ML17303A357

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Torsional Vibration Analysis KSV-20-T SN-7183-88 SO-0391.
ML17303A357
Person / Time
Site: Palo Verde Arizona Public Service icon.png
Issue date: 03/12/1987
From: Horne J
COOPER BESSEMER CORP.
To:
Shared Package
ML17303A352 List:
References
AM-3423, TAC-64398, NUDOCS 8704010605
Download: ML17303A357 (20)


Text

Cooper-Bessemer Reciprocating Products Division Cooper Industries, Inc.

Applied 'Mechanics Report AM-3423 Tor sional Vibration Analysis KSV-20-T'N-7183-88 S0-0391

.Bechtel .Power Corporation for Arizona Public Service Company Palo Verde Prepared by John M. Horne Manager Analytical and Compressor Engineering

,Gr ove Ci:ty, PA March 12, 1987 f gjpgpgOb05 870324 05QOO530 pgp pDOCK P..DR

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Scope This report covers the results of a torsional vibrati'on analysis of the subject engines which was originally performed in 1978. Attachment 1 to this report covers the results of' torsiograph test which was performed on one of the subject engines in August of 1978.

Attachment 2 covers additional analysis work done in February 1987 to address the reduction in diameter of the g9 crankpin in SN-7187.

Procedure

~ Resonant Holzer tables were developed using computer program FORTV installed on our Hewlett-Packard 1000 digital computer. Resonant str esses in the engine crankshaft and generator shaft were calculated for all significant multiples of the firing frequency within the operating envelope of the engine. Stimulation torques for the 1/2 through 10th orders of operating speed were calculated from actual indicator cards taken from similar engines. Normal energy balance methods were used to calculate 'the resonant stresses. The resonant Holzer tables are shown in figures 1 .through 3 of this report.

Results The results of this analysis are:

Mode I- 1459 cpm Qrder RPM Resonant Stress g ksi.

Crankshaft Generator Shaft 2 730 2.03 0 55 2-1/2 584 2 55 0.69 3 486 0.41 0. 11 3-1/2 417 1 ~ 19 365 0 0 4-1/2 324 4.69 1. 26 5 - 292 5. 13 1.38 5-1/2 265 2.54 0.68 6 243 0.08 6-1/2 222 0.66 0.18 7 208 0.28 7-1/2 195 0.07 8 182 0.20 8-1/2 172 0.10 9 162 0.03 9-1/2 154 0.34 10 146 1 ~ 27 0 34

0

,5 k

4L

'I gt k"

II 0

Mode II 4097 cpm 5-1/2 745 3.16 1. 41 6 683 0.18 0.08 6-1/2 630 0.56 0.25 7 585 0.91 0.40 7-1/2 546 0.06 8 512 0.64 0.29 8-1/2 482 0.09 9 455 0.07

'9-1/2 0.43 0'19 10 410 0 33 0.15 Mode III - 5969 cpm 10 597 0.06 0.09 The .str esses in the crankshaft are shown graphically in figure 4 of this report.

Discussion.

These resonant stress values are based on steady state operation at 231 BMEP at.

the corresponding resonant speed. During startup of 'the engine the full rated torque is .not developed until the engine .reaches rated,:speed, and the indivi;dual resonant speeds are passed through. very,guickly, so that full resonant. buildup does not occur. 'Ihus the torsional stress values during startup will be .well below the values shown above, and the full calculated values will develop only at speeds close to 600 rpm. These, stresses are well below the,DEMA limit of +5.0 ksi within, +10 percent of rated speed.

Conclusion All torsional vibration stresses in these engines, will be well below the acceptable limits for all modes of engine operation.

II

/

Johq M. Horne

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SV .20 APS 58 7 CPH 1ST HODE la MRSQ ZNERTZA AHPL ~ TORQUE STZFFNESS TWZST 251.190 15, 184 1, 0000 15.18 -12,45 -i. 2196 133, 960 8', 098 2., 2196 33,16 ,0346 959'.24'72.,00 254,078 15,359 2. 1850 66,72 .0864 253.350 15,315 2,0986 98,86 772.00 . 1'281 254,880 15,407 1.9706 129,22 772,,00 ,1674 254,.880 15.407 1,8032 157',00'si.

