tests performed at 180 psid, the maximum valve factor to hard seat was 0.30.
In addition to the EPRI valve, dynamic test data was available on 4"150 Lb. Class Aloyco Split Wedge Gates from Indian Point Unit 2 and Crystal River (references 1S and 19). The Indian Point 2 MOVwas tested at 92.8 psid and the hard seating valve factor (adjusted for measurement uncertainty) was 0.41. The Crystal River MOV was tested at 128 psid and the hard seating valve factor (adjusted for measurement uncertainty) was 0.32. The valve factors for the Indian Point and Crystal River valves were calculated in Attachment K-4.
Based on the 313 test results, Kalsi Engineering analysis, IP2 data, and Crystal River data, a valve factor of 0.50 in the standard industry equation to establish the minimum thrust requirement is acceptable for hard-seating ofthe valve under design basis conditions.
10"x 8"x10" 1500 class, Aloyco Split Wedge Gate Valves (Group A2)
There are two valves (896A/B) ofthis type (shown on drawing E-43540) in the GL 89-10 program.
The seating surfaces are hard faced with stellite.
Per reference 16, 896A/B are not required to be leak tight, and flow isolation was the functional requirement in the close direction for that MOV.
The MEDP for opening these MOVs is 33 psi based on the minimum threshold value in EWR-5080 R/8. A review ofEWR-50SO R/8 indicated that both MOVs are normally open and are not required to stroke to the open position during a design basis event.
Hence, there is no design basis safety function to open the MOVs, and the opening valve factor was not considered to be ofcritical importance.
Per EWR-5080 R/8 896A/B are required to be closed via a manual remote signal during switch over to recirculation aAer all pumps have been stopped.
The closing pressure across the valve under this scenario is negligible, and the closing valve factor was also not considered to be ofcritical importance for these MOVs.
Therefore, a valve factor is not needed to calculate the required thrust for the valves to perform their safety related function, and any reasonable value is acceptable for use in thrust calculations.
Westinghouse Flex Wedge Gate Valves 3" 20350 class Westinghouse Flex Wedge Gate Valve (Group Wl)
There is one valve (9746) ofthis type (shown on drawing 1168378D38) in the GL 89-10 program. The seating surfaces and disc guides are hard faced with Stellite. Per reference 16, this valve (9746) does not have a defined leakage limit,and flow isolation was the functional requirement in the close direction.
Per EWR-5080 Rev. 8, MOV9746 is required to close to isolate the "D"train SBAFW discharge piping and divert flowthrough the cross-connect.
The pump is stopped prior to closing the valve, and the DP and line pressure willessentially be 0. The minimum threshold value of33 psi was specified as the MEDP in EWR-5080. Therefore, a valve factor is not needed to calculate the required thrust for the valve to perform its safety related function, and any reasonable value is acceptable for use in thrust calculations.
MOVProgram Plan EWR 5111 Attachment K-Page 19 Revision 1
Date 2-20-98
Crane Flex Wedge Gate Valves 3" 150¹ class Crane Flex Wedge Gate Valves (Group C1)
'here are two valves (759A/B) ofthis type (shown on drawing K-6298) in the GL 89-10 program.
The seating surfaces are hardfaced with Stellite and the guide rails are carbon steel. Per reference 16, valves 759A/B are required to be leak tight. Therefore, hardseating was the functional requirement in the close direction.
Per EWR-5080 Rev. 8, the MOVs are required to close on receipt ofa containment isolation signal against 140 psid. MOV759B was successfully DP against approximately 70 psid in both directions, however, reference 24 concluded that the DP loads were too low (less than 1000 Lbs) to accurately calculate a valve factor. MOV759A was also tested against DP in the close direction, but direct thrust measurements were not obtained, and a valve factor could not be determined.
These valves are the same model as the 6", 813/814 valves and are shown on the same valve drawing. Since the 813/814 and 759A/B valves and service conditions are similar, a valve factor of0.90 based on the dynamic test of814 should be used as the interim open and close valve factor for 759A/B. Since the dynamic test ofthese MOVs does not produce enough DP load to calculate a valve factor, a PPM calculation should be performed in the long term The 0.90 value agrees well with the ComEd nominal valve factor for 3" Crane valves of0.75 plus the adjustment of0.10 and is slightly less than the conservative group valve factor of0.95.
6" 150¹ class Crane Flex Wedge Gate Valves (AllStellite Seating Surfaces) (Group C2)
There are two valves (813/814) ofthis type (shown on drawing K-6298) in the GL 89-10 program.
The seating surfaces are hardfaced with Stellite and the guide rails are carbon steel.
Per reference 16, valves 813, and 814 are required to be leak tight. Therefore, hardseating was the functional requirement in tlie close direction. Per EWR-5080 R/8 813/814 are required to close against a design basis DP of 100 psid and are not required to open in response to a design basis event.
Both 813 and 814 were tested against DP, but a valve factor could only be calculated for the 814 valve. The as-tested, adjusted close valve factor for 814 was 0.84.
Since the 813/814 valves and service conditions are identical, a valve factor of0.90 based on the dynamic test of 814 should be used as the interim open and close valve factor for 813 until additional dynamic testing ofthe 813 MOV is performed.
The 0.90 value is significantly greater than the ComEd nominal valve factor for 6" Crane valves of 0.68 plus the adjustment of0.10 and is equal to the conservative group valve factor.
6" 150¹ class Crane Flex Wedge Gate Valves (Disc Not Hardfaced) (Group C3)
There is I valve (4663) ofthis type (shown on drawing C-3151991-A) in the GL 89-10 program. The disc seating surface is A217 Gr. CA15 and is not hardfaced.
The body seat rings are hardfaced with Stellite.
Due to the different disc hardfacing materials, the 4663 valve was not considered to be identical to the 813/814 valves.
Per reference 16, 4663 does not have to provide a leak tight seal. Therefore, flow isolation was the functional requirement in the close direction. Per EWR-5080 R/8 4663 is required to close agairist a design basis DP of 95 psid and is not required to open in response to a design basis event.
MOVProgram Plan EWR 5111 Attachment K-Page 20 Revision 1 Date 2-20-98
MOV4663 was DP tested in the close direction at 59% ofthe design basis DP and the adjusted valve factor was 0.41. However, from figure 4, the minimum EPRI test DP was not achieved..
The minimum EPRI test pressure for 150¹ class valves is 60 psid, which is a mere 4 psi more than the test pressure for 4663. Since the design basis DP for 4663 is only 95 psid and test was performed by use ofa system alignment similar to the design basis condition, the 56 psid DP test and as-tested valve factor is considered to be acceptable for use on 4663.
10" 150¹ class Craze Flex Wedge Gate Valves ( Disc Not Hardfaced) (Group C4)
There is 1 valve (4670) ofthis type (shown on drawing C-3151560 Rev. C) in the GL 89-10 program. The disc seating surface is A217 Gr. CA15 and it is not hardfaced.
The body seat rings are hardfaced with Stellite.
The valve is not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction.
Per EWR-5080 R/8 4670 is required to close against a design basis DP of95 psid, and is not required to open in response to a design basis event. MOV4670 was tested against DP, but direct thrust measurements were not obtained, and a valve factor could not be determined. This valve is the same model (47 Ys XU-F) as the 4663 6"valve.
A valve factor of0.90 is significantly greater than the ComEd nominal valve factor for 10" Crane valves of 0.60 plus the adjustment of0.10 and the conservative group valve factor of0.80. Therefore, a value of0.90 should be used as the interim open and close valve factor for 4670 until additional dynamic testing or a PPM Calculation can be performed.
F Crane Solid Wedge Gate Valves 10" 150¹ class Crane Solid Wedge Gate Valves (AllStelllte Seating Surfaces) (Group C5)
There are two valves (738A/B) ofthis.type (shown on drawing K6299) in the GL 89-10 program. Both the seating surfaces are hardfaced with Stellite for the 738A/B valves. These valves are not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction.
Both 738A/B were DP tested in the open and close direction.
Therefore, sufficient Ginna test data was available to formulate a long term valve factor basis.
10" 150¹ class Crane Solid Wedge Gate Valves ( Stelllte on Stainless Steel Seating Surfaces) (Group C6)
There is 1 valve (4664) ofthis type (shown on drawing K-1055) in the GL 89-10 program. The disc is hardfaced with stellite and the body seat ring is "Exelloy"(410 SS) for 4664. Due to the different disc hardfacing materials, the 4664 valve was not considered to be identical to the 738A/B valves.
This valve is not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction.
Per EWR-5080 R/8 4664 is required to close against a design basis DP of95 psid, and is not required to open in response to a design basis event.
MOV4664 was successfully DP tested in the close direction and the adjusted close valve factor was 0.64. Therefore, sufficient Ginna test data was available to formulate a long term valve factor basis for this MOV.
MOVProgram Plan EWR 5111 Attachment K - Page 21 Revision 1 Date 2-20-98
20" 1500 class Crane Solid Wedge Gate Valves (Group C7)
There is 1 valve (4615) ofthis type (shown on drawings PB-137988 and AA-FA-VAA-A)in the GL 89-10 program. The seating surfaces are hardfaced with 410 SS (14% chrome). The seat ring is not hardfaced.
This valve is not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction.
The valve was DP tested in the open and close direction.
Therefore, sufficient Ginna test data was available to formulate a long term valve factor basis.
