ML20211D035
| ML20211D035 | |
| Person / Time | |
|---|---|
| Site: | Oyster Creek |
| Issue date: | 06/02/1986 |
| From: | NRC |
| To: | NRC |
| References | |
| NUDOCS 8606120488 | |
| Download: ML20211D035 (23) | |
Text
__ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _
, [sa nay'o . UNITED STATES
' ,n NUCLEAR REGULATORY COMMISSION e ' 3 .c. ,
, $ WASHINGTON, D. C. 20555 l
% ,((, J M2 1996 Docket No. 50-219 LICENSEES: GPU Nuclear Corporation Jersey Central Power and Light Company FACILITY: Oyster Creek Nuclear Generating Station
SUBJECT:
APRIL 3, 1986, MEETING WITH GPU NUCLEAR CORPORATION (GPUN) TO DISCUSS ITS REQUEST TO CANCEL THE REPLACEMENT OF THE LARGE CONTAINMENT PURGE AND VENT VALVES On Thursday, April 3, 1986, a meeting was held at NRC, Bethesda, Maryland with GPUN, the licensee, on the licensee's request to cancel its commitment to install large containment purge and ventilation isolation valves in the Cycle 11 Refueling (Cycle 11R) outage. The request was in the licensee's letter dated September 24, 1985. The staff's acceptance of the valves, that the licensee previously proposed to replace the existing valves with, is in the staff's Safety Evaluation (SE) dated January 21, 1986.
Attachment 1 is the list of individuals that attended the meeting. Attachment 2 is the material handed out by the licensee in the meeting for its presentation. This material is discussed further in these meeting minutes.
Attachment 3 is a copy of the staff's Request for Additional Information (RAI) dated January 27, 1986, on this subject. Attachment 4 is material submitted by licensee to the staff after the meeting to provide the information requested by the staff during the meeting. The following is a summary of the significant items discussed and the actions, if any, taken or proposed.
The agenda for this meeting is in Attachment 2. The licensee presented a history of its commitment to replace the existing valves and its request to cancel this comitment. This history and a drawing of the valves in the containment purge and vent system which was also presented by the licensee in the meeting are in Attachment 2.
Attachment 2 has the following material presented by the licensee: meeting agenda, history of its commitment, drawing of the containment purge and vent valves, letter from the Center Line Company on the 18 inch Series LTM valves installed at Oyster Creek (9 pages) and letter from Fisher Company on the dynamic torque sizing coefficient data on Continental valves installed at Oyster Creek (38 pages including 8 attachments).
l This meeting was requested by the licensee in the meeting of February 20, 1986, with the staff. It is the licensee's response to the staff's request for additional information (RAI) on this subject of January 27, 1986. The meeting sumary is written in terms of the discussion on each of the five areas identified on page 2 of the RAI.
8606120488 DR 860602 ADOCK 05000219 PDR
C 2
1.0 Valve Installation Configuration The licensee stated that there are elbows upstream of the valves and it assumed a factor of 3, the worst case, for all open positions of the valves in the calculations of torque. This is stated in the licensee's September 24, 1985, submittal. The licensee showed the staff isometric drawings of the location of the valves.
The staff stated that this response is sufficient to answer the question on this item in the RAI.
2.0 Dynamic Torque Analysis The licensee handed out letters from the Center Line and Fisher Companies.
Those letters are in Attachment 2. These letters discuss the torque coefficients and the dynamic torque analysis for the valves at Oyster Creek.
In its discussion on its dynamic torque analysis, the licensee referred to a paper on the " Effects of Fluid Compressibility on Torque in Butterfly Valves" by Floyd P. Harthum of Fisher Coernan Company. This is in attachment 2 to the letter to the licensee from Fisher Company. A copy of this letter is in Attachment 2 to this meeting summary. The licensee stated that the conclusion of this paper was that the Fisher Company had developed analytical equations for valve dynamic torque which correlated well with its experimental test data.
The staff stated that it was important that the shape of the valve disc for the valve tested by the valve manufacturer be similar to the shape of the disc for the valves at Oyster Creek. The shape of the disc is important to the torque coefficients curves. The licensee stated that it would provide the shape of the disc for the Oyster Creek valves.
The licensee stated that the test reports on the tests run by Fisher Company are considered proprietary by Fisher and are not available from the company to be submitted to the staff. The reports would be available to the staff for review if the staff would visit Fisher. The staff stated that it would review the letter from Fisher presented here by the licensee and decide whether a trip to the company was necessary for the staff to complete its evaluation.
The licensee stated that Center Line also considers its test reports proprietary but it will provide a copy of the report that would then be submitted by the licensee to the staff as a proprietary report. This would be pursuant to 10 CFR 2.790. The staff stated it will treat this report as proprietary or return the report to the licensee. The staff requested that the licensee request this report from Center Line and submit it to the staff as soon as possible.
3.0 Actuator Torque Margin The licensee stated that it will provide the valve spring torque at different valve opening angles in a future submittal.
o - _ _ - _ . - _ ._
3 4.0 Dynamic Torque Analysis The licensee stated that it used peak pressure from the design basis accidents in its stress analysis of the critical parts of the valves. This analysis is in TDR 266 revision 1 which was submitted in the licensee's letter dated September 24, 1985. The licensee stated that it will provide a stress analysis of the valve interfacing hardware and actuator in a future submittal.
The licensee stated that it will clarify the list of valves in Attachment 3.
This is the list of the valves at Oyster Creek and the valve manufacturer from the licensee. The list includes possible manufacturers other than Center Line and Fisher. The letter from Fisher to the licensee in Attachment 2 refers to the Continental valves in the list. The licensee will explain in a future submittal which test data applies to the Continental and Rockwell valves listed in Attachment 3.
5.0 Seismic Qualification of Valves The licensee stated that the seismic design criteria for the Oyster Creek station is discussed in Section 3.7 of the Updated Final Safety Analysis Report (FSAR) for Oyster Creek. This seismic criteria came out of the review of Oyster Creek in the staff's Systematic Evaluation Program. The licensee stated that the valves meet the Oyster Creek seismic design criteria and its basis for this conclusion is stated in the TDR 266, revision 1, submitted in its letter dated September 24, 1985.
6.0 Dynamic Torque Coefficients This item was discussed in the previous discussions held on the above items.
7.0 Plant Operation With Containment Purge / Vent Valves Open The licensee explained that these containment purge / vent valves are open for refueling, shutdown and restart and normally closed during plant operation.
The valves are not frequently open during the plant operating conditions above cold shutdown and then only for inerting or de-inerting the containment or monthly surveillance tests of torus-to-drywell vacuum breakers. The inerted j containment is part of the combustible gas control for Oyster Creek during an accident. Technical Specification (TS) 3.5.A.6 limits the use of these valves to within 24 hours2.777778e-4 days <br />0.00667 hours <br />3.968254e-5 weeks <br />9.132e-6 months <br /> after the reactor mode selector switch is in the run mode (for inerting) and to within 24 hours2.777778e-4 days <br />0.00667 hours <br />3.968254e-5 weeks <br />9.132e-6 months <br /> prior to shutdown (for deinerting).
l The licensee explained that it should not inert the containment and shut these valves in the restart mode because there are surveillances required by TS
! being conducted in the containment during restart. Some of these surveillances are at the reactor operating pressure. These surveillances require people in the containment during restart. If the containment were l
inerted during the surveillances, there would be a risk to the individuals because of the low oxygen concentration.
l L_ .
4 The staff requested a chart of the sequence of events during startup and shutdown showing the following: (1) when inerting containment begins and ends, (2) when de-inerting begins and ends (3) reactor pressure and temperature, and (4) the different reactor modes. The information will help the staff understand when these valves are open during restart and shutdown.
The licensee stated it is revising plant procedures so that these valves are not opened during the monthly surveillance on the torus-to-drywell vacuum breakers. This was discussed on page 4 of the licensee's letter of September 24, 1985. This would reduce the time when these valves are open and the reactor is at high temperature and pressure to only when the containment is being inerted or de-inerted as explained above. This is being done voluntarily by the licensee.
8.0 Summary The following is the additional information needed by the staff to complete its evaluation and to be provided by the licensee:
- 1. Clarify the list of valves and valve manufacturers in Attachment 3 and explain which valve test data (i.e., Fisher or Center Line) applies to the Continental and Rockwell valves.
- 2. Submit, pursuant to 10 CFR 2.790, the proprietary test report from Center Line. The licensee will have to request this report from Center Line.
- 3. Provide the relationship including the shape of the valves disc between the Center Line and Fisher test valves and the Oyster Creek valves.
- 4. Provide the spring torque at different valve opening angles for the Oyster Creek valves.
- 5. Provide the stress analysis of the interfacing hardware and actuator for the Oyster Creek valves. It is sufficient for the licensee to verify that the actuators have sufficient capacity to operate the Oyster Creek valves.
- 6. Provide a chart of the sequence of events during startup and shutdown.
The staff agreed to review the test data in the Fisher letter to the licensee in Attachment 2. The staff will determine if it is necessary to visit Fisher Company to review the proprietary test reports.