772.00 .2034

7 15,428 1.5998 68 730.26 ~ 2488 255,230'55,230 15,428 1,3510 202,53 772.00 2623 254.S80 15.407 1.0887 219. 30 772,00 ,2841

,;0 254'80 .8046 231. 70 772,00 .3001 15.407'5,315 253.350 ,5045 239.42 772,:00 ,3101 2 264,870 16,011 ,1944 242.'53 ssa.6o .4177 2342.0OO 141..571 -,2234 210'1 1914,00 , 1102, 4 10460.000 632.293 .,3336 ,oo

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<SV 20 APS

<:i; c'4 -AM 4!ED,., ii MAR .,

%987'7,4 CPM JO. WRSQ INERTIA AMPL TORQUE STXFFHESS TWIST 25i.i90 ii9,807 i.0000 ii9,8i -i2,45 -9, 6230 i33,960 63.893 io,6230 798,'54 959,24 8325 254,078 i2i.,i84 9,7905 i985,00 772.00 2.,57i2 253,350 i20.837 7,2i93 2857,36 772 00 F 3,70i2 254,880 i2i,567 3 ~ 5i8i '3285,04 772.'00. 4.2552 254,880 i2i,567 .7372 3i95.42 772.00 4 i391 255 230 i2i.734 -4.8763 260i..8i 730.26 3,5629 255,230 i2i.734 -8,4392 i574'8 772.00 2,0395 254.880 i2i,567 -i0.4787 300,,62 772.O0 ,3894 254.880 i2i,567 -S,o.sbsi -i020,57 772.00 -i,3220 253 '50 i20,837 -'9.,546 i -2i74 09 772,00 -2,8i62 2 .264.870 i26,33i -6,,7299 -30~4 580,6O -5,2089 2342.000 iii7.032 '-i,52iO -4723.30 i9i4.00 -2,4678 io460.ooo 4988.964 ,9468 ,06

8'24, AH MED,, ii'iAR,, i987

.SV 20 AfS 3

68. 7 CPH

'0. MRSQ INERTIA AHPL. TORQUE STIFFNESS TMIST 25i.i90 254,230 'i,0000 254,23 -i2 45 -20,420i i33 ~ 960 i35,58i 2i, 420i 3i58.39 959.24 3', 2926 254.078 257.i53 i8,i2'75 78i9.93 772.00 i'294 253.350 256.4i6 7.9980 9870,76 772.00 i2.7860 254,880 257,965 -4,7879 8635,65 772.00 ii,i86i 254 '80 257,965 -i5,9740 45i4,92 772.00 5,8483 255 230 258 3i9 -2i 8223 -ii22 20 730.26 -i.5367 255 '30 258,3i9 -20,2856 -6362.36 772.00 -8,24i4 254.880 257,965 -i2, 0442 -9469.35 772,00 -t2.2660 254 '80 257.965 .22i8 -94i2,i3 772,00 -i2.i9i9 253.350 i2,4i37 -6229.07 772.00 -8.0687 264 '70 268,0'76 20,4824 -738, 23 580.60 -i.27i5 3 2342.000 2370,345 2i,7539 50826,03 i9i4,00 26,5549

,4 i0460.000 i0586.596 -4.80i0 , i2

I

NU GAUIC IU DIET2GEN GRAPH f>APER DICTZGCN GORPQRATIDN ID X 10 PER INCH NAPC IH 4 ~,A

ENCLOSURE 3 KSV-20 VECTOR DIAGRAM

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~r/I ~i ~i >i7,7 Z, 'r

+ 7

II ENCLOSURE 4 UNIT 3 DIESEL GENERATOR "B" TESTS AND INSPECTIONS MARCH 13, 1987

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