20" 1508 class Raimondi Solid Wedge Gate Valves (Group R1)
There is 1 valve (4616) ofthis type (shown on drawing AA-FA-VAA-A)in the GL 89-10 program. The seating surfaces are hardfaced with 410 SS (14% chrome) and the seat ring is hardfaced with Stellite.
The valve is not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction.
The valve was DP tested in the open and close direction.
Therefore, sufficient Ginna test data was available to formulate a long term valve factor basis.
Velan Flex Wedge Gate Valves 3" 15008 class Velan Flex Wedge Gate Valves (Group V1)
There are two valves (871A/B) ofthis type (shown on drawing 88405-4) in the GL 89-10 program. The seating surfaces are hard faced with Stellite No. 6 and the guide rails are stainless steel with 4 stellited pads.
Per reference 16, valves 871A/B do not have to be leak tight, and flow isolation was the functional requirement in the close direction.
Both ofthe valves were DP tested in both directions, and the data could be used to calculate valve factors.
Therefore, sufficient Ginna test data was available to formulate a long term valve factor basis.
6" 15000 class Velan Flex Wedge Gate Valves (Group V2)
There are two valves (852A/B) ofthis type (shown on drawing 88405-5) in the GL 89-10 program. The seating surfaces are hard faced with Stellite No. 6 and the guide rails are stainless steel with 4 stellited pads.
Per reference 16, valves 852A/B are required to be leak tight, and therefore, hard seating was the functional requirement in the close direction.
The design basis opening scenario for 852A/B is against 2250 psi due to check valve leakage with a negligible flow rate. 852A/B are not required to close during a design basis event. The similar 871A/B (3")
valves were DP tested against approximately 1500 psi.
Upon comparison ofthe valve drawings for the 6" and 3" valves, the parts and materials appear to be identical. Therefore, application ofthe 871A/B data to the non-tested 6" valves for short term use was justified based on the similarityofthe valves, the EPRI finding that valve friction factors typically decrease with increasing DP and the ComEd finding that valve factors typically decrease with valve size. Hence, the valve factor for the 6" valves would be expected to be less than the lower DP 3" valves.
Per EWR-5080 Rev. 8, the flowrate under design basis conditions the MOVs is 0 gpm. Therefore, the possibility ofguide rail bending due to the Velan design is considered to be remote. In addition, these valves have been tested under static conditions, and any indication of guide rail bending due to previous strokes was not apparent in the static test data.
MOVProgram Plan EWR 5111 Attachment K - Page 22 Revision 1
Date 2-20-98
t~~
Per reference 23, these valves are susceptible to pressure locking. The pressure locking scenario is significantly more severe than opening the valve with DP across the disc. Therefore, the design basis pressure locking calculation should be used to establish the minimum required opening thrust. The valves do not have a closing design basis function, and the close valve factor value was not considered to be of critical importance.
10" 1500¹ class Velan Flex Wedge Gate Valves (Group V3)
There are two valves (700/701) ofthis type (shown on drawing 88904-1) in the GL 89-10 program. The seating surfaces are hard faced with Stellite No. 6 and the guide rails are stainless steel with 4 stellited pads.
Per reference 16, both ofthese valves are required to be leak tight, and therefore, hard seating was the functional requirement in the close direction.
Per EWR-5080 R/8 700/701 these valves do not meet the general requirements ofGL 89-10, but are considered to be "high risk." They are required to open and close against a design basis DP of410 psid.
The 3" 1500¹ class Velan Gate valves tested at Ginna yielded a maximum adjusted valve factor of0.46. The size differential between these valves and the 3" valves was too great to regard the valves as similar.
EPRI tested a 10" 1500¹ class Velan gate valve under steam blow down conditions as part ofits flow loop test program. Since the 700/701 MOVs are not subjected to steam blow down, the EPRI tests were not considered to be applicable.
Dynamic test data on two identical valves was obtained, at Carolina Power &
Light's H.B. Robinson Unit 2.
The adjusted open and close valve factors were calculated by use ofthe H.B. Robinson test data (References 21 and 22) and the equations in Attachment K-4. From Attachment K-4, the maximum adjusted open and close valve factors were 0.69 and 0.67. Per figure 7, the Robinson data meets the minimum EPRI criteria, but is only 32% ofthe design basis DP for the Ginna 700/701 valves.
Nevertheless, the Robinson data was the best available.
Since these valves do not meet the general requirements ofGL 89-10 a valve factor of0.70 based on the Robinson data should be used as the long term valve factor for these MOVs.
The 0.70 valve factor agrees well with the ComEd nominal valve factor for 10" 1500¹ Velan valves of0.595
'lus the adjustment of0.10.
Borg-Warner Flex Wedge Gate Valves 4" 300¹ class Borg-Warner Flex Wedge Gate Valves (Group BW1)
There are two valves (9629A/B) ofthis type (shown on drawing 73480) in the GL 89-10 program. The seating surfaces are hardfaced with stellite and the guide rails are heat treated stainless steel. The valves are not required to be leak tight (per reference 16), and flow isolation was the functional requirement in the close direction. Per EWR-5080 R/8 9629A/B are required to open and close against a design basis DP of95 psld.
MOV9629A was tested against DP, and the measured valve factors were 0.27 (close) and 0.30 (open). From figure 5, the minimum EPRI test DP was not achieved, however, the design basis condition of95 psid does not meet the minimum EPRI criteria either. The test was performed at 83% ofthe design basis DP, and the Ginna test data should be used to formulate a long term valve factor basis for 9629A.
The most similar valve in the EPRI test program was a 6" 150¹ class Borg-Warner flex wedge gate valve.
The maximum open disc friction coefficient was 0.872 and the maximum close value was 0.879. The bounding ComEd valve factor for Borg-Warner gate valves was 0.65 based on the maximum EPRI disc to seat coefficient offrictionof0.61 adjusted for a 5 wedge angle. This method was not considered MOVProgram Plan EWR 5111 Attachment K-Page 23 Revision 1
Date 2-20-98
acceptable for use at Ginna. Data from Comanche Peak in Reference 15 was also reviewed. Comanche Peak tested 16, 4" Borg-Warner valves under a wide range ofDP and flowconditions. The maximum valve factor for 4" Borg-Warner valves at Comanche Peak was 0.62.
During the EPRI test program, Borg-Warner valves exhibited higher than expected apparent disc friction coefficients at low DP due to parasitic thrust effects. In addition, NRC IN 89-61, "Failure ofBorg-Warner Gate Valves To Close Against Differential Pressure," discussed higher than expected valve factor (ranging from 0.38 to 0.74) for 4" 1500¹ class Borg-Warner gate valves at Catawba.
Due to the poor performance ofBorg-Warner valves in the EPRI program, a valve factor of0.90 should be used as the interim open and close valve factor for 9629B until dynamic testing of9629B is performed.
This value is very conservative when compared to the results ofthe 9629A DP test. It should also be noted that based on the present configuration and switch settings, both valves are capable ofopening and closing at valve factors much greater than 0.90..
GL 89-10 Globe Valves With the exception ofthe Fisher, balanced disc globe valves (9701A/B), Ginna station valve factor test data was not available to form a basis for the valve factor for globe valves.
Without available site specific test data, the valve factors for Ginna globe valves were determined based on the EPRI finding that ifthe appropriate area (seat or guide) is used, valve factors for incompressible flow are in the range from 0.9 to 1.1. Each Ginna globe valve types was compared to the globes in reference 4 to determine ifthey were seat or guide based.
The appropriate area was then used in the thrust/torque calculation along with a valve factor of 1.1.
Evaluation ofGlobe Valve Design Basis Flow Conditions Fisher Balanced Disc Globe Valves (Group Fl)
Valves 9701A/B are Fisher, balanced disc globe valves, which have been DP tested.
The manufacturer supplied the methodology used in the required thrust calculation.
These MOVs were DP tested and the calculated requirements agreed well with the dynamic test results. It should beeoted that the Fisher methodology is comparable to using a valve factor of 1.0.
2" 1500¹ class Velan Globe Valves (Group V4)
The design basis flowrate for valves 897/898 is 0 gpm at a temperature of 80 F. The valves are 2" Velan globes, and a review ofthe valve drawing (E-73-0545) indicated that they are seat based.
Since the design basis flowand'temperature are low, the use ofa 1.1 valve factor with the appropriate area was acceptable based on the EPRI test results.
3" 900¹ class Rockwell/Edwards Globe Valves (Group RE1)
The design basis flowrate for valves 4007/4008 is 230 gpm at a temperature of 100 F. The valves are 3" Rockwell globes, and a review ofthe valve drawing (P-447997) indicated that they are seat based.
Since the design basis flowand temperature are low, the use ofa 1.1 valve factor with the appropriate area was acceptable based on the EPRI test results.
MOVProgram Plan EWR 5111 Attachment K - Page 24 Revision 1 Date 2-20-98
3" 15000 class Rockwell/Edwards Globe Valves (Group RE2)
The design basis flowrate for valves 9703A/B is 200 gpm at a temperature of 100 F. The valves are 3" Rockwell globes, and a review ofthe valve drawing (ACD-31602215) indicated that they are guide based.
Since the design basis flowand temperature are low, the use ofa 1.1 valve factor with the appropriate area was acceptable based on the EPRI test results.
3" 900ff class Rockwell/Edwards Globe Valves (Group RE3)
The design basis flowrate for valves 9704A/B is 200 gpm at a temperature of 100 F and DP of 1461 psi.
