ML20083K724

Tests for Decay Heat Pumps 1A & 1B Baseline Data by External Accelerometer.Data Provides Sound Basis for Future Pump Analysis at End of Decay Heat Svc Cycle to Allow for Maint Planning

ML20083K724
Person / Time
Site:	Crystal River
Issue date:	08/30/1978
From:	FLORIDA POWER CORP.
To:
Shared Package
ML20083K722	List: ML20083K710 ML20083K724 ML20083K728
References
NUDOCS 7901300121
Download: ML20083K724 (42)

Text

- _ . .

f FLORIDA POWER CORPORATION

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CRYSTAL RIVER - 3 DECAY HEAT PUMPS 1A & IB BASELINE DATA 4

BY EXTERNAL ACCELEROMETER J. M. HUZD0VICH SUPERVISORY ENGINEER REACTOR DIAGNOSTIC SERVICES NUCLEAR SERVICE DEPARTIEIT AUGUST 30, 1978 THE BAECOCE AND WILCOX CCMPANY e

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I 1.0 References and Attachments 2.0 Introduction 3.0 Data Analysis 1

4.0 Su=ary i

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3.0 ?,eferences and

Attachment:

1.1 FPC, CR-3, Decay Heat Pump la Vioration Analysis by External Accelerczeter, J. M. !!u:::cvien, August 25, 1978.

1.2 Vibration Tolerances for Industry, ASME 67-PEM-14, presented by R. L. Baxter and D. L. Bernnard.

1.3 Attachment 1 - Baseline Data for Decay Heat Pumps lA and 13.

1.4 Attach =ent 2 - Bearing Frequencies.

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2.0 Jili30DUCTIO:!

Reference 1.1 provided the first spectral data regarding both DH Pu=ps at CR-3. Conclusions were drawn from these cata regarding the A Pu=p performance and reco==endations were made to i= prove that pu=p's operating condition, namely, bearing replace =ent. The A-Pu=p has been overhauled, with new bearings being installed. The B-Pu=p has undergone a similar overhaul to per=1t inspections. Since both pu=ps have now accu =ulated run-in ti=e (A-Pu=p: Approx. 150 hours0.00174 days <br />0.0417 hours <br />2.480159e-4 weeks <br />5.7075e-5 months <br />, B-Pu=p: Approx. 50 hours5.787037e-4 days <br />0.0139 hours <br />8.267196e-5 weeks <br />1.9025e-5 months <br />), baseline data have been taken to document their initial performance for future reference and analysis.

To insure that baseline data are used properly, the A & B Pump baseline data should only be co= pared to data taken under si=ilar operating conditions as listed for each pump in Attach =ent 1. Fcr example, the criginal data acquired in Reference 1.1 were obtained under various conditions, however, all at approximately 100 F. Consequently, the baseline data =ay not be directly cc= pared to the data of Reference 1.1.

If, however, the operating conditions in Attachment ~1 are duplicated at the next DH Service Cycle, spectral data acquired at that time can be co= pared directly to the baseline' data for analysis.

The baseline data was acquired at the monitoring points depicted in Figur'e 1. It was reviewed for frequency content'and noise source ,

identification, then reduced by deter =ining the G-RMS level for the do=inant rotational, pu= ping, bearing, and other significant. frequency

. peaks. A tabular listing for both pumps is in Attach =ent 1. 'Also listed for each pu=p .in Attachment 1 are the operating conditions and the'overall signal noise levels in MV-RMS. Figure 2 depicts a typical signal channel utilized in the baseline data acquisition.

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2 3.0 DATA ANALYSIS The analysis consisted of comparing the rotational, pumping, bearing, and other significant frequencies to generally accepted industry standards as found in Reference 1.2. The principle standard used to evaluate these baseline data was the IRD Mechanalysis " General l Machinery Vibration Severity Chart".

• The bearings on both machines are operating in the very good to very smooth region, with velocities of 0.028 in/Sec or less measured for all bearing frequencies. Since there are numerous frequencies for each bearing, the ' individual velocities are not tabulated in this report.

However, the frequencies are listed in Attachment 2 along with a copy of I the spectra for position 5 for each pump. Performing a direcc spectra comparison is less time consuming'and is just as effective as ce=parire velocity values.for obvious noise level changes.

i The highest velocity level measured on either pu=p at the fundamental rotational fpequency was 0.021 in/Sec indicating a very good balance condition. However, at twice the rotational frequency, (especially on the A Pump), an unusually high level is observed with the largest readings.

measured at the second flange off the pc=p on the suction and discharge piping. The maximum velocity level obtained is 1 91 in/Sec, wh4.ch was measured at the discharge flange. These high levels appear to be caused by a piping system resonance with some additional affect possibly contributed by 60 HZ electrical noise and cold-to-hot alignment changes.

