ML19210A617
| ML19210A617 | |
| Person / Time | |
|---|---|
| Site: | Crane  |
| Issue date: | 11/02/1977 |
| From: | Herbein J METROPOLITAN EDISON CO. |
| To: | Reid R Office of Nuclear Reactor Regulation |
| References | |
| GQL-1496, NUDOCS 7910300652 | |
| Download: ML19210A617 (4) | |
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NRC OISTRIBUTION =cn PART 50 CCCKET MhTERIAL A 1:P=cc:.usNT FRCM:
Metropolitan Edison Company 11/2/77 i
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Mr. R. W. Reid Reading, Pa.
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- r METROPOLil~AN EDISON COMPANY Pt4T OFFic.E BOX 542 READING. PENNSYLVANIA 19603 TELEPHONE 215 - 929-0601 Ilovember 2, 1977 GQL 1h96
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/ g g#4 Director of 'Iuclear Reactor Regulation
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Attn:
R. W. Reid, Chief 4'
Operating Reactors 3 ranch Ilo. k C % g7 7
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- Iuclear Regulatory Ccamission Washington, D.C.
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Dear Sir:
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Three Mile Island IIuclear Station Unit 1 (T5
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4 Docket :lo. 50-289 Operating License No. DPR-50 Decay Heat Pump Shafts During a telephone conversation on October 19, 1977 between the IIRC (Mr. Zevt:ig) and Met-Ed (L. Stevens), the IIRC requested Met-Ed to provide a summarv of the stress analysis performed for the TMI-l Decay Heat Nmp Shafts. This information was to be provided in two parts. Our letter GQL 1h77, of October 27, 1977, provided information on loads and stresses a+, a recirculation flow rate c f 80 grm. This letter nrovides the re.aaining information and delineates the loads acting on the decay heat pump shafts at flow rates of 135, 550, and 3,000 gpm.
1.
Steady-State Radial Loads Steady-state radial loads were calculated using parameters in a Worthington report of radial loads.1/ The calculated loads are as follovs:
Flow Rate, em Radial Load, lbs_
80 ho 1 35 ho 550 80 3,000 120
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1/
"An Exterimental Investigation of Radial "hrust in Centrifbgal hm= s' b-A. Agostinelli, et al, ransactions of the ASME-Jcurnal of Basic Engineering, April 1959 11113 115
R. W. REID, CHIEF November 2,1977 GRL 1496 It is noted that these values are sc=ewhat lever that. e 260-pound value calculated by Worthington and reported in our letter of October 27, 1977. The Worthington value was calculat ed using a con-servative apnroximation rather than the more accurate detailed method given in the referenced Worthington paper.
Ustng either method, the steady-state radial loads are very lov at a ll flcv rates and result in very low stresses.
2.
Steady-State Torcue Loads The steady-state torque loads were calculated by coriverting the pump brake horsepcver to a torc.ue value using the standard textbook formula. 2/
The calculated loads are as follevs:
Flow Rate, gyn Torcue, lb-in 80 5,250 135 5,250 550 5,680 3,000 11,900 The highest steady state torsional load occurs at 3000 sp: and results in a steady state stress of 21,000 psi 3/ which includes the effects of a stress concentration factor (5 0).
This stress is well belev the torsional yield stress of 62,500 psi.
(1/2 the Armco catelegue tensile yield strength for H-ll50 heat treated conditicn).
3.
Alternating Radial Loads Worthington has advised us that they do not have any methods for esticating the alternating radial leads, either at lov flows or at rated flev.
Accordingly, the upper bound value of 670 pounds we provided you in our October 27, 1977, letter for an 80 gp flow rate is the only load estimate available. However, it is expected that the alternating radial loads vill decrease at higher flows, since there is less likelihood of recirculation type flev instabilities within the pump at higher flev rates.
h.
Alternatine Torcue Loads Worthington has advised us that they do not have any methods for esticating the alternating torque loads, either at lov ficvs or at rated flev. The upper bound value of 11,300 lb-in we provided you in our October 27, 1977 letter is the only lead estimate available for flows of 80 and 135 gp=.
However, based en discussions with personnel at E&W and Southwest Research 2/ "For=ulas for Stress and Strain", 5th Edition, McGraw Hill, Inc., Ccpy Right 1975, Page 321, Ray =cnd J. Roark and Warren C. Young.
3/ "For=ulas for Stress and Strain", hth Edition, McGraw Hill, Inc., Copy Right 1965, Page 19h, Chapter 9, Table o, Raymond J. Ecark.
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R. W. REID, CHIEF November 2, 1977 GQL 1L96 Institute, we estimate that at flows of 550 to 3,000 gpm, the alternating torque loads vould be in the range of 15 to 65 of the steady state loads given in Item 2 above. Thus, the estimated alternating loads are as follows:
Flow Rate, c:n Alternatine Toroue. Ib-in 80 11,300 135 11,300 550 3ho 3,000 710 In su= mary, the loads acting on the pump shaft are calculated to be less than design allevable. The highest alternating loads are calculated to occur at 80 gym and as discussel in our letter of October 27, 1977, result in an upper limit alternating stress of 21,660 psi much below the normal design allevable of h5,000 psi. The maximum steady state loads are calculated to occur at 3000 gps, and result in a maxi =um torsional shear stress of 21,000 psi which is nuch less than a torsional yield stress of 62,500 psi.
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/ J. G. Herbein Vice Presidant JGH:WEP:tas 1492 185