The valves are 3" Rockwell stop checks, and a review ofthe valve drawing (ACD-31602220) indicated that they are guide based.
These valves are in'he Stand By AuxiliaryFeed Water System, and since the design basis flowrate and temperature are low use ofa 1.1 valve factor with the appropriate area was acceptable based on the EPRI test results.
14" 900N class Rockwell/Edwards Stop Check Valves (Group RE4)
The design basis flowrate for valves 3976/3977 is 0 gpm at a temperature of 345 F and DP of400 psi. The valves are 14" Rockwell stop checks, and a review ofthe valve drawing (P-447073) indicated that they are seat based.
These valves are in the Main Feed Water System, and since the design basis flow rate is 0 gpm, they willnot be subjected to a blowdown condition. Therefore, the design basis fluid is expected to be liquid water, and the use ofa 1.1 valve factor with the appropriate area was acceptable based on the EPRI test results.
These valves were both DP tested, and the test results supported the use of a 1.1 valve factor.
Valve Factor and Required Thrust Conclusions Based on the process in Figure 1, each gate valve in the Ginna GL 89-10 program was evaluated to determine:
~
ifa long term valve factor could be justified
~
the value of long term and interim valve factors
~
a recommended required thrust methodology and action for long term resolution based on the feasibility ofdynamic testing the valve.
The recommended required thrust methodology and action required for long term resolution are summarized in Attachment K-5 for each gate valve in the Ginna GL 89-10 program. The long term and interim valve factor values and basis for the values (as discussed previously) are summarized in Attachment K-6.
The present valve factor of 1.10 and standard industry equation used for unbalanced disc globe valves in the Ginna GL 89-10 program is considered adequate at this time based on EPRI and Ginna globe valve test data.
Further justification ofthis value should be obtained as part ofthe MOVPeriodic Verification Program, by performing a representative sample ofdynamic tests or obtaining and evaluating industry test data on similar globe valves.
It should be noted that as additional dynamic test data is obtained, this evaluation willneed to be revised to incorporate and evaluate the results ofthose tests and account for the reasonable and expected variation in valve factors based on the data scatter. In addition, the method used to account for valve factor degradation should be confirmed or refined when results ofthe Joint Owner's Group (JOG) Program on MOVPeriodic Verification methodology become available. The margins that have been applied to the as-tested valve factors are shown in Attachment K-7. This Attachment is provided for future comparison to the results, of the JOG Program on MOVPeriodic Verification.
MOVProgram Plan EWR 5111 Attachment K-Page 25 Revision 1
Date 2-20-98
4.
Analysis ofLoad Sensitive Behavior and Stem Coefficient ofFriction Load Sensitive Behavior EPRI and industry test data has demonstrated that MOVoutput thrust at close control switch trip can be significantly lower under dynamic (differential pressure) conditions than the output thrust under static conditions. This phenomenon has been called the "rate-of-loading" effect or "load-sensitive behavior".
EPRI testing has shown that the thrust change from static to dynamic conditions was due mainly to changes in the coefficient offriction (p) at the stem to stem nut interface. The change in p was found to be caused by a "squeeze film"effect. Under static conditions the load between the stem and stem nut increases rapidly when the valve disc impacts the seat. This rapid loading does not allow enough time for the lubricant to flowout ofthe stem/stem nut interface. Under these circumstances, the parts can be supported on a thin filmofpressurized lubricant which is a mixture ofboundary and hydrodynamic lubrication.
Under dynamic conditions, the load increases slowly due to the build up ofdifferential pressure forces.
Under this loading, there is enough time for the lubricant to be squeezed from between the parts resulting in higher coefficients of friction associated with boundary lubrication. 'The precise extent to which the phenomenon occurred for a particular stem, stem nut, and lubricant combination was found to be
- unpredictable.
Close torque switch settings are verified by measuring the thrust at control switch trip (CST) under static test conditions. Where practical, DP testing should be performed to verify proper switch settings under design basis flowand pressure.
However, since it is not possible to DP test all 89-10 MOVs, the potential decrease in thrust under dynamic conditions must be accounted for when establishing the minimum close thrust at CST criteria for MOVs which were only tested under static conditions.
Load sensitive behavior uncertainty is accounted for in the Target Thrust/Torque Calculations.
The required minimum acceptable thrust at CST for static testing is increased by appropriate factors to ensure that the combined effect ofall uncertainties willnot result in insufficient thrust at CST to close the valve under dynamic conditions.
The potential differences in the thrust at CST under dynamic versus static conditions may be accounted for by use of a load sensitive behavior correction factor (LSB). The value ofthe correction factor can be calculated for MOVs which have adequate close DP test thrust data by use of Equation (1).
where LSB% = [(S. TilTST - D. ThTST) / S. TiiTST]
~ 100 Eq. (1)
S.ThTST
= Static Closing Thrust at Control Switch Trip D.Th.TST
'= Dynamic Closing Thrust at Control Switch Trip The correction factor is used to adjust the target closing thrust value determined in the target thrust/torque calculations as follows:
Req'd Thrust Under Static Conditions = Req'd Thrust Under Design Basis DP Conditions ( 1 + LSB)
- where, LSB = LSB Correction Factor.
Eq. (2)
MOVProgram Plan EWR 5111 Attachment K-Page 26 Revision 1 Date 2-20-98
V 1
4 I
Stem Coefficient ofFriction (p-Stem)
The stem coefficient offriction is calculated from the measured stem factor and physical dimensions ofthe stem threads. The stem factor is the ratio ofthe closing torque at CST to closing thrust at CST. The torque and thrust are not adjusted for instrument error. The stem coefficient offriction is calculated using Equation (3).
where:
24 (Tq.TST/Th.@TST)
(tan )I ) + ds p
=
cos $2 [24 (Tq.@TST/Th.@TST) ds tan $ 1 ]
Equation (3)
= stem thread tooth pressure angle (from Table 1)
= stem thread lead angle
= tan'stem thread lead/nQ
= stemthreadpitchdiameter
= d ~ -h d;~ = stem thread major (outside) diameter h = stem thread height Tq.ITST =Closing Torque at Torque Switch Trip from Static or DP test Th.@TST = Closing Thrust at Torque Switch Trip from Static or DP test ACMEScrew Thread Type
$, (degrees) h (in.)
Standard Stub 14.5 14.5 0.5 0.3 Table 2: ACME Power Screw Dimensions Application ofGinna LSB and Stem Coefficient ofFriction Test Results As discussed in the Introduction, the two best sources oftest data for validating assumptions are valve specific data and plant specific data. Actual dynamic testing is not practicable for many valves. Other valves may have been tested in the past only to have subsequent industry experience and improvements in testing technology cast doubts on the data which was obtained. As a result, the possibility exists for a significant number ofvalves to be lacking in reliable, supporting test data; therefore, the need to apply plant specific test data becomes increasingly important.
Industry experience has shown that when applying measured test data to non-tested valves, the load sensitive behavior and stem coefficient offriction tend to be a function ofplant specific maintenance practices such that measured test results can generally be applied to all valves at a particular facility. Values of load sensitive behavior, and stem coefficient ofcan be calculated from the measured data using equations I and 3. Because ofthe uncertainty associated with the measured values, some type ofstatistical method should be employed prior to the application ofthe calculated results.
MOVProgram Plan EWR 5111 Attachment K-Page 27 Revision 1
Date 2-20-98
The following is an acceptable method for statistical analysis.
Mean = Zx/ n Sample Standard Deviation = [(nZx> - (Zx)>)/ n(n-1)]>/2 By calculating the mean and the standard deviation, a 97% confidence value can be determined as the mean plus 2 standard deviations. This value represents a generally acceptable, conservative bounding value for the value in question.
Evaluation ofLSB 8r, p-Stem Test Data The available DP test data packages were reviewed to determine the measured values ofthrust at CST (static
&dynamic), and N -Stem (static &dynamic).
The data that was extracted to evaluate LSB is presented in Table 3 for the reliable DP tests as determined in section 3 ofthis evaluation. The evaluation was based on a statistical analysis of load-sensitive-behavior (LSB), and stem coefficient offriction (p-Stem). The entire population ofavailable data was used for the analysis ofLSB and p-Stem since these factors are generally independent ofvalve type and application.
The percent LSB for each valve was derived from the thrust at CST (static and dynamic) by use ofequation (l). The calculated values are recorded in Table 3. The values ofp-Stem were taken directly from the DP test data packages. Static test p-Stem values are shown in Table 4 and the dynamic p-Stem values are shown in Table 5.