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3.0 DATA MJALYSIS (Continued)

In additien, locations 12 and 6 which are axial, also :now high levels.

This is believed to be cue to the fact that these locations are influenced by the axial loadir; transmitted from the shaft through the bearings.

Since these pumps are end suction type, they do experie=ce axial loadir.g.

While these readin5s could indicate that the pu=p is ru:ning rough, they appear to be cor,e indicative of piping influence and nct a pump anc=oly.

The levels associated with the pumping frequencies indicate a fair condition for both pumps. The B Pu=p exhibits a velocity of 0.135 in/See at the worst location, and the A pump exhibits a velocity of 0.106 in/See at its worst location. The' harmonics of the vane rate T148 HZ) decreased as expected indicating no unusual resonances on the pu=p.

The other frequencies listed for A Pump are attrib:: table to .he piping system. This includes the 1375 HZ frequency discussed in Section 3.2 of Reference 1.1. These noises were traced to the DH heat exchanger valving and were measured on the DH Pu=p suction valve and secord flange cff the pump discharge (position 10) at higher levels than elsesisere on the pump.

They show up as the highest noise levels on the pump due to it being an anchor point in the piping system. No . resonant phenomena was observed being excited by these frequencies on the pump. 'Ihis is based on the observation that the levels decreased when ceasured directly on the pu=p casing or bearing housing. The same, can be 'said for the.1690 HZ peak on

- B Pump.

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4 4.0 StaiMA?.Y  !

1he baseline data presented in this report shculd provice j a sound basis for future pu=p analysis at the end of a decay. heat t serv' ice cycle in order to allow for =aintenance planning. We dc=inant

. influence of the piping system cannot be taken lightly.

Its affect can influence the data in the 1-2 KHZ range for each pucp and as the data

. indicates for A Pu=p, even at lower frequencies. At present, the rotational, pumping, and bearing frequencies associated with each pt.=p indicate an acceptable condition for operation. To further clarify the s'ource of the high 60 Hz' level on the "A" Pump, however, it is reco== ended i that.a hot alignm6nt check be performed.

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SPECTRUM ANALYZER > X-Y PLOTTER -

1he signal channel was calibrated. by attaching the Accelerometers to an NBS traceable Unholtz-Dickie portable shaker and inserting 1 G-RilS through the chain and checking the 1 volt RMS out of' the

• charge amp. This was done on all channels' prior to data acquisition.

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FIGURE 2 1

I ATTACEiENT 1 BASELINE DATA FOR DECA'l HEAT TUMPS 1A AND 15 O

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TABLE 1-1 l l

A. FREQUENCY LEVELS IN G-RMS  !

l PUMP A, BASELINE 8-29-78 CHANNEL:

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FREOUENCY 5 12 6 8 9 10 SUCT VLV i

Rotational 29.6 .0036 . 003 .0018 .003 .0054 .01 NA

59 2 .021 . 3 .0042 1.26 1.29 1.3

'88.8 .039 . 012 .015 .0051 .024 .012 1

Pumping, 148 .18 .-17 .08 .13 .15 .08 296 .06 . 013 .045 .09 .12 .058 F

444 .042 , .0069 .022. .07 .009 .07

, 592 .03 .015 .040 .042 .024 .022 Other 1280 1.29 .6 2.2 1.2 .48 6.8 .4 1430 .339 .27 1.26 1.2 .39 1.3 1.6 B. TOTAL NOISE LEVEL MV-Rv3 l

5 - 1780 NOTE: These total noise level 12 - 1375 values are heavily influenced l ,

6 - 2320 by piping system response 8 - 3000 and do not necessarily reflect 9 - 1800 on the condition of the pu=p.

10 - 6900 ,

C. PUMP CONDITION - RECIRC 'ID VESSEL Pressure Suction -240 PSIO Fluid Temperature - 170 0F Discharge -390 PSIG Flow - 3000 gpm

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W9CCT-2 A. FREQUE!!CY LEVELS IN 0-RMS PUMP B, BASELINE 8-29-78 CHA!.'!!EL:

• FREQUENCY 5 12 6 8 9 10 Rotational 29.6 .009 .003 .0015 .003 .0072 .0035 59 2 .012 .3 .016 .32 .28 .033 88.8 .0032 .0033 .0022 .0073 .0069 .004 Pumping 148 .23 .12 .10 .07 .16 .14 296 .01 .03 .03 .17 .057 .14 444 .012 .0038 .022 .054 .011 .023 592 .013 .062 .036 .07 .036 .082 Other 1690 .24 5 1.59 2.53 2.16 4.0

5. 'IOTAL NOISE LEVEL MV-RMS 5 - 425 NOTE:

These total noise level 12 - 620 values are heavily influenced 6 - 1710 by piping system response 8 - 2800 and'do not necessarily reflect 9 - 2200 on the condition of the pump.