9.0 Post Meeting Sumary The licensee has provided items 1, 5 and 6 in the meeting with the staff on April 23, 1986, at the licensees headquarters. The staff's meeting summary for this meeting with this information attached is dated May 22, 1986. The licensee provided item 3 for only the Fisher valves and item 4 for both the Fisher and Center Line valves to the staff in a telecopy. This material is in Attachment 4. The Center Line proprietary test report has been requested by the licensee and will be submitted as soon as it is received by the licensee.
Distribution: w/ enclosures w/o enclosures
C. Jamerson*
E. Jordan
- B. Grimes
- ACRS (10) .
cc: Licensee Service List s
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DATE iS/ d /86 i 5/ 15 /86 i 6/ 2. /86i ?
0FFICIAL RECORD COPY t
e MEETING
SUMMARY
DISTRIBUTION Licensee: GPU Nuclear Corporation Jersey Central Power and Light Company
- Copies also sent to those people on service (cc) list for subject plant (s).
f ocketFilh y-L PDR BWD-1 Rdg JZwolinski JDonohew OELD EJordan BGrimes ACRS-10 JLombardo Glainas RBernero RLaGrange BDLiaw l
l 1
J Oyster Creek Nuclear Generating Station cc:
Ernest L. Blake, Jr. Resident Inspector Shaw, Pittman, Potts and Trowbridge c/o ll.S. NRC 1800 M Street, N.W.
Washington, D.C. 20036 Post Office Box 445 Forked River, New Jersey 08731 J.B. Liberman, Esquire Commissioner Bishop, Liberman, Cook, et al. New Jersey Department of Energy 1155 Avenue of the Americas 101 Commerce Street New York, New York 10036 Newark, New Jersey 07102 Euoene Fisher, Assistant Director Regional Administrator, Region I Division of Environmental Quality U.S. Nuclear Regulatory Commission Department of Environmental 631 Park Avenue Protection King of Prussia, Pennsylvania 19406 380 Scotc; Road Trenton, New Jersey 08628 BWR Licensing Manager Mr. P. B. Fiedler GPU Nuclear 100 Interpace Parkway Vice President & Director Oyster Creek Nuclear Generating Parsippany, New Jersey 07054 Station Deputy Attorney General Post Office Box 388 Forked River, New Jersey 08731 State of New Jersey Department of Law and Public Safety 36 West State Street - CN 112 Trenton, New Jersey 08625 Mayor Lacey Township 818 West Lacey Road I
Forked River, New Jersey 08731 D. G. Holland Licensing Manager Oyster Creek Nuclear Generating Station Post Office Box 388 Forked River, New Jersey 08731 1
d ATTACHMENT 1 MEETING WITH GPU NUCLEAR CORPORATION (GPUN)
TO DISCUSS CANCELLATION OF THE REPLACEMENT OF THE LARGE CONTAINMENT PURGE / VENT VALVES APRIL 3, 1986 NAME ORGANIZATION J. Donohew NRC/NRR/ DBL J. Lombardo NRC/NRR/ DBL R. Green State of New Jersey
- M. Laggart GPUN J. Lachenmeyer GPUN S. Miller GPUN A. Rochino GPUN B. Miller BNL**
R. Hoder BNL Department of Radiation Protection
- Brookhaven National Laboratory, DOE
f ATTACHMENT 2 Agenda o Valve Installation Configuration - A. P. Rochino, S. S. Miller o Dynamic Torque Analysis - A. P. Rochino o Actuator Torque Margin - A. P. Rochino o Seismic Qualification of Valves - J. D. Lachenmayer o Containment Atmospheric Release - A. P. Rochino o Valve Closure Times Greater Than 15 Sec. - A. P. Rochino, S. S. Miller o Dynamic Torque Coefficients - S. S. Miller o Summation - M. W. Laggart 4
3147f e
Oyster Creek Nuclear Generating Station Multi-Plant Action B-24 GPUN - NRC Meeting April 3,1986
Subject:
Cancellation of GPUN commitment to install new containment vent and purge valves at the Oyster Creek Nuclear Generating Station.
Purpose of Meeting: To present GPUN's efforts to date relating to NRC's request for additional information of January 21, 1986 and January 27, 1986.
History: NRC issued B-24 concerns on November 29, 1978.
GPUN committed to limit the opening of the existing valves to 30*
on December 17, 1979.
GPUN committed to install new vent and purge valves on July 31, 1980.
GPUN requested installation deferral on August 27,1981 and provided Technical Data Report (TOR) No. 266 which demonstrated the ability of the valves to close against LOCA loads.
GPUN and NRC held a meeting on February 13, 1985 to discuss, among other items, B-24 and GPUN's TDR No. 266.
GPUN requested cancellation of valve replacement on September 24, 1985 and provided a revised TDR based on NRC comments of February 13, 1985.
NRC requested additional information via letters dated January 21, 1986 and January 27, 1986.
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January 31, 1986 GPU Nuclear 100 Interpace Parkway Parsippany, NJ 07054 Attn Jim Correa
Dear Sir:
This letter is in response to our phone conversation 1-20-86 in reference to the 18" Series LTM valve installed at Oyster Creek in 1976. As you requested I am verifying the Ct (coefficient of dynamic torque) values ycu obtained from Jerry Nichols and Bill Generke in 1981.
The enclosed graph (C9 vs T/D) was derived by Colorado State University from flow tests on valves from various manufacturers.
CD is coefficient of discharge (similar to Cv) and T/D is the ratio of disc thickness to valve I.D. The enclosed chart agrees with values you gave ce over the phone. Ct was calculated from the CD values from the graph using the stated equation. This equation was derived by Center Line from flow tests of our valves at Colorado State University. All of this data is proprietary and should be given only to cyster Creek and GPU personnel.
I hope that this will answer Oyster Creek's questions and if I may be of further assistance, please call me.
/
Sine} rely, //
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R.L. Alger Associate Engineer RI.A/db A UNIT OF MARK CONTROLS CORPORATION r
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. FISHER Memorandum ,
o,. To: Kent;RuTnmelhart' From: John Dresser
/E cc: Floyd Harthun Gene Taylor Dan Button Gary Icenogle cai : March 12, 1986 Floyd Jury sueject: Torque Coefficient Basis for Oyster Creek Purge and Vent Valves QER: 860N21 Ref. a. Letter, GPU Nuclear (Correa) to Fisher Controls Co. (Rummelhart) dated 1-24-86. Reference No. MC-86-3560; same subject.
- b. Continental Equipment Co. S.0. P62604 8" Class 150 Model 9100 with 656-60 Actuator.
Continental Equipment Co. Serial No. 103160-103163, Agent 1-24690,
- c. "Contiinental Division CC No. 4E27551 12" Class 125 Model 9500 with 656-60 Actuator.
Continental Division Serial No. BF200233-BF200234, Agent 003-59920.
- d. NRC NUREG/CR-4141 (EGG-2374).
" Containment Purge and Vent Valve Test Program Final Report",
by Steele and Watkins, Idaho National Engineering Laboratory. September 1985. The following response is provided to the GPU Nuclear request for dynamic torque sizing coefficient data per the GPU Nuclear letter of 1-24-86 (Reference "a" - see copy in Attachment 1)
- 1. We_ concur with the dynamic torque coefficients cited in the GPU Nuclear letter, with one exception which is believed to be. a typographical Er~ror. Be~e the list, restateTis follows below, with the corrected value circled:
Valve Opening 8" Type 9100 12" Type 9500 Angle Conventional Disc
- Fishtail Disc
- Degrees Aspect Ratio 4:1 Aspect Ratio 5:1 10* , 2.1 12.1 20 4.3 20.7 30* i 7.0 20.7 40 15.0 21.7 50 27.0 .
60* 51.0 105.0 70* 103.0 219.0 80* 163.0 259.0
- Note: Both these conventional and fishtail discs are symmetrical; i.e.,
there is no " shaft side" or " flat side," since both sides of the discs are the same configuration. W13-25/1
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- 2. The use'of these. dynamic torque factors should be clarified as followst [ .,: '
-d These A'ct'A ors (known'as C" factors) are to be multiplied by the actua "'
~
~
pressgef drop (AP act) or by the effective pressure drop (AP eff) . applicable for each angle of opening, using whichever aP value is least.; This wil'1 give the dynamic torque in inch-pounds. For the total torque at open angles, additional factors ("A" and "B") should be added to account for bearing and packing friction, respectively. See Attachment 4 for a further explanation of this procedure, and for the method of
), determining "aP eff" based on disc type, type of fluid involved, and angle of disc opening. It should be observed that the upstream pressure (P1 ) is entered as psi absolute, not psi Lac e. In this case, the appropriate "A" factor values are: for the EF valves, "1.47"; for the 12" val ves, "4.13". The "B" factor values at open angles are: for the 8" valves, "100"; for the 12" valves, "140".