Valve ID Work Order 738A 19221443 738 B 19221441 19221433 814 Test Date 22-Mar-94 20-Mar-94 20-Mar-94 7305 10202 3619 7490 N/A 3594 2 47%
N/A
-P 7P%
D. Th@TST S. Th@TST LSB 857A 19604163 857B 19702113 871A 19404023 871 B 19221428 3504A 19703805 3505A 19604599 4615 19402962 09-Nov-96 04-Nov-97 06-Oct-94 02-Apr-93 03-Dec-97 11-Nov-96 19-Apr-95 4637 4487 3423 7447 12848 18547 19546 5095 4542 N/A 8290 13098 20068 21071 8 99%
1.21%
NIA 10.17%
1.91%
7 58%
7 24%
4616 19221506 02-Apr-94 20471 20116
-1.76%
4663 19400660 4664 19504253 9629A 19702111 9746 19400530 01-Mar-94 08-Apr-96 17-Feb-97 24-Feb-94 3208 6424 7929 5427 3299 7419.3 7468 5562 2.76%
13.42%
2.43%
Mean 3.92%
Sample Standard Deviation ( < )
5.64%
Mean + 2o 15.20%
Maximum 13.42%
Table 3: LSB Test Data MOVProgram Plan EWR 5111 Attachment K - Page 28 Revision 1
Date 2-20-98
Valve ID 18138 313 3504A 3505A 4615 4616 4663 4664 515 516 700 701 738A 7388 7498 759A 7598 813 814 852A 8528 856 857A 8578 857C 865 8968 9629A 9701A 97018 Test Type'tatic Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Static Test Date 30-Mar-94 22-May-96 07-May-96 11-Nov-96 06-May-96 05-Nov-96 09-May-96 08-Apr-96 17-Apr-95 18-Apr-95 16-Mar-94 15-Mar-94 22-Mar-94 15-Apr-96 26-Mar-94 26-Mar-94 23-Oct-97 01-May-96 20-Mar-94 08-Sep-96 09-Sep-96 22-Mar-94 09-Nov-96 04-Nov-97 03-Nov-96 11-Mar-94 17-Apr-96 01-Nov-97 14-Apr-95 13-Apr-95 ttSTEM 0.045 0.134 0.142 0.119 0.069 0.086 0.131 0.072 0.101 0.097 0.072 0.070 0.192 0.115 0.126 0.116 0.114 0.148 0.108 0.075 0.095 0.114 0.115 0.104 0.091 0.091 0.038 0.037 0.120 0.117 Mean Sample Standard Deviation ( rr )
Mean+
2'aximum 0.102 0.034 0.169 0.192 Table 4: Static Test p-Stem Data MOVProgram Plan EWR 5111 Attachment K-Page 29 Revision 1
Date 2-29-98
Valve ID 3504A 3505A 4615 4616 4663 4664 738A 738B 814 857A 857B 871A 871B 9629A 9701A 9701 B Work Order 19703805 19604599 19402962 19221506 19400660 19504253 19221443 19221441 19221433 19604163 19702113 19404023 19221428 19702111 19402945 19221941 Test Type DP DP DP DP DP DP DP DP DP DP DP DP DP DP DP DP Test Date 03-Dec-97 11-Nov-96 19-Apr-95 02-Apr-94 01-Mar-94 08-Apr-96 22-Mar-94 20-Mar-94 20-Mar-94 09-Nov-96 04-Nov-97 06-Oct-94 02-Apr-93 17-Feb-97 14-Apr-95 21-Apr-93 0.106 0.051 0.056 0.129 0.138 0.091 0.213 0.127 0.138 0.108 0.113 0.123 0.204 0.044 0.117 0.124 Mean Sample Standard Deviation ( tr )
Mean+
2'aximum 0.118 0.046 0.210 0.213 Table 5: Dynamic Test p-Stem Data The statistical analysis ofLSB and p-Stem shows that using a 97% confidence value of"mean plus 2 sigma" results in:
%LSB
= 15.72 p-Stem (static)
= 0.19 p -Stem (dynamic)
= 0.21 These are bounding values and are in good agreement with accepted industry experience.
Load Sensitive Behavior Conclusions Based on the 97% confidence LSB value of 15.20%, an LSB "bias" term of 15% was selected for use in thrust/torque calculations for Ginna GL 89-10 MOVs. The 15% value bounded 13 ofthe 13 available data points.
Another acceptable method to address LSB is by use ofa "bias" (direct multiplier) and "random" (combined by the square root ofthe sum ofthe squares (SRSS) technique with other uncertainties such as measurement error and torque switch repeatability factor). This willbe referred to as the "SRSS'ethod. Ifthe "SRSS" method were used, a bias value of3.92% and random value (equal to 2 standard deviations) of 11.28%
would be used to account for LSB based on the statistical LSB results in Table 4.
The use ofthe "SRSS" type methodology removes excessive conservatism in the application ofthe
- LSB, measurement error, and torque switch repeatability factors.
While the benefits ofusing this methodology are desirable, it can become difficultto implement. Therefore, for simplicity, it was decided that a single "bias" term would be used to account for LSB. In order to demonstrate the conservatism ofthe 15% value selected to account for LSB at Ginna, an evaluation ofthe combined effect ofLSB, measurement uncertainty, and torque switch repeatability factors was performed.
MOVProgram Plan EWR 5111 Attachment K-Page 30 Revision 1 Date 2-20-98
SRSS method The overall required thrust multiplier using the SRSS method can be calculated by use ofthe followingequation:
Required Thrust Multiplier= (1+ LSBbias) (1+ (LSBrandom 2+ eI 2+ TSrep 2) ~>)
where:
LSBbias = LSB bias term = 0.0392 from Table 4 LSBrandom = LSB random uncertainty term = 2 standard deviations = 0.1128 from Table 4.
eI = test equipment measurement uncertainty assumed to equal best possible value of0.05.
TSrep = torque switch repeatability assumed to equal best possible value of0.05.
Required Thrust Multiplier= (1+ 0.0392) * (1+ (0.1128 2+ 0.05 2+ 0.05 2) ~>)
Required Thrust Multiplier= 1.178 by SRSS method LSB Bias Method The overall required thrust multiplier using the LSB Bias method can be calculated by use ofthe following equation:
Required Thrust Multiplier= (1+ LSB) (1+ (eI 2+ TSrep 2) ~>)
where:
LSB = 0.15, which was selected to account for LSB effects at Ginna.
eI = test equipment measurement uncertainty assumed to, equal best possible value of0.05.
TSrep = torque switch repeatability assumed to equal best possible value of0.05.
Required Thrust Multiplier= (1+ 0.15) * (1+ (0.05 2+ 0.05 2) ~>)
Required Thrust Multiplier= 1.23 by LSB Bias method When compared to the SRSS method, the use ofan LSB value of0.15 results in an additional conservatism ofapproximately 4%, [(1.23-1.178)/1.178].
By calculating LSB in accordance with equation (1) and applying the 15% LSB factor in accordance with equation (2), the resulting Required Thrust Under Static Conditions is approximately 2.3% lower than ifthe Required Thrust Under Design Basis DP Conditions wer'e divided by (1-LSB). This was offset by the conservatism ofthe LSB Bias method used in the calculations.
Based on a comparison ofthe 2 methods, a value of0.15 can be used as the LSB correction factor. The resulting required thrust multiplier for the SRSS and Bias methods have been compared using various combinations ofeI and TSrep values, and the bias method was found to produce a larger multiplier in all cases with an LSB value equal to 0.15. Based on the evaluation ofthe SRSS and bias methods the use ofa 0.15 LSB value willproduce conservative and appropriate adjustment ofthe required thrust in the thrust/torque calculations.
The values/methods to account for LSB in RG&E MOVcalculations, which are used for both the open and close directions, were determined by use ofthe followingcriteria:
- 1) For MOVs which have been adequately tested under DP Conditions A)
The "as-tested" %LSB value calculated in Table 3 may be used in the thrust/torque calculation for the subject MOV.
MOVProgram Plan EWR 5111 Attachment K-Page 31 Revision 1
Date 2-20-98
B)
IF additional conservatism is desired, the LSB correction factor of 15'%ased on the preceding analysis data may be used in the thrust/torque calculation for the subject MOV.
C)
An acceptable alternative method to account for LSB in test and margin calculations setup for open and limitswitch close MOVs is to convert the minimum required thrust to overcome design basis DP and available thrust capability to corresponding torque values by use ofthe as-tested dynamic stem factor or a dynamic stem factor based on a coefficien offrictionof0.20.
The 0.20 value is justified based on the statistical analysis ofthe dynamic stem coefficient of friction data.
- 2) For MOVs which have NOT been adequately tested under DP Conditions A)
The LSB correction factor of 15% based on the statistical analysis ofGinna test data may be used in the thrust/torque calculation for the subject MOV.
B)
An acceptable alternative method to account for LSB in test setup and margin calculations is to convert the minimum required thrust to overcome design basis DP and available thrust capability to corresponding torque values by use ofa stem factor based on a coefficient offrictionof0.20.
The 0.20 value is justified based on the statistical analysis ofthe dynamic stem coefficient of friction data It should be noted that as additional dynamic test data i's obtained, this evaluation willneed to be revised to incorporate and evaluate the results ofthose tests.
Stem Coefficient of Friction Conclusions The 97% confidence values ofp-Stem (static) and p-Stem (dynamic) of0.20 and 0.21 are in good agreement with accepted industry experience and the results ofthe EPRI MOVPerformance Prediction Test Program. Therefore, a stem coefficient offrictionof0.20 was a maximum value under both static and dynamic conditions. A lower value ofp-Stem may be used in the setup calculations, as required, and where properly justified by available test data.
The stem coefficient offriction is constantly verified to be less than 0.20 during periodic MOVtesting, It should be noted that as additional dynamic test data is obtained, this evaluation may need to be revised to incorporate and evaluate the results ofthose tests.
MOVProgram Plan EWR 5111 Attachment K-Page 32 Revision 1 Date 2-20-98
Analysis ofPacking Load Packing load is a value which is obtained directly through static testing. An analysis ofavailable test data may be used to develop a window ofmargin that can be used to justify not re-testing a valve following packing adjustments (assuming the packing gland nuts are torqued to the same value). This type of analysis could be performed using a population based analysis or a group based analysis.
