ML17303A357
| ML17303A357 | |
| Person / Time | |
|---|---|
| Site: | Palo Verde  |
| 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 Torsional 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
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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 Crankshaft g ksi.
Generator Shaft 2
730 2-1/2 584 3
486 3-1/2 417 365 4-1/2 324 5
292 5-1/2 265 6
243 6-1/2 222 7
208 7-1/2 195 8
182 8-1/2 172 9
162 9-1/2 154 10 146 2.03 2 55 0.41 0
4.69
- 5. 13 2.54 0.08 0.66 0.28 0.07 0.20 0.10 0.03 0.34 1 ~ 27 0 55 0.69
- 0. 11 1 ~ 19 0
- 1. 26 1.38 0.68 0.18 0 34
0
,5 k
4L'I gt k"
II 0
Mode II 4097 cpm 5-1/2 6
6-1/2 77-1/2 8
8-1/2 9'9-1/2 10 745 683 630 585 546 512 482 455 410 3.16 0.18 0.56 0.91 0.06 0.64 0.09 0.07 0.43 0 33
- 1. 41 0.08 0.25 0.40 0.29 0'19 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
ik Il 0
- SV.20 APS
- 7 133, 960 254,078 253.350 254,880 254,.880 255,230'55,230 254.S80
,;0 254'80 253.350 2
264,870 2342.0OO 4
10460.000 58 7
CPH la MRSQ 251.190 1ST HODE ZNERTZA 15, 184 8', 098 15,359 15,315 15,407 15.407 15,428 15,428 15.407 15.407'5,315 16,011 141..571 632.293 AHPL ~
1, 0000 2., 2196
- 2. 1850 2,0986 1.9706 1,8032 1.5998 1,3510 1.0887
.8046
,5045
,1944
-,2234
.,3336 15.18 33,16 66,72 98,86 129,22 157',00'si.
68 202,53 219. 30 231. 70 239.42 242.'53 210'1
,oo
-12,45 959'.24'72.,00 772.00 772,,00 772.00 730.26 772.00 772,00 772,00 772,:00 ssa.6o 1914,00 TORQUE STZFFNESS TWZST
-i. 2196
,0346
.0864
. 1'281
,1674
.2034
~ 2488 2623
,2841
.3001
,3101
.4177
, 1102,
P II A,
il I
<SV 20 APS
<:i; c'4
%987'7,4 CPM JO.
WRSQ 25i.i90 i33,960 254,078 253,350 254,880 254,880 255 230 255,230 254.880 254.880 253 '50 2
.264.870 2342.000 io460.ooo INERTIA ii9,807 63.893 i2i.,i84 i20.837 i2i,567 i2i,567 i2i.734 i2i.734 i2i,567 i2i,567 i20,837 i26,33i iii7.032 4988.964 AMPL i.0000 io,6230 9,7905 7,2i93 3
~ 5i8i
.7372
-4.8763
-8,4392
-i0.4787
-S,o.sbsi
-'9.,546 i
-6,,7299
'-i,52iO
,9468 TORQUE STXFFHESS ii9,8i 798,'54 i985,00 2857,36
'3285,04 3i95.42 260i..8i i574'8 300,,62
-i020,57
-2i74 09
-30~4
-i2,45 959,24 772.00 772 F 00 772.'00.
772.00 730.26 772.00 772.O0 772.00 772,00 580,6O
-4723.30 i9i4.00
,06 TWIST
-9, 6230 8325 2.,57i2 3,70i2 4.2552 4 i391 3,5629 2,0395
,3894
-i,3220
-2,8i62
-5,2089
-2,4678
.SV 20 AfS 8'24, AH MED,, ii'iAR,, i987 3
- 68. 7 CPH
'0.
MRSQ 25i.i90 i33
~ 960 254.078 253.350 254,880 254 '80 255 230 255 '30 254.880 254 '80 253.350 264 '70 INERTIA 254,230 i35,58i 257.i53 256.4i6 257,965 257,965 258 3i9 258,3i9 257,965 257.965 268,0'76 3
2342.000 2370,345
,4 i0460.000 i0586.596 AHPL.
'i,0000 2i, 420i i8,i2'75 7.9980
-4,7879
-i5,9740
-2i 8223
-20,2856
-i2, 0442
.22i8 i2,4i37 20,4824 2i,7539
-4.80i0 TMIST
-20,420i
-i2 45 254,23 3i58.39 78i9.93 9870,76 8635,65 45i4,92 959.24 3', 2926 i'294 i2.7860 ii,i86i 5,8483
-i.5367
-8,24i4
-t2.2660
-i2.i9i9
-8.0687
-i.27i5 26,5549 772.00 772.00 772.00 772.00 730.26 772.00 772,00 772,00 772.00 580.60 i9i4,00
-ii22 20
-6362.36
-9469.35
-94i2,i3
-6229.07
-738, 23 50826,03
, i2 TORQUE STIFFNESS
I
NU GAUIC IU DIET2GEN GRAPH f>APER ID X 10 PER INCH DICTZGCN GORPQRATIDN NAPC IH 4 ~,A
ENCLOSURE 3 KSV-20 VECTOR DIAGRAM
3)g z)37
~r/I f
J
>zq 7~
~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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