NOTE: The dynamic torque coefficients listed under Paragraph 1 above and in the referenced GPU Nuclear letter already account for the valve diametgr; therefore, they should not be multiplied by a DJ term. Instead they should be used as-is,
- multiplied only by the appropriate AP,.to give -
dynamic torque in inch-pounds.
- 3. The basis for the subject dynamic torque ("C") factors is provided as follows:
- a. Dynamic torque factors to be used in butterfly valve sizing were develooed from_ test _ data obt31 A gd from modeh,yith..sjnilat_ disc c_onfiourationLand flw charactechtici. The dimensionless aspect ratio (defined as the ratio of the disc diameter to the maximum disc thickness) was judged to be a significant parameter for evaluation of dynamic torques at various opening angles. Therefore, a series of flow tests were_ conducted wittL amoup_gf 4" anj._6" bu tt_erf_ly_Jalve_Judeh_sonst ructed with _various_. asper _t_rati os ,
tanging from .2:1 to.14:1 (such as 3:1, 4:1, 5:1, 8:1, 11:1, and 14:1),_in.various_ disc. configurations (conventional, offset, Ifishtail). The tests were conducted _using water: following the Fluid Controls Institute (FCI) specifications for test arrangement p and conduct, per FCI paper 58-2 (see Attachment 5). 3
- b. _Tjle_)Asjt1 followed by Fisher in using incompressible (water) flow lmodel tests to establish l_a_tge. diameterSl_ves.jn dynamic torque compr_essiblellow._ servicecoefficients _ applicable
_.jl oresented in _t ! 'the_lSA_Iransactions_ article-provided_as Attachment 2 ("Effect of
' Fluid Compressibility on Torque in Butterfly Valves" by Floyd P.
Harthun, ISA Trans. Vol. 8, No. 4, 1969). 1 l (1) On page 282 of the referenced paper, a relationship is developed l relating torque to the nominal valve diameter and pressure drop, for incompressible flow conditions, namely: TO " X 103aP (Eqn. 10-B) W13-25/2
)
Page 3
<. : ~ ' . . % ,. 5 ./
March 12,1986 . tgr. - _%,t .. ep j S in which K1 is a dimensionless torque coefficient for incompressible iflow.. It may be noted that this relationship applies to various valve sizes, as well as to various pressure drops. The K1 value is determined by test (using water), for various rotation angles as shown in Figure 1, Page 283 of the ISA paper.
).
(2) The referenced ISA paper then considers dynamic torques developed during compressible fluid flow. In this case, the actual torque is n3_.langer._lbtear.with__ respect to A9 _(incompressible flow torque has a linear relationship with respect to pressure drop across the valve up to the choked flow condition); for convenience, however, a similar relationship is developed, using a ape factor as follows: TD " K 103aPg (Eqn. 25) This relationship (Eqn. 25) permits determination of dynamic torques for various valve sizes under conditions of compressible flow, providing K1 and ape are determined. For the same pressure drop conditions, it is noted that the dynamic torque is directly related to the cube of the disc diameter. This is l consistent with the dynamic torque scaling relationship D3 T shown in NUREG CR/4141 (Ref. d) for 2=(32) T1 __01 __ i developinq full scale toraue values (Td f rom small_ scale model l tests, based on the same pressure conditions and assuming i similar disc configurations. > (3) Figure 5, Page 284 summarizes the rationale presented in the ISA paper; this figure shows a plot of calculated and experimental torque values for various pressure drops and flow conditions. The_Straig__t h line labeled " Incompressible._Elow" is a representation of the relationship: TD"K1 D3aP, while the cur _ved line represents conDress_it)le flow.lorque_va.lllPs, following the relationship: TD = K1, D3 ape. Test data for compressible flow is also plotted, showing close agreement with the calculated values. (4) Reference is made to Figures 6, 7, and 8, page 285 of the ISA paper showing a comparison of test data and calculated data for various angles of rotation. Close agreement with ape torque values for compressible flow is indicated. [ Note: There are a few typographical errors in the ISA document figures: the aP/P1 values given in the captions to Figure 7 should be 0.155 and in the caption to Figure 8 should be 0_.466.] W13-25/3
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- l g . t 4 Applicatfon of thi conclusions from the ISA paper are presented in M Attachmitt 3, Figures 1 and 2: " Torque-Pressure Drop Relationships Used in Dynamfc Torque Coefficient Selection", which is a representation of the Figure 5 curves from the ISA paper. This shows how the torque values for compressible flow are conservatively determined and related to incompressible flow torques. ILshou11Lbeloted that the compressible flow curve reaches __altitical flow _condLt_ign_4t_large_aP values, resulting i __in a mulgun_tEque_yalue (T,-), which _cannot _ be exceeded. regardless of AN l A rge AP hacomen
- a. A APeff value is obtained from the Fisher sizing table (shown in .
Attachment 4) based on the absolute inlet pressure value, type of I disc, and flowing fluid. I l
- b. If the actual AP is greater than APe rf, then the APerf value (labeled APc in Figure 1, Attachment 3) is used, corresponding to Tc (the maximum possible torque). This is conservative, predicting a higher torque than is actually present.
- c. If the actual AP is less than APerf, then APact is used, which predicts a more conservative (greater) torque, but less than Tc l (see Figure 2, Attachment 3). '
- d. An actuator is selected, based on the predicted maximum torque req ui rements. The actuator must be able to provide the necessary torque to'open, close, or maintain the valve in position.
Note: The APerf value (not to be confused with ape used in the ISA paper) is based on critical flow conditions which will produce the maximum possible dynamic torque. (Tc)-
- 5. Capacity and Torque curves obtained from a typical model test with a aspect ratio (5:1) similar to that for the subject 12" valves are enclosed (Attachment 6) to illustrate the method and general shape of the curves for Type 9500 butterfly valves with f.ishtai.l. Jigs. Note that when the dynamic torque is positive, flow tends to close the valve.
Figure 2, Attachment 6 shows that this valve is flow-closed throughout all angles of interest.
- 6. A corresponding typical torque curve for 4" model tests applicable to the Type 9100 butterfly valves with conventional discs is provided as Attachment 7. Only the CEC 0 4" CL 2HP curve applies (Continental Equipment Co. 4" Class 2 Heavy Pattern), for a P1 of 100 psi and a
! AP of 10 psid; the aspect ratio for this disc was 3.5:1, not far from l that for the subject 8" valves (4:1). Again, note that the dynamic ! torque was positive for all open angles, tending to close the valve.
- 7. Summarizing the previous statements, dynamic torque sizing equations (Egn.10-B ar.d Eqn. 25) were developed relating torque to the nominal valve disc diameter, pressure drop and a constant K1 . Through testing of various valve nodels, data was obtained for K1 at incremental angles of opening. Scaling,nethods were then used to obtain dynamic torque f actors applicable for larger size valves. ,
1 W13-25/4 w ise - -- -
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- 8. Tjle_Efstfer Test.3.eports describing _the butterf_ly_Jal.ve modeltesti_inf.
detat.TRthat form the b_asjl_f_of_.the. dynamic torque. factors)Ee_ considered to _be prooriet ACy.;__h. owe,yer m .thes.e. reports are available fot. re. view _at._ thelisher__ Controls _.I.nternational, Inc. premises at Marshalltown, . Iowa, proyiding appropr.i. ate . advance notification and arrangements. are_made. It should be borne in mind that there are a series of test reports involved, covering wide range of valve types, pressures, and disc
> aspect ratios. Ihara is na eing b epnet =u2ilahAthat summari7ac all.
this_ data,__at the present-t h
- 9. The development of the dynamic torque coefficient values for different valve sizes and configurations was based on scaling factors determined in the model tests. The coef ficients also reflect allowances for uncertainties and variations and have been adjusted for consistency from type to type and size-to-size. All these torque coefficient value adjustments have generally been in a conservative direction (increase in coef ficient value). These dynamic sizing coefficients for open-angle positions have been in use for over 13 years, in many appli-cations besides nuclear power plants, with no known instances of inadequacy for the many valves of this type built and placed in service over this period.
- 10. It is Fisher's position that the torque coefficients developed generally have a substantial degree of conservatism (dynamic torque values calculated are usually well in excess of the actual dynamic torque values experienced). To illustrate this, the following comparisons are made, based on the particular configurations of interest:
- a. For the 8" Type 9100, Conventional Disc, AR4:1 Reference is made to dynamic torque test data for a CEC 0 8" C12 HP valve cited in Problem 1340, Report 1 (air test). (See Attachment 8).
This 8" test valve construction has an aspect ratio of 4.57:1 with a conventional disc, so it is very similar in construction to the subject 8" purge and vent valves. For: Pi = 100 psig (114.7 psia) AP = 5 psi For gas, min APeff = 0.140 Pi = 16.0 psi (at 80' open), so not critical flow, use APACT = 5 psi (least) Angle Calculated Values Test Values of "C" aPACT CAPACT Air Opening Factor psi in-lb in-lb 10 2.1 5 10.5 16 20 4.3 5 21.5 18 30 7.0 5 35.5 22 40* 15.0 5 75.0 44 50* 27.0 5 135.0 98 60 51.0 5 225.0 224 70' 103.0 5 515.0 420 80 163.0 5 815.0 440 W13-25/5
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March 12,1986
-c J .is apparent that the calculated dynamic torque values (based on-t stated "C" factors) are well in excess of the observed test values for all angles except at 10*, which is not of significance in considering actuator sizing.