Population Based Analysis - a population based analysis would evaluate the available data from the entire valve population. Each measured data point should first be evaluated for validity. Ifthe data for a valve is not considered valid, the data should be removed from the analysis and the valve eliminated as a candidate for relaxed testing requirements. For the valves which pass this initial screening, a bounding, assumed packing load should be established based on EPRI recommendations, as follows:
Stem Diameter Assumed Packin Load Up to I inch I to 1.5 inch 1.5 to 2.5 inch 2.5 to 4 inch 1000 lb.
1500 lb.
2500 lb.
4000 lb.
Once the bounding EPRI number is established, each measured valve packing load (segregated into open and close directions) is divided by the bounding EPRI number to establish a packing load ratio. The mean value and the standard deviation (see section 2.5 below) are then calculated for the entire population of packing load ratios (again segregated into open and close directions). From the calculated mean and standard deviation, the performance ofGinna Station valve packing loads relative to the bounding EPRI values can be assessed with the intent to establish a packing load margin which can be used to justify relaxing test requirements Group Based Analysis - A group based packing analysis uses a different approach than that described above. The intent ofa group based analysis would be to segregate valves into groups based on similar packing performance characteristics (i.e packing type, stem diameter, stem material, valve type & service conditions, etc.). Then measured packing load data would be obtained for valves within each group. The measured data should include corresponding pairs of"as-found" and "as-left" packing loads for the same valve. This data could then be statistically analyzed to establish the expected packing load range for the group. The "as-found" and "as-left" data pairs could be used to determine the anticipated change in packing load which results from re-torquing the gland nuts. This type ofanalysis would be most useful for valves which do not have large thrust margins. Ifit can be demonstrated, for a particular group ofvalves, that the packing load is significantly less than the bounding EPRI value, then the thrust/torque calculations could be based on the smaller, measured test values while still maintaining sufficient margin to justify relaxing the testing requirements.
Initial inspection ofavailable test data showed that there was insufficient data available to support a group based analysis, therefore, a population based analysis was performed. The original scope ofthe analysis was to include gate and globe valves only, however, after reviewing the test data it was determined that there was insufficient valid globe valve data, therefore, the analysis was limited to gate valves only. The analysis was performed using the values for measure running load in the open and close direction taken from the static test data packages. Once the raw test data was collected, each data point was reviewed to establish its validity. Data points were excluded for the followingreasons:
~
The recorded value exactly equaled the bounding EPRI number. In these instances it appears that an actual measured value could not be determined and the EPRI number was recorded instead.
MOVProgram Plan EWR 5111 Attachment K-Page 33 Revision 1 Date 2-20-98
4
~
The measured values exceeded the bounding EPRI number. This is considered to be indicative of some type ofpacking problem and these valves and the associated data were excluded from consideration.
The remaining valves, not excluded for the reasons listed above, were included in the analysis and are considered candidates for relaxed testing requirement. Attachment K-8 presents the valves included in the analysis along with the associated measured packing loads.
Each measured data point listed in Attachment K-8 was divided by the associated, bounding EPRI value to establish a packing load ratio. The results are recorded in Attachment K-9.
A statistical analysis (refer to section 4) was performed for the calculated ratios as documented at the end of Attachment K-9. The results ofthe analysis show that the average packing load is approximately 40% ofthe bounding EPRI value with a standard deviation ofabout 20%. A 97% confidence, "2 sigma" value ofthe packing load ratio is about 80%. Thus the available data indicates that the maximum expected packing load ofGinna station MOVs is about 80% ofthe bounding EPRI number. Since the packing torque typically was not known prior to performance ofthe static test, it is assumed that the statistical results encompass the expected range ofpacking torque values at Ginna. In other words, the test data scatter should be indicative ofthe packing loads at both the nominal torque values and the loads at reduced gland torque values.
Therefore, retorquing the packing to the nominal torque value is also expected to be encompassed by the 80% bounding value.
Packing Load Conclusions On the basis ofthis analysis, it is reasonable to establish a margin limitat 80% ofthe bounding EPRI value determined as discussed previously. Based on the statistical results, there is a high level ofconfidence that the packing load for any given gate valve is less than 80% ofthe assumed design packing torque. Therefore, the margin limitcan then be used as a criteria forjudging whether the re-test requirements for a given valve may be relaxed. The requirement to re-test a valve followingpacking adjustment may be waived ifall ofthe followingconditions are met:
~
The valve must be a gate valve.
~
Valid static test data must be available for each valve (grouping is not supported by this analysis) which demonstrates that the measured packing load in the open and close directions is less than 80%
ofthe bounding EPRI value.
~
The scope ofthe packing adjustment must be limited to re-tightening the gland nuts, in accordance with controlled procedures, to the torque value which was established prior to obtaining the test data discussed above.
~
The packing load value used to determine target thrust/torque values to establish switch setting limits must be equal to or greater than the bounding EPRI value.
MOV Program Plan EWR 5111 Attachment K - Page 34 Revision 1
Date 2-20-98
6.
Attachments Attachment K-I - Calculation ofValve Factor From Ginna Test Data Attachment K-2 -. Open DF Thrust Traces for MOVs 860A and 860D Attachment K-.3 - Calculation ofValve Factor From EPRI Test Data for Aloyco Split Wedge Gate Valves.
Attachment K Calculation ofValve Factor From Indian Point 2 and Crystal River Test Data for 4", 150tf class Aloyco Split Wedge Gate Valves and 10" 1500/f Velan Flex Wedge Gate Valve from H.B.
Robinson Attachment K Recommended Required Thrust Methodology and Actions Required for Long Term Resolution.
Attachment K Long Term and Interim Gate Valve Factors.
Attachment K Margin For Valve Factor Degradation (in Safety-Direction) for MOVs with Long Term Valve Factors Attachment K-8-Packing Load Analysis Test Data Attachment K-9 Packing Load Analysis MOVProgram Plan EWR 5111 Attachment K - Page 35 Revision 1 Date 2-20-98
P 1
References i
NMAC Report NP-6660-D, "Application Guide for Motor Operated Valves in Nuclear Power Plants", Final Report, March 1990.
Deleted EWR-5080 Rev. 9, "RG&E Design Analysis NSL-5080-002" 4,
EPRI Topical Report
-TR-103237 Rev.
2- "EPRI MOV Performance Prediction Program (PPM):
Implementation Guide Revision 1," Electric Power Research Institute, Palo Alto, CA, October 1996.
5.
6.
EPRI Topical Report -TR-103244 Rev.
1- "EPRI MOV Performance Prediction Program (PPM): Topical Report - Revision 2," Electric Power Research Institute, Palo Alto, CA, April 1997.
EPRI Topical Report -TR-103232- "EPRI MOV Performance Prediction Program (PPM): Engineering Analysis Report for Anchor/Darling Double Disk Gate Valves," Electric Power Research Institute, Palo Alto, CA, November 1994.
7.
EPRI Topical Report -TR-103235- "EPRI MOV Performance Prediction Program (PPM): Engineering Analysis Report for Aloyco Split Wedge Gate Valves," Electric Power Research Institute, Palo Alto, CA, August 1996.
8 EPRI Topical Report -TR-103229- "EPRI MOV Performance Prediction Program (PPM): Gate Valve Model Description Report," Electric Power Research Institute, Palo Alto, CA, November 1994.
EPRI Topical Report -TR-103233- "EPRI MOV Performance Prediction Program (PPM): Engineering Analysis Report for Westinghouse Flex Wedge Gate Valves," Electric Power Research Institute,,Palo Alto, CA, November 1995.
- 10. EPRI Topical Report -TR-103227- "EPRI MOV Performance Prediction Program (PPM): Globe Valve Model Description Report," Electric Power Research Institute, Palo Alto, CA, April 1994.
- 11. Commonwealth Edison White. Paper No. 164 Rev. 1, "Anchor Darling Double-Disk Gate Valve Factors,"
October 9, 1995.ComEd
- 12. Commonwealth Edison White Paper No. 160 Rev. 0, "Crane Valve Factors," October 4, 1995.
- 13. Commonwealth Edison White Paper No. 176 Draft Rev. 0, "Borg-Warner Valve Factors," April6, 1995.
- 14. Commonwealth Edison White Paper No. 172 Rev. 0, "Miscellaneous Valve Factors," March 6, 1996.
V
- 15. BillR. Black, TU Electric-Comanche Peak Steam Electric Station, "Results of the Motor Operated Valve Engineering and Testing Program", Proceedings of the Third NRC/ASME Symposium on Pump and Valve Testing, NUREG/CP-0137, Vol. 1, July 1994.
- 16. RG8cE Inservice Test Program, Rev. 0
- 17. NRC Information Notice, IN 89-61, "Failure ofBorg-Warner Gate Valves To Close Against Differential Pressure"
'OV Program Plan EWR 5111 Attachment K - Page 36 Revision 1
Date 2-20-98
- 18. Consolidated Edison, Indian Point 2, SE-SQ-12.314, MOVDynamic Test Evaluation for Valve LCV-112C.
Test date: 3/8/93.
- 19. New York Power Authority, Indian Point 3 IP3-RPT-MULT-01345, R/1, Attachment 2, "Evaluation of Valve CH-LCV-112B"dated 1-13-98. (Includes evaluation ofCrystal River DP Testing of DHV-12).
- 20. Crane-MOVATS ER-5.0 Rev. 10 Addendum 0.