10 - 4000 ,

C. PUMP CONDITION - RECIRC TO VESSEL -

Pressure Suction -240 PSIG- Fluid Temperature - 170 0F Discharge -390 PSIG Flow - 3000 gpm I

01

l ATTACHMENT 2 EEARING FREQUENCIES e e e

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Baaring frequencies P2 dial 5214C3 10 Balls Thrust 7313B 12 Balls

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Badial Bearing - 5214C3 B = 2.76 D = 4.92 i r' E = 1/2 (B + D) = 3.84 d = 11/16 = .688 N = 10 -

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ff= 29.6 fo=f r f

- 2(1 - d COSa) = 29.6 (1 .688 COS 35*) = 14.8 (1 .147)

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fE0 = 12.62 HZ IEI " ff (1 + d COSa) = 14.8 (1,147) 2 E fEI " 10*I fB=Ef f(1 - d COS 2 2 a) = 82.60 (1 .022) fB = 80.78 HZ ,

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B = 2.56 D = 5.51 E = 4.04

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EI = 14.8 (1 + d COSa) fEI " 1

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'f 3 = 14.8 (E) (1 - dj COS a) = 14.8 (4.31) (1 .032) f 3= 61.75HZ (d) ( E )

f B0 " EO B0 "

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.7313B THRUST HARMONICS C $s ,' 1 2, 3 4 5 6 7 8 9 12.17 24.34 36.51 48.68 60.85 -73.02 '85.19 97.36 109.53 17.43 34.86 52.29 69.72 87.15 104.58 122.01 139.44 156.87 61.75 123.5 185 247 308 370 432 494 555 146 292 438 584 730 876 1022 1168 1314

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209 418 627 836 1045 1254 1463 1672 ISE1 5214C3 RAD 12.62 25.24 37.86 50.48 63.1 75.72 8S.34 100.96 '113.58 16.98 33,96 50.94 67.92 84.9 101.8E 138.86- 135.84 152.82 80.78 ,161 242 323 403 464 .

565 64 6 727 128.2 252 ~378 504 631 757 '883 1009 1135

[-. 169.8 340 509 679 .849' 3018 1188 - 1358- 1.A.V

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, . .r 2-3 Bearing Frequency Calculations iloriencla ture : ' '

B = Bore, inside bearing diameter (inches).- . . . d - Ball diameter (Inches)

D = Outside bearing diameter (inches) '

N = Number of balls ~

E = Fitch diameter = 1/2 (BFD) (inches) o - Contact angle (degrees) f = Fundamental rotational frequency ~

f (RPH/60) (liZ)

Formulas .

Frequency _(II7.) Apfroximate Contact Angle Remark 9.

Cage. to outer fg (1-d/E) fg (1-d_ COSa) Fundamental cage (train) frequency when ring frequency 2 E the inner ring is rotating and the outer f '

ring is stationary.

(fEO)

Cone to loner f 7(1+d/E) f Fundamental cage (train) frequency when rine, frcsuency" f (1+d/E'COSa) the inner ring is stationary and the outer 7 f ring is rotating.

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Td- F this frequency.

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F0 fnr.cr hallpass Nf EI Frequencies generated due to an irregularity ll(F.T (FBI) n the stationary raceway.

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, P.O Sci 120, L,r.cr.tu.;;. .a. . . ..

Teie:nce.e> 604; 254 51 :

October 13, 1977 Mr. R. S. Burns .

CR-3 Engineer 1ug Manager Florida Pcuer Corporation P.O. Box 14342 St. Petersburg, Florida 33733 Subj ec't : Decay Heat Punp Operation Reference - Letter, RS Burns from GT Fairburn, dated 7/12/77

Dear Mr. Burns:

This letter is to advise you that B&W.has revised the limits on the operation of the Decay Heat Pump'during the recirculation mode (85/100) spm from 30 minutes continuously and 60 minutes total in any 12 month period to 15 hours1.736111e-4 days <br />0.00417 hours <br />2.480159e-5 weeks <br />5.7075e-6 months <br /> continuously 9 and 80 hours9.259259e-4 days <br />0.0222 hours <br />1.322751e-4 weeks <br />3.044e-5 months <br /> total within the life of the pump.

Th'is revision is based on the results of a design review meeting at Worth-ington and their' authorization of operation limits of these Decay Heat Pu=ps.

Very truly yours,

4. J. Ja /~---

G. T. Fairburn Service Manager GTF/hh I cc: EC Simpson S Laing i SP Melancon l~

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