- b. For the 12" Type 9500, Fishtail Disc, AR5:1
~.
Reference is made again to the dynamic torque test data for a 4" Fishtail Disc Valve model, with an aspect ratio of 5:1 (See Figure 44, Problem 13408, Report 5 provided as Attachment 6). This was a water test, under the following conditions: P1 = 100 psig (114.7 psia) AP = 5 psi (not critical flow) Plot of opening angle vs "K" value Wnere: T(10)3 =x (See Eqn. 10-B, ISA paper, Attachment 2) 03(aP) and since Dynamic Torque (T) = C'(AP) in-lb.. Substituting for "T" C'(AP) (10)3 = C' (10)3 K= Dd (AP) 03 Rearranging: KD3 =C' = Derived Dynamic Torque 1000 Coefficient Relating the 4" test model to the 12" valves: Let: 01 = 4" = Nominal Dianeter of Test Model D2 = 12" = Nominal Diameter of 12" valve C1' = Derived Torque Coeff for 4" Test Model C2' = Derived Torque Coeff. for 12" valve K = Factor read from test chart for each opening angle. (From Fig. 44, Rep. 5, Prob.13408). Applying the Scaling Ratio per Section 3.b (2) of this memo 3 ' T2 = C2'(aP) = D2 = C2 5 8 C1 (aP) D1 3 C1' l W13-8/6
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March 12,1986
' ~
) Then C2a = D23 C1' = Derived Dynamic Torque
-y factor from test, scaled 01 for 12" size.
I 1 j, Angle K C Fapor , C2 F Sizing Table of Factor (02 3) C1 actor.8
" KD1 I Dynamic Torque l
Opening (from Tast) Factor "C"
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10* -3 -0.19 -5.18 12.1 20* 0 0 - 20.7 30* 0 0 - 20.7 40* +3 0.19 5.18 21.7 50* +9 0.58 15.55 48.4 60* +35 2.54 60.48 105 70* +102 6.53 176.3 219 80* +153 9.79 264.4 259 Thus, it is noted that the sizing table dynamic torque ("C") factors are well in excess of the corresponding factors ("C2 ') derived from the test data for all angles except at 80* open where there is close agreement (within 2%). This illustrates the general conservatism of the dynamic torque factors provided in the sizing tables.
- 11. This constitutes the information we have for response to the GPU Nuclear i nqui ry. Please advise if there are further specific questions for resolution.
Dohn Dresser , Engineering Qualification and Analysis Group W13-25/7 O w.*
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Enclosures / , _ Attachment 1: GPU Nuclear letter of 1-24-86 (MC-86-3560) Attachment 2: ISA Transactions Vol. 8, No. 4, 1969 "Ef fects of Fluid Compressibility on Torque in
;. Butterfly Valves" by Floyd P. Harthun.
Attachment 3: " Torque-Pressure drop Relationship Used in -Butterfly Valve Dynamic Torque Coefficient Selection." - Attachment 4: CFG 408-10, Page 1, January 1973 s.- -
"BFV Torque Determination;" --
Attachment 5: FCI 58-2. " Recommended Voluntary Standards for Measurement Procedure for Determining Control Valve Flow Capacity."- - Attachment 6: Fisher Lab Report Excerpt Problem 13408, Report 5, Figures 2,11, and 44. Attachment 7: Fisher Lab Report Excerpt. 2 - Problem 13408, Report 2ip#igurea.imanc : Attachment 8: Fisher Lab Report Excerpts. Problem 1340B, Report 2, Figure 2 Problem ~1340, Report 1, Figure - 5 W13-25/8 e-
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to Fisher Controls Co. (Rummelhart) dated 1-24-86 Ref. No.--MC-86-3560 .- -
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(201)263-6500 TELEX 136-482 Writer's Direct Dial Number: ) January 24 MC-86-3560, 1986 Mr. Kent Rumelhart Fisher Controls Company Marshalltown, Iowa 50158
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Subject:
Continental Equipment Co. S.O. P62604 8" Class 150 Model 9100 with 656-60 Actuator Continental Equipment Co. Serial No. 103160-103163 Agent 1-24690 -- ~ Continental Division CC.No. 4E27551 12" Class 125 Model 9500 with 656-60 Actuator Continental Division Serial. No. BF2002.33-BF200234 Agent Order No. 003 59920 = -- -
Dear Mr. Rumelhart:
The purpose of this letter is to document our conversation of January 22, 1986 and to formally request data to allow GPUN to qualify its valves for continued service. Oyster Creek Nuclear Generating Station has six of the subject valves installed in purge and vent systems. The NRC requested in 1979 that all utilities either qualify their existing purge and vent valves or replace them with qualified valves. As part of the GPUN effort to qualify the existing valves, A. Schiau and myself visited your Continental facility in Corapolis, PA in March of 1981 and met with John Mark and Carl Wilson. Included in the data given to GPUN were the following dynamic torque coefficients (Ct): Valve Opening Angle Ct03 8" valve 12" valve 10' 2.1 12.1 20' 4.3 20.7 30' 7.0 20.7 40' 15.0 41.7 50* 27.0 48.4 60' 51 .0 105.0 70' 103.0 219.0 80' 163.0 259.0 0 = valve diameter in feet GPU Nuclear Corporation is a subsidiary of General Public Utilities Corporation
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- f The Ct va'lu.es were required for calculations to show that the valves could close against design basis accident conditions. The NRC has reviewed the GPUN Calculation and has requested that information be provided concerning the Ct values. The NRC requires that test reports that detail how the torque coefficients were determined including a description of the test setup, test
). disc size and shape, aspect ratio, flow conditions, media used, etc. be provided.
Therefore, Fisher is requested to submit the NRC required information to GPUN so that GPUN can complete its qualification effort. Thank you for your cooperation in this matter. Very truly yours,
. H. Correa Piping Engineering Manager JHC/pa e
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. Attachment 2: ISA Transactions, Vol. 8, No. 4,1969
" Effects of Fluid Compressiblity on Torque in Butterfly Valves" by Floyd P. Harthun I
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0ornpress.b...ty i i;i on ! Torque in Bui:terfly Valves
- FLOYD P. HARTHUNt Fisher Governor Company Marshalltown, Iowa
)- A technique is presented by which the shaft torque resulting from fluid flow through butterfly valves can be determined with reasonable accuracy for 30th compressible and incompressible flow. First, the general torous relationship for incompressible flow is 1 established. Then. an effecuve pressure differentialis defined to extend this relationshio to include the effect of fluid ccmcrossibility. The application of this technique showed very good agreement with experimental test results.
INTRO DU CTIO N DEVELOPMENT OF GENERAL TORQtJE THE APPLICATtoN of butterdy valves in vanous automatic RELATIONSHIP control systems requires proper actuator sizing for The total shaft torque required to operate butterfy efkient control Thus, a thorough knowledge of the valves can be separated into two major components: fluid reaction forces acting on the valve disc is required. . Extensive expenments! work'" has been performed in 1. Dynamic torque-that portion of the total the past to establish a relationship to determine these operating torque attributable to the duid reaction forces and thus determine the resultant shaft tcrque. The force of the Sowing medium acting on the valve general form of this relationship has been e tablished and disc. constmed. However. by using the classical fluid momen. 2. Friction , torque--that portion of the total I tum approach. a similar relationship can be obtained in operating torque attributable to friction in the ! which the torque is shown to be directly proportional to packing and bushings. I the measured valve pressure dirTerential for a given disc .. I position. This relationship along with most of the Since each of these components is mdependent of the l previously published terque information is adequate for ther, a separate evaluation of each component adords incompressible flow. Although the effect of fluid com- the best approach to this problem.This tnvestigation is pressibility on torque has been recogm d. no useful limited to an evaluation of the dynamic torque com* relationship has been developed. The pnmary ob. ponent. If the (netton on the valve snatt,is assumed to be I jective of this investigation is to extend the established independent of direction of rotation, it can be readily l torque relationship to melude the effect of duid com. isolated. The torque required to rotate the valve disc is pressibility. 4 . measured in a clockwise and a counterclockwise direc. tion through full travel. Since friction always opposes 194815A Annual conference.:rensed August 1969. motion the difference between these values will be twice O . Presented seine fltesesten Engnett. the actual shaft friction.
. 281 ISA Transactions Vol.3. No. t .