- 21. H.B. Robinson Calculation RNP-M/MECH-1471 Rev. 2, "Evaluation ofStatic and Dynamic Test Data for RHR-744A"
- 22. H.B. Robinson Calculation RNP-M/MECH-1472 Rev. 2, "Evaluation ofStatic and Dynamic Test Data for RHR-744B"
- 23. Altran Technical Report 94108-TR-01, Pressure Locking and Thermal Binding Evaluation.
- 24. Duke Engineering and Services Report, Ginna Station MOVDP Test Review, Generic Letter 89-10 Closure, dated February 18-20, 1998
- 25. Duke Engineering and Services Report, Ginna Station MOVAssessment Generic Letter 89-10 MOV Program Closure
- 26. Kalsi Engineering Document 8 2029C Rev. 0.
MOVProgram Plan EWR 5111 Attachment K-Page 37 Revision 1
Date 2-20-98
i
Attachment K-1 Calculation of Valve Factor From Ginna Test Data Page 1 of 1 CLOSE VALVEFACTORS Valve ID Adjusted Corrected Thrust to Measured Upstream Press overcome DP Static PL Stem Pressure (A)
Conectod DP OriTico Close Valve Class (M1) (Clsd)
(Clsd)
Diamotor (Clsd)
(Closed)
Area Factor 0857A 6x4x6 A/0 DD 300 1864 293 1.375 170 187 15.904 OA4 814 6'rane FW 150 4663 6
Crano&h FW 150 2304 1795 186 0.875 106 91 26.970 0.84 1123 1.125 56 56 26.970 0.41 4615 20 Crane FW 150 4616 20 Crane FW 150 17090 374 2.250 95.2 92.2 338.163 0.62 14821 740 2.000 107.2 103.2 338.163 0.39 4664 10 Crane FW 150 5454 546 1.625 86 86 85.932 0.64 0738A 10 Crane SW 150 3320 816 1.625 113.5 98.1 88.247 0.26 0738B 10 Crane SW 150 3049 993 1.625 104.5 89.1 88.247 0.23 0871A 3
Velan FW 1500 4214 604 1.125 1480 1420 5.157 0.29 0871 B 3
Velan FW 1500 4558 1101 1.125 1460 1390 5.157 0.28 Closed VF
~ (M1-Moasurod PL<tom Ares'Upstrosm Prossuro)/(DP Origo Area)
Test data from M%4.1.6 Dots Shoots for Each MOVexcept for 857A which is from Attschmont 2 adjustod by 1.414 k road. +117 Lbs..
OPEN VALVEFACTORS Valve ID 0857A 6x4x6 A/D DD Corrected Upstream Pressure (A)
(Opn)
Open Corrected Orifice Valve DP (Open)
Area Factor Adjusted Thrust Moasurod Press to overcome DP Static PL Stem
- Class, (M1) (Opn)
(Opn)
Diameter 300 1065 293 1.375 170 187 15.904 0.34 9746 3"
W FW 1500 1273 620 1.125 1360 650 8.143 0.38 4615 20 Crane FW 150 15079 1405 2.250 95.2 92.2 338.163 0.45 4616 20 Crane FW 150 12550 1296 2.000 107.2 103.2 338.163 0.33 0738A 1Q'rane SW 150 3131 982 1.625 112.5 96.1 88.247 0.28 0738B 10 Crane SW 150 3389 846 1.625 104.5 88.1 88.247 0.35 0871A 3"
Volan FW 1500 2335 2169 1.125 1480 1420 5.157 0.22 0871 B 3"
Velan FW 1500 3026 1192 1.125 1460 1390 5.157 0.46 810 1.375 990 975 26.239 0.41 Open VF
<<- (M1-Measured PL+Stem Area'Upstream Pressure)/(DP'Orffx:o Area )
MOVProgram Plan EWR 5111 Attachment K-Page 38'evision 1
Date 2-20-98
Attachment K-2 DP Thrust Traces for MOVs 857A, 860A and 860D Page 1 of5 MOV857A'Open Static and DP Thrust UllrUCtlpfDIQWe\\w v~
Tar Tscco IJr~
T19 TECCO I
-93'.r98
-293.2r0 Lb LB 8'574 52 Sta ic tra Cora~or IF",
Trace Araet ctrt er,'~g~cikiep 2,9ago s o ID'gjIDELTh-P tttCEe~l" ~
fRcZ
+Otrtt cue>
~o~}
'HoF ZI~iit CL'!'x'goy>pgDA L'"IFS!
U O'PS an '~er
'OV Program Plan EWR 5111 Attachment K-Page 39 Revision 1 Date 2-20.98
Attachment K-2 DP Thrust Traces for MOVs 857A, 860A and 860D Page 2 of5 MOV857A Close and DP Thrust Qtt
@3Th>>e
. 10rt~ Vkhry,TO Fl I
ch~Ntt '.<g~t.egg<s~slystrrls l sacr ggvatae~
thuta tya Vi T82 THCOC T29 TECOC F69.834 293 270 Lb Lb asia esr~
$3
".RtFS "Cut or~~
D/P Trace Static-Tra
)Vcft(
cIm}iT pH
.fnà C;/+~[+ ~~t~ LT960 Sto Qgg@ FOLL STjtOXE
~
4t~ h'ill',~ay~
Kj PIC MOVProgram Plan EWR 5111 Attachment K-Page 40 Revision 1
Date 2-20.98
l,
Attachment K-2 DP Thrust Traces for MOVs 857A, 8GOA and 8GOD Page3 of5 MOV857A Expanded View of Static and DP Thrust at Hard Scat
,Veitl&t) 7.3K 3.3K
~700
~4
-3 T82 THCOC 2.0K
'TeTi.Seieiiptlan.'jr DELTd-P tr'frPiaVisr 2
3 e
10 1722.862 I
11 1
1 14 Lb K>>GPSS
'stem.",'~w 3000 gt 'g os~ger r>>~ ~ s,p~,w
.~ Uket Ttoe'tiny.1+A,W
<<none>
astro?e Tjyv~l~y
@oedVjfe! Iate1Nbfj 4
250.0
,Ran y 2.0K Dftt 1.4K Coiso p~~ (~4 Kotj
<<Dela!
781.7 10.8 10.0 11.0 1'l.l 112 113 11.4 1 1.S
'I 1.0 1 1.7 E+~ Pi QpR~i Qgf!
%3a<ey re.",t
&iQ>>~ a7'k'1.3400 Seo g'an;Celeb
" MOVProgram Plan EWR 5111 Attachment K-Page 41 Revision 1
Date 2-20-98
Attachrncnt K-2 DP Thrust Traces for MOVs 857A, 8GOA and 8GOD Page 4 of5 MOVSGOA Open Static and DP Thrust OrrtattygstseaturepFgiAfy'KjneD v~
T24 THCCO fJt~
trt~Varue.
pp,crrtrrs~
-007.295
-496.335 V3 T52 THCCO LB Ph'6t vip rya~
$60a 860a sl
$2 ter Curse~r
~
p D/P ace
+~ +r Pt Koonl Stat cTra e
'Outt pj" pyttjy FyDrr pohn ran.
FS lar 1SNle at%(4 2500
~d19gll'lo~P~ cnene>
Seo gg> hS LEFT DZLIh-F 4N~~~~
erp Q@!
MOVProgram Pian EWR 5111 Attachment K-Page 42 Revision 1
Date 2-20-9S
C
L,
~ E
Attachment K-2 DP Thrust Traces for MOVs 857A, 8GOA and 8GOD Page5of5
'OV SGOD Open Static and DP Thrust vg T24 THCCO Vi T62 TECCO
-808.841 LB
-738.8U4 Lu 8600 F81 e
1
<<136l5)
D/PT a race tatic Y Cursor~
+ f4 fglliri11
<Tii>~4+9 ttOti~F llttg eauP~pA lVH Inv, ltd Aiihtrtatian gBVP5.
Seo hSIEFf DELTh.P BACH
.. &SR" MOVProgram Plan EWR 5111 Attachment K - Page 43 Revision 1
Date 2-20-98
4
Attachment K-3 Calculation of Valve Factor From EPRI Test Data for Aloyco Split Wedge Gate Valves Page 1 ofI Calcolation of Open &Close Valve Factors From EPRI Test Data for the Aloyco Split Wedge Gate Valve (Wyle Valve ¹15)
EPRI Test Open Open Open Open
~
Open Apparen Stem A Disc A DP LP Thrust PL VF Disc 232 234 236 240 242 244 246 250 0.785 0.785 0.785 0.785 0.785 0.785 0.785 0.785 13.98 89 96.56 13.98 183 191.69 13.98 275 283.4 13.98 280 275.6 13.98 278 268.9 13.98 181 190.6 13.98 93.2 99.3 13.98 245.7 250.98 423 236 0.21 542 236 0.18 705 236 0.18 669 236 0.17 759 236 0.19 600 236 0.20 492 236 0.26 696 236 0.19 N/A N/A N/A N/A N/A N/A N/A N/A Stem Diameter = 1.000 in.
Mean Seat Diameter =4.219 in.
Open VF W en DP Thrust - 0 en PL+ StemA'0 en LP Disc A*Open DP Notes: EPRI did not calculate apparent di~alues in the open direction.
Valve, pressure, and thrust data obtained from Attachment 3 of EPRI Technical Report -TR-103235-MOVPerformance Prediction Program (PPM): Engineering Analysis Report forAloyco Split Wedge Valves," Electric Power Research Institute, Palo Alto, CA, August 1996.
EPRI Test Close Close Close Close Close Apparen Stem Disc DP L
hrus P
V Disc 231 233 235 239 241 243 245 0.785 0.785 0.785 0.785
. 0.785 0.785 0.785 13.98 87 13.98 180 13.98 274 13.98 260 13.98, 275.6 13.98 181.8 13.98 93.9 94.4 590 308 0.17 187.34 912 330 0.17 282.89 2782 352 0.58 286.8 2250 374 0.45 286.2 3175 396 0.66 185.5 1333 418 0.30 98.31 862 440 0.26 0.11 0.13 0.13 0.19 0.18 0.21 0.18 Stem Diameter = 1.000 in.
Mean Seat Diameter =4.219 in.
Close VF Close DP Thrust - Close PL - StemA'Close LP Disc A*Close DP Notes: Apparent Dispel is based on Flow Isolation. Valve Factor calculated at hard Valve, pressure, and thrust data obtained from Attachment 2 of EPRI Technical Report -TR-1 03235-MOVPerformance Prediction Program (PPM): Engineering Analysis Report forAloyco Split Wedge Valves," Electric Power Research Institute, Palo Alto, CA; August 1996.
MOVProgram Plan EWR 5111 Attachment K-Page 44-Revision 1
Date 2-20-98
Attachment K-4 Calculation ofValve Factor From Indian Point 2 and Crystal River Test Data for 4" 1500 Class Aloyco Split Wedge Gate Valves and 10" 1500/f Velan Flex Wedge Gate Valve from H.B. Robinson Page 1 of 1 Indian Point 2 and Crystal River 150ff Aloyco Split Wedge Gate Valves Adjusted Corrected Thrust to Upstream Hard Seat Valve Press reach Measured Stem Pressure Corrected Orifice Valve Valve ID Size Valve T e
Class Hard Seat Static PL Diameter A
DP Area Factor 4"
Aloyco SPW 150 796 190 1.000 98.9 92.8 13.980 0.41 4"
Aloyco SPW
'50 1277 609 1.000 131 128 13.980 0.32 Hard Seat VF
= (Adj. Hard Seat Thrust-Measured PL-Stem Area'Upstream Presswe)/(DP'Orffice Area)
Indian Point 2 Test Data from Reference 18
'rystal River Test Data from Reference 19 Thrust Error Adjustments in accordance with reference 20.
H.B. Robinson 15008 Velan Flex Wedge Gate Valves Adjusted Corrected Thrust to Upstream Close Valve Press reach Measured Stem Pressure Corrected
. Orifice Valve Valve ID Size Valve T e
. Class Hard Seat Static PL Diameter A
DP Area Factor RHR-744A 10" Velan FWG 1500 6206 1282 2.500 141.4 130.3 48.710 0.67 RHR-744B 10'elan FWG 1500 4428 779 2.500 141.4 130.3 48.710 0.47 Corrected Adjusted Upstream Open Open DP Measured Stem Pressure Corrected Orifice Valve Thrust Static PL Diameter A
DP Area Factor RHR-744A, 1ty'elan FWG 1500 '765 1516
'2.500 141.4 130.3 48.710 0.62 RHR-744B 1(y'elan FWG, 1500 4562 861 2.500 141.4 130.3 48.710 0.69 Close VF
= (Adj. Hard Seat Thrust-Measured PL-Stem Area'Upstream Presswe)/(DP'Orffice Area)
Open VF
= (Adj. Open DP Thrust-Measured PL+Stem Area'Upstream Presswe)/(DP'Orffice Area)
Test Data and Error Values from References 21 and 22 MOVProgram Plan EWR 5111 Attachment K-Page 45 Revision 1
Date 2-20-98
Attachment K-5 Recommended Required Thrust Methodology and Actions Required for Long Term Resolution.
Page 1 of1 Valve Valve.
Number Size ANSI Press.
Valve Type Class Recommended Action Required Calculation for Long Term Valve Vendor Methodology Resolution 313 515 516 700 701 704A 7048 738A 7388 10 10 10"x8"x10" 1Irx8"x10" 10 10 SPW GATE DD GATE OD GATE GATE GATE DD GATE DD GATE GATE GATE 1513 1513 Aio Anchor DaAin Anchor Darling VELAN VELAN Anchor Darling Anchor Darling CRANE CRANE Standard EPRI PPM EPRI PPM
, Standard Standard EPRI PPM EPRI PPM Standard Standard None Perform PPM Perform PPM None None Perform PPM Perform PPM None None 759A 7598 813 814 3
GATE GATE GATE GATE CRANE CRANE CRANE CRANE EPRI PPM EPRI PPM Standard Standard Perform PPM Perform PPM DP Test None 841 850A 8508 1frxPxt0" 10 10 DD GATE DD GATE DO GATE Anchor Darling
= Anchor Darling Anchor Darling Standard EPRI PPM EPRI PPM None Perform PPM Perform PPM 852A 8528 6
GATE GATE VELAN VELAN EPRI PPM EPRI PPM Perform PPM Perform PPM 856 857A 8578 857C 860A 8608 860C 860D 865 871A 8718 896A 8968 3504A 3505A 4615 4616 4663 4664 4670 9629A 96298 9746 10 6"x4"x6" 6"x4"x6" Px4"x6" 1trx8"xt0" 1%x8"xt0" 10"x8"x10" 10 10 OD GATE OD GATE OD GATE DD GATE DD GATE OD GATE OO GATE DD GATE DD GATE GATE GATE SPW GATE SPW GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE 2035 Anchor Darling Anchor Darling Anchor Darling Anchor Darling Anchor Darling Anchor Darling Anchor Darling Anchor Darling Anchor Darling VELAN VELAN Al oco A
o Anchor Darling Anchor DaAing CRANE Raimondi CRANE CRANE CRANE Borg Warner BorgWarner Westinghouse Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard Standard None None None OP Test Open DP Test Open DP Test Open OP Test Open OP Test None None None None None None Close DP Test None
'one None None DP Test None DP Test None MOVProgram Plan EWR 5111 Attachment K-Page 46 Revision 1
Date 2-20-98
0
Attachment K-6 Long Term and Interim Gate Valve Factors.
Page 1 of 1 or n e mor ass or Valve Press.
Valve Valve Long Term Valve Number Valve Size Valve Type Class Valve Vendor Factor Factor Use?
Factor 313 515 516 701 704A 7048 7388 759A 7598 813 814 850A 8528 857A 8578 857C 8608 860C 860D 871A 8718 896A 8968 3504A 3505A 4615 4616 4670 9629A 9746 3 'PW GATE 150 0.50 0.50 L
Tenn 1, 11 3
DDGATE 1513 AnchorDart'PRI PPM EPRI PPM Term N/A 3
DDGATE 1513 Anchor 'PRI PPM EPRI PPM Tenn N/A 10 GATE 1500 VELAN 0.70 0.70 L
Term
- 4. 8. 10 10 'ATE 1500 VELAN 0.70 0.70 L
Term 4, 8. 10 ttrxtrX10'DGATE 300 Anchor Darf EPRI PPM EPRI PPM L
Term 6
1trxtrxt0" DD GATE 300 Anchor EPRI PPM EPRI PPM L
Tenn 8
10 GATE 150 CRANE 0.40 0.30 L
Tenn 1,2 10 GATE 150 CRANE 0.40 0.30 L
Tenn 1,2 3
GATE 150 CRANE 0.90 0.90 Interim 5
3 GATE 150 CRANE 0.90 0.90 Interim 1,5 6
GATE 150 CRANE 0.90 0.90 Intenm 5
6 GATE 150 CRANE 0.90 0.90 Lan Term 1
1irxtrxt0'OGATE 1500 Anchor Dartl N/A N/A L
Term 3
10 DO GATE 300 Anchor Oarli EPRI PPM EPRI PPM L
Tenn 8
10 DO GATE 300 Anchor Darli EPRI PPM EPRI PPM L
Tenn 6
6 GATE 1500 VELAN FROM PUTB CALO L
Tenn 9
6 GATE 1500 VELAN FROM PUTB CALO L
Tenn 9
10 DDGATE 300 Anchor N/A N/A L
Tenn 3
Px4xs'O GATE 300 Anchor Darti 0.50 0.50 L
Tenn 1
Px4x6'D GATE 300 Anchor Darling 0.50 0.50 Long Term 1
M4'xs" DDGATE 300 Anchor Darti 0.50 0.50 Interim 2
Px4"xs'D GATE 300 Anchor Darli 0.50 0.50 interim 1,2 Px4x6'O GATE 300 Anchar Darling 0.50 0.50 interim 2
Px4'xs'O GATE 300 Anchor Darlin 0.50 0.50 Interim 2
Px4'x6'O GATE 300 Anchar Darlin 0.50 0.50 interim 1.2 ItrXtrxt0'OGATE 1500 Anchor Oading N/A NIA Lcng Tenn 3
3 GATE 1500 VEtAN 0.55 0.35 Lang Tenn 1.2 3
GATE 1500 VEIAN 0.55 0.35 Long Term 1.2 1trXIrxt0" SPW GATE 150 A
N/A N/A L
Term 3
ttrxtrXIO'PWGATE 150 A
N/A N/A L
Term 3
6 GATE 600 Anchor Darli 0.50 0.50 Lcng Term 1, 2 8
GATE 600 Anchor Darli
, 0.50 0.50 Interim
- 1. 2 20 GATE 150 CRANE 0.60 0.60 L
Term 1,2 20 GATE 150 Ratmand 0.50 0.50 Long Term 1.2 6
GATE 150 CRANE 0.50 0.50 L
TeNI 1
10 GATE 150 CRANE 0.70 0.70 Long Tenn 1
10 GATE 150 CRANE 0.70 0.70 Interim 5,6 4
GATE 300 Borg Warner 0.50 0.50 Long Term 1
4 GATE 300 Borg Warner 0.90 0.90 Interim 7
3 GATE 2035 Wasti house NIA N/A L
Tenn 3
Valve Factor Basis Key 1 Dynamic Test of Subject MOV 2 Max'enln Adjusted Vshte Factor for group of Identical valves.