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of the Buid reaction forces acting on the valve disc. It Q would be discult to determine these forces by purely analytical tec Experimentaldetermination of the To = 4 ; (10)b ( pressures and v. ty pronles in the immediate area of or the discwould quite discult.However.tfa control volume is selected'so the boundanes are points of known To = K D'AP; (10.A) pressure and velocity, an analysis of these forces can be where made from the change in duid momentum through this control volume. Ks = g,sBsB3 BA To - (10.B)
), INCOMPRESSIBLE FLOW # = UAE An expression for dymmic torque is developed Equatio assuming incompressible Sow. This torque is a function coefe:ent n (10.B)is dear.ed as the dimensionless torque which can be determined experimentally from of the duid reaction force.F.and a moment arm.D.which tests conducted with incorspressible Row.
is a charactenst2c dimension of the valve disc. To-f(F.D) (1) COMPREssiaLE Flow Using the Suid momentum approach. the force. F is De dynamic torque for butte:8y valves is proportional given by: to the mass How rate and velocity change through & , F = MAV selected control volume for both comoressible and ' (2) incompressible Sow (i.e To ec MAV). Therefore, the ' where approach used to obtain an expression for this torque assuming incompressible Sow can be extended to F = sum of external forces acting on Suid compressible Sow by re deaning these two variables. M = mass Sow rate - First. assume that the velocity at the valve disc. V,. AV = Suid velocity change through the control is proportional to the velocity change through the control volume volume. Then, the dynamic torque can be expressed as The mass How rate. M. is given by Te oc NV, (11) g M - pA V (3) The velocity at the valve disc is given by By using a proportionality constant. B , the mass How M rate can also be deaned as V"pd (12) M = B, AfpaP)"2 (4) Equations (31 and (4) are combined to obtam the follow-By combining Equations (!!) and (12) the dynamie ing expression for Suid velocity: torque is shown to vary directly as the square of the mass Sow rate and inversely with th: Buid density at the valve V = B t(AP/p)5'8 (5) disc. He velocity change tf rough the control volume. AV. M8 in Equation (2) can be expressed in terms of the velocity To x (13) at the valve disc by use of a propornonality constant. Ba Determining the Sow rate of a compressible Huid T = BsMV (6) through a control valve by analytical techniques is quite By substituting the e$pressions for mass Sow rate di5 cult because of valve geometry. The major eroblem Equation (4) and Suid velocity Equation (5) into Equa- !s to establish the pressure differential between the valvs , tion (6) the force on the valve disc is "I't and the vena contracta. However, by deSning the 2 physical system in which the valve is mstalled to conform F = B i BsAAP (7) with spec:8 cations given by the Fluid Controls Institute For a given valve size.the How area. A. for any angle of (FCD.'2' empirical relationships developed specifically dise rotation. 9. can be wntren as for determining Sow rate for control valves can be considered. Several such empineal relationships base j 2 been developed; however, only one, the Universal Gas A = B,nD (8) Sizing Equation."' has been shown to accurately de5ne l the Sow rate for any valve cortiguration. This equation l De force. F. acts upon a moment arm which is a function is $1ven by { of the disc diameter. D. Now, the dynamic torque can be _-. - 1 written as 5:0 .
,59.64 AP, Q= -P Ci CsC,sta O To - B FD 3 (9) U i
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- ISA Transact.ons . Vol. 8. No. 4 182
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i 59.64 - - x2y M = 1.06 p Pa 2C C, sin - g ,,CaC P. ,,, (15) i For convenience the form of Equation 124)is simplifed. The sine function in Equations (14) and (15) is used to 7,= K D3ap i (25) define the transition between incompressible flow oc:ur- where ring at low pressure ratios (AP/P ) and critical flow. CC.
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;. ~59.64 AP' Equation (26) is defined as the pressure differential 8"
tC Cs ( CO.ntributing to the dynamic torque on butterdy valves with conditions of compressible dow. Rewriting Equation (15)in the following manner: EXPERIMENTAL RESULTS M = 1.06,fp P C C C,F i (17) De factor, F,is bounded by the fo!!owing: ne first step in the experimental evaluation was to establish the dimensionless torque coedic:ent. K , as a F = sin 6 for 6 < x/2 function of valve disc rotation as defined by Equation (IS) (10-B). A test was conducted on a 4-in. valve under the F = 1.0 for 9 2 z/2 following controlled conditions: By substituting Equation (17) for the mass Sow rate in Equanon (13), the dynamic torque for a given valve is 1. De valve was installed in a 4 in. test line with a given by . minimum of 12 pipe diameters of straight pipe
. upstream, Pi(Ci Cs sin g)s 2. The pressure taps were located according to FCI To
- pi (195 specidestions and attached to the test line
#d d according to specifications in the ASME Power
- The cnly parameter in Equation h that cannot be and Test Code.
readily obtained is the density at tne valve disc. p,. 3. Water at ambient temperature was used as the d_ Assuming that the change in the ratio of Suid density at f!cwing medium. the valve inlet to fluid density at the valve disc with 4. The inlet pressure and outlet pressure were held increasing pressure ratio is small relative to the total constant, change in = ass dow rate, the torque expression can be 5. ne test was conducted at a low pressure ratio si=plined in the following manner: (AP/P i= 0.0881 to ensure incompressible dow. To x P i(Ci Ca sin 6)s (20) Therefore, for compressible flow: 32 l l l l
' l Ta = K P (C C: sin 6)2 i (21)
For small values of pressttre ratio (AP/P ) Equation (21) l l l l 28 reduces to the incompressible torque relationship given l l;l by Equation (10-A). 24 - l l l l l As AP/P ~0 go A sin 9 - B (radians) % x 4 l l l l l l [k To - K (59.64)s3p The expression in Equation (22) is equivalent to the
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d12 l l l l lfl l e l l l l l expressionin Equation (10 A): n 8 K (59.64)*AP = Ki D aP 8 i l l *l)l l l K: = 9~ g (23) l l 0 10 20 30 40 50 60 70 8C 90 i By substituting the expression in Equation (23) for the a .- - ANGI,E CF RCTATlCN.CEGREES coedicient K 2in Equation (21), a general expression for ; O dynamic torque for torque compressible pi,o r. i . osm.n.ione... ,,u. co.ef tei.ne. 4.in. nutt.,,,, the dimensionless coefeientdow is obtained established for using velvo inco<noreesible flow: pi = s00 psie. p = A10 msi. -- 283 ISA Transactions . Vol. 8. .'Vo. 4 . Oc' l* '*" ' ' YY l e-eg. . . . .
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0 10 20 30 40 50 60 70 80 90 0 10 20 30 40 50 60 70 80 90 ANGLE OF ROTATION.CEGREES ANGLE CF ROTATICN.0EGREES Figure 2. Dynamic torque ve. angle of dise rotation,4 in. Figure 4. Dynamie tortrue vs. angle of dies rotation,8 4n. ' butterfly velve coenperison of oncerimental results with ' butterfly volve, comparison of especimental reeutts with calculated torque. Incompreemable flow: p, m 100 peig, cadeu8eted torque, incompressible flows p m 100 peig, sp a s pea. . as e a pea. Torque measurements were made at selected incre. ment between measured torque and the torque calculated a ments of disc rotation (0-90*). A transducer, consisting using this coc5cient. of a steel bar with strain gages attached. was f!xed to the The next step was to verify that the torque coeScient valve shaft and used in conjunction with an osetllograph is indeed applicable to other valve sizes provided geo-g to measure and record the shaft torque. The data from. metric similarity is reasonably-well maintained. The this test were used to determine the dimensionless torque results on Figures 3 and 4 again show very good agree.
) coe:!icient plotted as a function ofdisc rotation on Figure
- 1. 'Be curves plotted on Figure 2 show exc:llent agree.
ment between measured torque and calculated torque for two 8 in. valves. 72C 36C 64C l l 32C
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butterfly valve. compersoon of esperimental reeuite with butterfly volve. 60* disc rotation. comparison of espers. sp celculated a $ paa. torque, incompreesible- flow: p, a 100 peig, mental results with calculated torque, compressible flowt ' O p, a 214.4 paie, flowing medium a est. ISA Transactions Vol. a. No. 4 284 -e-..+ *
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0 10 20 30 40 50 60 70 80 90 40 1 Id r X ANGLE OF ROTADCN.CEGREES ' C Figure 4. Dynamle torque vs. engle of dies rotation. 4-in. O mM M 4 2 60 70 80 M butterfiy veive, comparison of empenmental reeuits wit
- calculated torque, comorossible flow: p sea 114.4 pose, ANGt! CF ROTATICN.CEGREES ar a 5 pel(ap/Fs e o.0444), flowing medium a ai'*
F1gure 8. Dynamic torque vs. engle of dise rotation. 4-in. betterffy valve comparison of test results with calculated It should be noted that discs in the two 8 in. valves **'au' **m. e-bie fiow: p, = 64.4 poi as w so p.s were of substantially diferent geometric shape. Using ('#I#' " '(*'"'***"**8"**i"'**d'"""*i'- the ratio of disc diameterto hub diameter as an indicator. #. M these ratios were 4.56 :1 and 3.55 :1 for the valves used to similar to the disc in the 4-in. test valve used to establish obtain the data for Figures 3 and 4. respectively. The difrer==>c= i= 'cra= ====i'=d r=< 'h' : ita = the torque cociEcient.K .