3 0 paid or negligbie MEDP in safety direction.
4 Max'mtxn Adjusted Valve Factor for group of similar valves.
5 As.Tested Vahe Factor forsinxlara identhal Vahre.
6 CamEd Valve Factor Data 7 Conanche Peak Vahe Factor Data 8 Nat a TRUE GL 89-10 MOV,hduded in program due to risk signiYicanca 9 MOVhas open sa/ety functkxh M'n. requ'rement is dua to PUTS.
10 IP2 snd Crystal River or Robinson Vahe Factor Test Oats MOVProgram Phn EWR 5111 Attachment K-Page 47 Revision 1
Date 2-20-98
Attachment K-7 Margin For Valve Factor Degradation (in Safety-Direction) for MOVs with Long Term Valve Factors Page1 of1 OPEN SAFETY FUNCTION VALVES Valve As-Tested Long Term Open Open Valve Open Valve VF Factor Factor Margin 857B 857B 4615
- 4616, 738A 738B 3504A 3505A 9629A 0.34 0.39 0.45 0.33 0.28 0.35 0.29 0.41 0.30 0.50 0.50 0.60 0.50 0.40 0.40 0.50 0.50 0.50 0.16 47%
0.11 28%
0.15 33%
0.17 52%
0.12 43%
0 05 14%
0.21 72%
0.09 22%
0.20 67%
CLOSE SAFETY FUNCTION VALVES As-Tested Long Term Close Close Valve Close Valve VF Valve Factor Factor Margin 4615 4616 4664 814 871A 871B
. 3504A 9629A 0.52 0.39 0.64 0.84 0.29 0.28 0.23 0.27 0.60 0.50 0.70 0.90 0.35 0.35 0.50 0.50 0.08 15%
0.11 28%
PP6 9
0.06 7%
0.06 21%
0 07 25%
0.27 117%
0 23 85%
MOVProgram Plan EWR 5111 Attachment K-Page 48 Revision 1 Date 2-20.98
Attachment K-S Packing Load Analysis - Test Data Valve ID Work Order ape Disc Stem Dia.
EPRI Smartbook Close Test Open Test Packing Load Packing Load Packing Load Packing Load 0313 0515 0516 0704B 0738A 0738B 0738B 0749B 0759A 0759B 0813 0814 0850A 0856 0857A 19601738 19402869 19402867 19221563 19221443 19504231 19221441 19321381 19321386 19321389 19601477 19221433 19321364 19521366 19504238 GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE SP DD DD DD SW SW SW FW FW FW FW DD DD DD 0.875 0.75 0.75 1.375 1.625 1.625 1.625 0.625 0.625 0.625 0.875 0.875 1.5 1.5 1.375 1000 1000 1000 1500 2500 2500 2500 1000
~
1000 1000 1000 1000 1500 1500 1500 878 627 1000 1000 1500 532 514 815 2500 1000 1000 1000 1000 1000 1500 1500 1500 993 206 23 46 194 186 702 528 439 2500 816 2500 843 547 568 513 1086 982 935 846 195 23 57 319 240 1170 455 247 M/VProgram Plan EWR 5111 Page 49 Revision 1 Date 2-20-98
Attachment K-8 Packing Load Analysis - Test Data Valve ID Work Order Type Disc Stem Die EPRI Smartbook Close Test Open Test Packing Load Packing Load Packing Load Packing Load 0857A 0857B 0857B 0857C 0857C 0860A 0860A 0860B 0860C 0860D 0865 0871B 0896A 0896B 1815B 19604163 19504240 19604162 19604161 19504242 19221439 19400531 19221438 19221437 19400532
. 19321368 19221428 19240743 19504243 19241158 GATE GATE
~ GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE DD DD DD DD DD DD DD DD DD DD DD FW SP SP SP 1.375 1.375 1.375 1.375 1.375 1.375 1.375 1.375 1.375 1.375 2.125 1.125 1.25 1.25 1500 1500 1500 1500
- 1500 1500 1500 1500 1500 1500 2500 1500 1500 1500 1000 1500 1500 1500 1500 1500 772 772 924 634 806 2500 1500 1500 1500 1000 726 458 568 440 421 706 772 924 634 806 620 1101 1173 403 569 637 498 469 330 513 700 699 804 605 709 810 1192 1173 459 628 MOV Program Plan EWR 5111 Page 50 Revision 1 Date 2-20-98
Attachment K-8 Packing Load Analysis - Test Data Valve ID Work Order T3'pe Disc Stem Die EPRI Smartbook Close Test Open Test Packing Load Packing Load Packing Load Packing Load 3505A 3505A 4615 4616 4616 4663 4663 4664 4664 4670 9629A 9629A 9629B 9746 9746 19600234 19604599 19504250 19602930 19221506 19400660 19504251 19221519
'9504253 19502206 19504257 19221943 19221944 19400530 19241156 GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE GATE FW FW SW FW FW FW FW FW FW FW FW FW FW 1.375 1.375 2.25 1.12 1.12 1.625 1.625 1.375 1.125 1.125 1500 1500 2500 2500 2500 1500 1500 2500 2500 1500 1000 1000 1000 1500 1500 1500 1445 1500 304 2500 374 2500 1200 1200 2500 2500 1500 1000 1000 1000 1500 1500 740 1123 741 1350 546 344 623 642 369 609 609 2500 1593 1445 810 1405 1817 1296 1200 718 1350 477 605 220 620 620 MOV Program Plan EWR 5111 Page 51 Revision 1 Date 2-20-98
Attachment K-9 Packing Load Analysis Valve ID EPRI Packing Load Tested Close Packing Load Tested Open Packing Load
[Close / EPRg PL Ratio
[Open / EPRq PL Ratio 0313 0515 0516 0704B 0738A 0738B 0738B 0749B 0759A 0759B 0813 0814 0850A 0856 0857A 0857A 0857B 1000 1000 1000 1500 2500 2500 2500 1000 1000 1000 1000 1000 1500 1500 1500 1500 1500 627 532 514 815 816 843 993 206 23 46 194 186 702 528 439 726 458 547 568 513 1086 982 935 846 195 23 57 319 240 1170 455 247 637 498 0.627 0.532 0.514 0.543 0.326
'.337 0.397 0.206 0.023 0.046 0.194 0.186 0.468 0.352 0.293 0.484 0.305 0.547 0.568 0.513 0.724 0.393 0.374 0.338 0.195 0.023 0.057 0.319 0.240 0.780 0.303 0.165 0.425 0.332 MOV Program Plan EWR 5111 Page 52 Revision 1 Date 2-20-98
Attachment K-9 Packing Load Analysis Valve ID EPRI Packing Load Tested Close Packing Load Tested Open Packing Load
[Close / EPRIJ PL Ratio
[Open / EPRI]
PL Ratio 0857B 0857C 0857C 0860A 0860A 0860B 0860C 0860D 0865 0871B 0896A 0896B 1815B 3505A 3505A 4615 4616 1500 1500 1500 1500 1500 1500 1500 1500 2500 1500 1500 1500 1000 1500 1500 2500 2500 568 440 421 706 772 924 634 806 620 1101 1173 403 569 1445 304 374 1593 469 330 513 700 699 804 605 709 810 1192 1173 459 628 1445 810 1405 1817 0.379 0.293 0.281 0.471 0.515 0.616 0.423 0.537 0.248 0.734 0.782 0.269 0.569 0.963 0.203 0.150 0.637 0.313 0.220 0.342 0.467 0.466 0.536 0.403 0.473 0.324 0.795 0.782 0.306 0.628 0.963 0.540 0.562 0.727 MOV Program Plan EWR 5111 Page 53 Revision 1 Date 2-20-98
Attachment K-9 Packing Load Analysis Valve ID EPRI Packing Load Tested Close Packing Load Tested Open Packing Load
[Close / EPRIJ PL Ratio
[Open / EPRIJ PL Ratio 4616 4663 4663 4664 4664 4670 9629A 9629A 9629B 9746 9746 2500 1500 1500 2500 2500 1500 1000 1000 1000 1500 1500 740 1123 741 1350 546 344
-623 642 369 609 609 1296 1200 718 1350 477 605 220 620 620 0.296 0.749 0.494 0.540 0.218 0.229 0.623 0.642 0.369 0.406 0.406 0.518 0.800 0.479 0.540 0.477 0.605 0.220 0.413 0.413 Statistical Analysis ofPacking Load Ratios Average of
[Close / EPRI]
PL Ratio 0.419 Standard Deviation of
[Close / EPRg PL Ratio 0.200 Average of
[Open / EPRIj PL Ratio 0.456 Standard Deviation of
[Open / EPRI]
PL Ratio 0.206 MOVProgram Plan EWR 5111 Page 54 Revision 1 Date 2-20-98
I
/
Pg