" '= = " dr"=='* ' 'a" i
( E9 5 psi pressure diferential shown in Figures 3 and 4.is
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include the efect of Suid compressibility is accumplished t the result of this diference in geometry. The disc in the by dedning an efective pressure diferential as shown in 3 in valve used for the test in Figure 3 was geometrically Equation (25).The curves on Figure 5 show the transition from incompressible dow to entical Sow with increasing 18 0 pressure ratio for a 4-in. valve set at 60* disc rotation. l l Here again there is very good agreement between the g i I torque calculated using Equation (24) and the experi-t I 8 .To=K,0 aFl3 mental results. The incompressible torque curve is also 140
. I shown on Figure 5 to emphasize the efect of Suid 2
6 compressibility. s 4- TI o= K,0 i a P'i l M The curves on Figures 6 through 3 are presented to j.320 ,, 'OATj l A compare experimental results with torque calculated
, 10 0 I e I (l/ li using Equation (24) for full 90* disc rotation. At low w l 1 \ pressure ratios. the torque using air as the Sowing 8 I I 4 .o medium is essentially equal to the torque for incom-g 80 .% pressible dowl Figure 61 As the pressure ratio is increased.
y 60 the efect.of duid comoressicility becomes more pro-l I l I l I l I /Y jf l l
"\J nounced as shown in Figure 7. Once entical dow has 40 \ been attained, no further increase in torque is realized l by increasing the valve pressure diferential as shown on l l l Figures.
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l I CONCLUSIONS 0 10 20 30 40 50 60 70 80 70 ANGLE CF ROTATION.0EGREES A technique is presented w hich ean be used to determine Figure 7. Dynamia torque vs. engle of disc rotation,4 ine. the dynamic torque for butterdy valves with reasonable butterfly velve, comperisers of eagerimentas results with accuracy. The basic torque relationship developed for incompressible dow is extended to include the efect of O omiculated teraue, cornarseeable flow: - '
- 7. = 64.4 pese, ar = to poi (ar/p, si41.1;LH flowing medium se ear. Huid compressibility. The method presented is deve! aped C
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Q = Mow rate incompressible dud sdh C. = now rate comprmbie sa4 seh _ (, incompressible Sow to critical flow. Application of this I " * * "*" *" method shows excei!ent a$reement with experimental T. = Dynanuc torque in,'*b I s test results. .. .. .
, _ . V = Ruid velocity.in./s ,
/
pi = Rund density at upstream pressure tap. lb/IrLa
/ NOTATIOst p = nuad dessary at vahe disc.Ibeia.*
A = Row area. ia.8'- t Be . Ba , 2,, s. - Constaats of proporuonality ~ REFERENCES C - C/C. C - Correction factor for var:auen in spec 8c heat ratio I. Keller. t. C. and Satanaan. I. F. Jaawy 1936. Aerodynanue C = Gas sanas coeht Model Tests on Butterdy Valves." Escher.Wyss News. 9.
.. C,, = now coedkanat 2. R.
' - =- Volmesary Standards for Maarvement Procehrefar pr @ Nonunal valve diameter. is. . Deter =enne Cae ret Vahe flew Capacity.1958. Flud Controts I - Force. !b !asutute. !ac. paper FCI $8 2.
G = Speedic gravity 3. Suresh. J. F, and Schuder. C. S. October 1964. **The Develv9 ment K - Dimensionless torque cost 5cwas of a Universal Gaa TJnas Equanos for Control Valves." 114 Trans. M = Mass Sow rate. lbis 3:322-323. F, = lalet pressutt. pssa 4. Flow Measwement: Isrtrwnents and Apparatus. Supplement to she M = Valve pressure ddferential pst ASME / ewer Test Codes. ASME toport irTC 19J 4 1959.
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. INSTRUMENT SOCIETh of AN,kRid
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INSTRUMENTADON TECHNCLOGY FROCEEDINGS Off!cial monily n:againe of the society, containing Bound volumes of technical papers presented at ISA practical, cunent, authoritative information on all phasea Conferences and Sympes a each year.These proceedings of instruznentation -in:!uding measurement, data proc- are a permanent re:ord cf all papers programmed and .
; essing, telemetering, ccmputation, and automatic control made available for publican:n. ney represent the in-E:ch issue carries timely editerials, technical uticles, portant progress being made in the total Seid of inatm.
operations and :naintenance features, application and mentation. Proceedings are invaluable references for design stcries, new techniques and proc: cures, new every :ngtacer, eaceutive, researr.her, and technician procucts, c:w !!terature, corning me: tings ard confer. working in tbc Eeld of icdustrial and scienuf: instru-ences, and Society news. mentation. - -
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A 550 psy reference text gentaining oVer 500 ab. ne Society proA6s three basic trait.ng tests .:wo stracts of instrumentstieth and auscusador coctrobstaah sound color movie A:ms, and a ilm: trip for education ards S recccmedded p'rac ice [devyc'psd by 2F tecif and truining of technicians and engine: s it the fr!d of zic:1 societies.tist inch.dse datsdirduo.of cost cuirent inst-umentation. Texts are availabic for purshase. Films revision and rod:ct cf avs!IabSiry. Contaics every. rec- mayJe.re;ke;i or purchased. , ,, , ,j ,, ., om= coded prs:Tice af ISA in coreplete detail. Lists titles n.u . , v. n..m. .- t 4..., ,3..'. cf British and Canadian standarda for instr.unentatica. 2.9 " "- - - - Inder.ed by subject.
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A three.vpluice series of valuable reference books in a fleid vital to instn. men 4. tion inc!udes Elterriest tisstru- [' 15A RECCMMENDED PRACTICE AND STANDARCf mentrin Naurdous Loe2rtons.a 223.page text Els;rricci ( More than 30 individ talISA standards and pr:ctices fagry Prcerters, a 174.page stste ff-the. art:omplemen-for instru== t specifestions, termine:ogy and nemen- tary vo!ume. and St. crrical Sc/ cry Abstraers. ucv !a its clan:re, insta!!atica precederts, operatien prec:dures, third edition. maintensuce pro:cdures, application procedures, design spe:id:stices, and other aspects Of industn21 and scien- ISA TRAN5DUCIR COMPENDIUM,2nd EDITION tife iristrumentation :r: m circulation. Thne standards An updat:d guide to transdut:r sts:c.of.the art and Are deve:oped and r.pprose.,. .ay ISA Ccmmitt::: and product pecfctmante d:ta for the dss.rr'ter, speed..er,and Board, st:ded by authorities represecung 1: consensus . purchaser of irtstruinentation equipment. It.ts the only cf opinions of the users of instrurrentation. W r m e m a m M .M s du:ers :emprising 1300 mecei series. Data are presented , 1RANSLATIONS CF FClitlGN JCUKNAt$ ir. a form refersbis ?.o the latest engineering s: ndards and ! Inst ::;pm Society M MW ecvi'et editertst di. .-cy-eri tr2rtiert. T'te 2cd Edition of this standard
, re: tion for tne En;lish cover.to.coser trans!stien of tour refererc: will de publish:d 'n thret pets at one ye:r inter.
iending technical journats onfi n:dy published irt th: vais, e.t;n part to be revised tr.entti:al;y. Part 1 avai'aof t ' (i.S.S.R. D:y are Me1rurement Techniques. Ins:ru. now, mets tt r.shcets for the vartnoles pressure, dow, 1:~r: and Enerimr4 T&enos Automa: ion cra ned neve. P1tts Et nnd lit, to be published in 1069 and Remotr Centnl. and Industrul L Aorciory. The Chi. 1970. xas ilst :: ntdu~.:ts for tetr.ce 2ture. chtmicat : ort. nese journal A.rta Awome:ic Sirxa is abo pub;ish d pasmon, ph'.st: l prepe:ues.hu-'t.cQ and moisture. sdt. with NSF ass. stance. 2tien. menon. ,fieens ca. fore: and torque, and seund. ; heq:.r!rrier eilof nee conse ISA valicatmns shum'd t,e dirtt:ed 20:
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Ir.strurrer:t Soc.rty of A=mca A .8CO Stanwtx Street Fi;tsburgh. Pa. !!r.2 M_ - sr
, Attent.cn: Publicat: ens D epsrtment ( t t
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C_ ~ d Attachment 3: Torque-Pressure Drop Relationships Used in Butterfly Valve Oinamic Torque Coefficient Selecticn "- 9 ' 1
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Attachment 4: CFG 40B-10, Page 1, January 1973 "BFV Torque Determination"
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, p 5gHAND 800/r CFG 408-10 TQ3* JANUARY 1973 PAGEI CONTWIENTAL DIVISION BFV TORQUE DETERMINATION
}. Objective It should be noted at this point that the sum of a number of torque compo. l before velve torque is determined, the nonts. To avoid confusion, a number The determining factor in accu. user should consuit CFG 200 20 to of these have been combined and a rately selecting the most economical ensure that the pressure drop limi. number of calculations have been actuator for a butterfly valve is the tations aro not exceeded for the specific performed in advance. Thus, each torque recuired to open and close the valve construction in consideration. valve type can be represented with the valve. The following is a quick and . same sempte, practical fo'rmuTa shcwn ,
easy method of determining actuator below. The various torque components I torque recuired in both the open and lettroduction and the process of simplification are l the closed position of a butterfly explained fully in the appendis (See l valve. Butterfly volve torque is actually Page 23). where: A, B, C = Tabulated coefficients
. [APacte Ne'er} APactg = Actual pressure drop TOTAL TORQUE (IN.LBS) = A (APacte*) + B + C or is at angle a*
APdfq* smaHer i AP.,,g = Effective pressure drop at angle a' [ Procedure 4. Select values for A, B and C again, Refer to CFG 40F.20 for Fisher ( 1. From the above t&e, determine this time according to the character. W of the value at the desired mani. actuator selection. _ . ~._. the effective pressure drop, AFeffq+, mum open angle (a*). Write the
. at the desired maximum angle of equation snown uti g the new values
- The effective pressure drop term, opening. and perform. the simple calculatisn JP.,,.a*, arises due to the flow con.
required. This determines t*s required ditions near the disc. It is a calculated
- 2. Tum to the tabic for the valve actuator torque (valve tnrque required) value and will usually vary from the type, class and disc type in consider. at the desired angle of opening. actual pressure droo. It may be ation, described.as the pressure drop seen by
- 5. An actuator may now be selected the disc in tne region of dow which
- 3. From the table, choose values for with either: affects oniv the "C" multiplier in the A, B and C according to the character- g tcrous formula. Note that, due to its istics of the valve in the flgjgg posi- , g nature, the effective pressure drop is tion (0,). Write the ecuation shown used onlY at open angles (JP a ,,.o*
- using the selected values and perform dewiM in 3 W 4
. APact.0*) and then oniv wnen it is less the simple calculation required. This b) A varying torque output which than the actual oressure d reo determines the required actuatcr equals or exceer's both of the deter. (aP,,, o s).
torque to move the valve disc away mined toro,cs at their respective from its seat. valve positions. l EFFECTIVE PRESSURE OROP 1 NOTE. Pi
- Uostream pressure iosial at tee maicated angte of openmg !Q*) TABLE t Type of Type of Anele of Oise Coenine Dene Flu.d 0* l 10* 20* l 30* l 40 ' 50' l 60* l 7e
- So'9e*
0.enventi6nas L,cuid ! 2 Pact 8 l 0.570P i 0.730P l0.$00P l0690P i i 0.550P i l 0 450Pil0.390P i , 0 35 cpi or Offset Gas APactg- lQ.Pa er.10) @ l 0.25CP i 0.250Pi l 0 200Pil0.200P, l0.140Pil0.140Pil
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APseta' l 0 700P i f0700P)
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l0670P i s g_ Liowd 0.700P i 0.700Pi 0.600Pi !O500P l0450Pi i Gas 0.350Pi 0 350P l 2 Pact 4* l 0.260Pi il0.350P i l0250P i l0.180Pi l0.110P i l 0 090Pil
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Attachment 5: FCI 58-2. " Recommended Voluntary Standards for Measurement Procedure .sr Determining Control Valve Flow Capacity 4
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Fluid Controls Institute, Inc. NEW YORK CITY. N. Y.
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RECOMMENDED VOLUNTARY STANDARDS FOR MEASUREMENT PRODEDURE FOR . DETERMINING CONTROL VALVE FLOW CAPACITY l k
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l l l ADOPTED NovruBER 25, 1958 PRICE 10 CENTS i PRINTED IN U S.A. REPRODUCTION WITH CREDIT TO FCl PERMITTED
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( e" FOREWORD In the fall of 1950, the Fluid Controls Institute, Inc. (then known as the National Steam Specialty Club)
- s. recognized the contribution that could be made in the Control Valve industry by establishing stand-ards which could be applied for testing such valves.
In the spring .of 1952, a formal engineering committee was established for the purpose of evaluating l the possibilities of " Recommended Voluntary Standards for Aleasurement Procedure for Determining Control Valve Capacity". Because of the many variables and problems entailed, numerous drafts of this St ndard hase been
. evolved and the procedures tried by several companies interested i:t this work.
l This present proposed standard is the result of these years of effort. Control Valve Section of the Fluid Controls Institute, Inc. apr reciates its responsibility in connection with this standard and welcomes all constructive suggesticas for its expansion and revision. 1 l FCI ENGINEERING STANDARDS CONINIITTEE l CoxTaos VAtyt SEcTrox 1957 - 195S A.J. Hanssen (Chairman) Conoflow Corporation Philadelphia, Pa. George Chinn Kieley & Stueller Co. Sliddictown, N. Y. Otto Kniesel Hammel Dahl Co. Providence, R. I. Cecil 31. Johnson Fisher-Governor Co. h!arshalltown, Iowa Donald J. L. Lin Black, Sivalls & Bryson Tulsa, Oklahoma Ralph Rockwell 3!inneapolis.Honeywell Ft. Washington, Pa. Paul Wing Alason Nellan Division of Norwomi, Alass. Worthington Corp. 2 . v - _ _ _ _ _
. .. g v . g gy4fts - g ' . . . , . u. n 7 e cl C g.2 s - i RECOMMENDED VOLUNTARY STANDARDS FOR MEASUREMENT PROCEDURE ~~'- o FOR DETERMINING CONTROL VALVE FLOW CAPACITY ..
I:llf7 qf - - -- -~~ W SCOP.E"F'.,,. __ _ ._ A. Thisis a recG...-..ua of a standard procedure for determining the flow capacity of a con, trol C vahe and a standardization of the arrangement of the test manifold used as a basis for establish-in; such flow capacity. - ;gy i,*n .s "s-4, ,, g C. m yp. , , u :, D. These procedures are for the guidance and voluntary acceptance by industry in determining con-trol vahe capacity. 11 TIEST SIANIFOLD DESIGN . 7 A. Line Si e
- 1) The conduits either side of the valve being tested shall be pipe of the lightest schedule, having a pressure rating at least equivalent to the body rating, but in no case lighter than schedule 40 pipe. This pipe shall be of the same nominal size as the nominal size of the valve except that, for vahe sizes smaller than 1" nominal, a 1" pipe shall be used. The pipe shall be free from scale, rust or other obatructions which may cause excessive turbulence. ,
B. Line Length
- 1) There shall be a sufficient length of straight pipe ahead of the valve being tested to secure a f.dtly uniform velocity profile in the approaching stream. The ASalE Power Test Code on Fh,w Steasurement shall be used as a guide and the valve being tested shall be installed under thejpcatiepyL flp themuurwtrionargivg6gi trol v:rtres the 'Dd/ul rat fnay be considdredypereies to k &T! agdeprifice plageqryt,e@.
~' ~* '--d ngor con.
- 2) To insure a reliable pressure ;neasyrement ther,c A gf traight pi t equal to, or longerThan,'4rre pi>CWikiteterifoMitMidt frone, shat!4c a .tength,,
ttfefocustreasypatsstre",Iap.* f > tT C. Pressure Tap
- 1) Pr" essure
- ti s sNa}l 3Erh[Nt/d siz'eYddnYghitbo tMikikMiNbhe kb!EhMer Test 8
Code section on Flow >!easurement for pressure taps for orifice plate flow measurement.
- 2) The upstream pressure tap shall be fodited 6 pin (Mtto 2M pipe diameters upstream from the inlec connection of the valve being tested.
- 3) The downstream pressure tap shall be located from 4 to 6 pipe diameters downstream from the outlet connection of the valve being tested.
D. Flow Measurement
- 1) The means used for the measurement of flow shall be in accordance with accepted r ractices to result in a measurement accuracy within plus or minus 2To of the measured value and shall be calibrated frequently to insure maintenance of this accuracy.
E. Pressure Measurement
- 1) The means for measuring pressures and pressure differentials shall be accurate within plus or minus 2c*o of the measured value and shall be calibratett frequently to insure maintenance of this accuracy.
111 TESTING PROCEDURES A. Fluid
- 1) Water at a temperature between 40F and 120F shall be used as the fluid for conducting these tests.
B. Pressures
- 1) A pressure drop of from 5 to 10 psi shall be used.
- 2) To insure that the downstream pipe is completely filled, it is recommended that a downstream pressure of at least 2 pig be maintained. When this is not pouible due to vahe pressure rating or test facility limitatmns, a positive back pressure as high as practical shall be maintained.
C. Data to be Recorded
- 1) Upstream pressure (PI).psig and/or downstream pressure (P2) psig.
- 2) Pressure drop (6P) psi
( 3) Flow (Q) U. S. gallons per minute
- 4) Valve lift or opening within plus or minus 17o of rated openin:t. ;
- 5) Water Temperature in *F 3
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- 6) A physical descriptian cf th2 valve being tested, including thi directi:n of flow. I
, , 7) Barometric pressure (if required to convert P1 and P2 to PSIA).
D. Number of Tests
- 1) Each val graph Ill B,ge shall after flow be. tested has been at three different pressure drops within the range stated in(Pa stabilized.
u ( IV EVALUATION OF. DATA
- 1. Divide cach of the flow readings by the square root of each respectise pressure drop. Q
- 2. Average the three results to obtain a factor. VF
- 3. This factor may be called Cy under conditions established by the manufacturer as being reason-
' able for use on a valve where the configuration of the valve will not give excessive variation within their flow formulas.
1 FLUID CONTROLS INSTITUTE, INC. STANDARDS AVAILABLE PRICE FCI 55-1 Standard Classification and Terminology for Power Actuated Valves 25c FCI 581 Definitions of Regulator Capacities 20c FCI SS-2 Recommended Voluntary Standards for Measurement Procedure for 10c Determining Control Valve Capacity L 4 . ~
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4 Attachment 6: Fisher Laboratory Report Excerpts Problem 13408, Report 5 1 1 e
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TEST SETUP FOR DETERMINATION OF VALVE CHARACTERISTICS AND SIGNIFICANCE OF IRESSIRE TAP IOCATION m :o a b
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Body Pressure Drop 6f'M i
- Average CyA t .9 a
- Rated Travel = m t Air Test Body Inlet Pressure C S m/A Body Pressure Drop c eme-C ~
Average Cg At 9d* Rated Travel = nvm _ 100 6
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Attachment 8: Fisher Laboratory Report Excerpts Problem 13408, Report 2 Problem 1340, Report 1 O
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l v ATTACHMENT 3 ( ENCLOSURE REQUEST FOR ADDITIONAL INFORMATION l
, OYSTER CREEK NUCLEAR GENERATING STATION .
DOCKET NO. 50-219 CONTAINMENT PURGE AND VENT VALVE REPLACEMENT CANCELLATION l 1.0 _ Mis _torical Background The licensee has been maintaining the purge and vent valves mechanically re- l stricted from opening more than 30* in accordance with NRC's interim position as stated in the October 23, 1979 NRC letter. GPU coomitted to replace all containment purge and vent valves with qualified valves rather than qualifying the existing valves in their letter of July 31, 1980. A subsequent letter from CPU dated August 27. 1981 requested an extension in the schedule for re-placing the containment purge and vent valves from December 1, 1981 to the end of their cycle 10 reload refueling / maintenance outage. The licensee's April 19, 1984 submittal included a report number 4-01-82 by the Clow corporation containing operability demonstration information for the Clow replacement valves. This information was reviewed and found to demonstrate operability ( for the Clow valves from the 90* full open position under LOCA conditions in the proposed installation configuration (BNL TER dated July 26, 1984). The licensee's September 24. 1985 submittal proposes cancelling the replacement of the existing valves with Clow valves and contains an analysis (TDR 266, Revi-sion 1) that is intended to demonstrate valve operability for the existing valves under combined seismic and DBA/LOCA conditions from a restricted vsive opening angle of 30' open. 2.0 Preliminary Evaluation
~ I -
The existing valves are shown in the table below: Valve Site Number (Inches) Location Manufacturer Use V27-1 18 Outside containment Centerline Drywell vent V27-2 18 Outside containment Centerline Drywell vent V27-3 18 Outside containment Rockwell Drywell purge V27-4 18 Outside containment Centerline Dryvell purge V23-13 8 Outside containment Continental Drywell purge V23-14 8 Outside containment Fisher Drywell purge ; V23-15 8 Outside containment Continental Torus purge ! V23-16 8 Outside containment Fisher Torus purge I
. V28-17 12 Outside containment Fisher Torus vent V28-18 12 -
Outside containment Fisher Torum vent The analysis included in the September 24, 1985 submittal from CPU (Technical ) Data Report TDR Number 266. Revision 1, dated May 9. 1985) has been examined 1
- and does not contain sufficient information for a complete review of operabil- )
ity demonstration under the postulated accident conditions for the presently installed valves. 1 I l ~ l
e . Ths items listed bslow are intendsd no a guida for c'ompleting tha informatien required to perform a valve operability review in order to comply with NUREC-0737 Item 1.1.E.4.2.4.
. _ Dynamic Torque Coefficients (CT). The licensee states on page 5 of TDR 266, Revision 1, that the torque coefficients used in his analysis may be obtained from the valve manufacturera and references a letter. This is in-adequate for a review. Acceptable documentation in this area should in-clude' test reports that detail how the torque coefficients were determined -
including a description of the test setup, test disc size and shape, aspect ratio, flow conditions, media used, etc., so that confidence can be estab-11shed in the torque coefficients used in predicting valve dynamic loads.
.. . . . . .....t . . . . .. . . . . .
. Valve _ Installation Configuration. The licensee's analysis TDR 266, Revi-sion 1 does not provide this information for each valve. Typically, the following infornation is required:
- 1. Direction of flow.
- 2. Disc closure direction.
- 3. Curved side of disc upstream or downstream (anymmetric discs).
- 4. Orientation and distance of elbows, tees, bends, etc. within 5 pipe diameters of valve.
I
- 5. Shaft orientation.
- 6. Distance between valves.
. Dynamic Torque Analysis. The licensee provides in TDR 266, Revision I the methodology used for ,his torque analysis and references Oyster Creek Purge and Vent Valve Analysis Calculation Book Calculation 1302 SX-322C-A07. The referenced calculations, which should include assumptions used should be
( provided for the reviewer.
. Actuator Torque Margin. In order to demonstrate adequate torque margin by comparing valve torque loads durinE closure to actuator closure torque availability, curves or incremental data, such as spring torque at various valve angles need to provided by the licensee.
. Seismic Qualification of Valves. The licensee has not indicated by ref-erencing documentation that the valve assemblies are seismically qualified.
As an example, for further guidance in understanding the type of informatio'n required for operability demonstration, the licensee should examine the Clow
" Purge and Vent Velve Operability Qualification Analysis Report" Number 4 82 submitted to the NRC with the CPU letter of April 19, 1984 In addition, Attachment A to the November 29, 1982 NRC letter (V. Noonan to D. Crutchfield) can be used as a guide for valve operability demonstration requirements.
t l h me m.
O f ATTACHMENT 4 l l I l L_
' 14:15 GPU NJCLEIR NO. 0H5 082 05/05/96 O h C.ek C+L'oh M M % *s --
~
Provide cross section of valve discs and verify that they are the l same as those used in the Ff sher Test. g,rw //p//g Ff sher provided disc data in 1961 which was confinned via 8+. ~ telecon on 4/11/86 For the a valve the disceter is 8" and the smieum thic) N M df*y 4:1. For the 12ness is 2", valve thediameter is 12" and the maximumresulting in an aspect ratio of
. thickness is 2 3/8* resulting in an aspect ratto of 5:1.
Fisher in their memo, of March 12, 1986 reconfimed the aspect b-+ El M- ,j l ratf os and the fact that the discs (8" is conventional and 12" . is fishtail) are considered syneetrical. Fisher also stated in [J/ their memo that the 8' test valve had an aspect ratto of 4.57:1
%ich is sisillar to the 8* valve and that the 4* test valve with a fishtail disc had an aspect ratio of 5:T mhich is the same as the 12" valve. .
With respect to the Fisher / Continental valves. verify that the Fisher test report methodology and test data (s applicable to these valves. Fisher in their memo of March 12, 1986 referred to Fisher
~
Laboratory Reports as being applicable for both the 8' and 12' valves. Continental was a subsidiary and then a division of
- Figher. The model numbers for the valves and actuators are F1 sher isodel numbers. s 4gg p,% . Q ct, M TC- M fhw V d'1 3/e4 ove Q d d . 1 Provide spring torque vs. valve closure positions. .
The Centerline valves have double acting actuators (air to open, air to close) with an accumulator as a fati-safe device (added per 1.ER 84-023). Centarline has provided a curve of output torque vs. valve opening (attached). Based on a minims i i supply air pressum of 60 psig, the available output torques are as follows: Ofsc Position Output Torque , 300 (open) 15903 in-Ibs ! 150 (open) 14706 in-1bs 50 (open) 12711 in-lbs l 10 (open) 11514 in-lbs 00 (closed) 11286 in-lbs The output torque values are less than those listed in TDR 266 but still result in available safety factors above those ; required by TDR 266. It should be noted that the nominal i supply air pressure is 80 psig and this will result in output torques greater than those in TDR 266 for all disc positions except for 10 open. At 10 ppen the output torque will be 985 of that shown in the TDR. afr to Seth open,Fisher spring valve to close. models have Fisher 656-60 actuatorsThe spring part number is 1K1 wtth a spring rate of 280 lbs/in. Fisher has stated that they do not have torque curves available for these actuators, but has suppfled the following dgta. The available torque at 600 open is 1561 in-1bs and at 0 open is 2076 in-lbs. These , values are less than the 4800 in-lbs listed in 1DR 266 but are still above the calculated required torques. Mechanical Components is meeting with Fisher on S/2/86 to discuss the actuator staing and possible endifications to increase output torque.
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