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TECHNICAL PAPERS

Acoustic Fatigue of a Steam Dump Pipe System Excited by Valve Noise

[+] Author and Article Information
Suzanne Michaud

Centrale Nucleaire Gentilly, Becancour, Quebec G9X 3X3, Canada

Samir Ziada

Mechanical Engineering, McMaster University, Hamilton, Ontario L8S 4L7, Canada e-mail: ziadas@mcmaster.ca

Henri Pastorel

Institut de recherche d’Hydro-Quebec, Varennes, Quebec J3X 1S1, Canada

J. Pressure Vessel Technol 123(4), 461-468 (May 23, 2001) (8 pages) doi:10.1115/1.1400741 History: Received December 07, 2000; Revised May 23, 2001
Copyright © 2001 by ASME
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References

Howe, M. S., and Baumann, H. D., 1992, “Noise of Gas Flows,” Noise and Vibration Control Engineering, eds., L. L. Beranek and I. Vér, pp. 519–563.
Baumann,  H. D., 1984, “Coefficients and Factors Relating to the Aerodynamic Sound Level Generated by Throttling Valves,” Noise Control Eng. J., 22, pp. 1–6.
Baumann,  H. D., 1991, “Determination of Peak Internal Sound Frequency Generated by Throttling Valves for the Calculation of Pipe Transmission Losses,” Noise Control Eng. J., 36, pp. 75–83.
Floyd, J. D., 1995, “Understanding IEC Aerodynamic Noise Prediction for Control Valves,” Technical Monograph No. 41, Fisher Controls International.
Reethof, G., 1983, “Control Valve and Regulator Noise: Generation, Propagation and Prediction—Review,” NOISE-CON, 83 , pp. 9–20.
Reethof,  G., and Ward,  W. C., 1986, “A Theoretically Based Valve Noise Prediction Method for Compressible Fluids,” ASME J. Vib., Acoust., Stress, Reliab. Des., 108, pp. 329–338.
Graf, H. R., Ziada, S., Rohner, R., and Kaelin, R., 1997, “Verification of Scaling Rules for Control Valve Noise by Means of Model Tests,” Fluid-Structure Interaction, Aeroelasticity, Flow-Induced Vibration and Noise2 , eds., M. P. Paidoussis et al., ASME Pub. Ad-53-2, pp. 455–462.
Graf, H. R., Ziada, S., Rohner, R., and Kaelin, R., 1997, “Reduction of Control Valve Noise by Means of Model Tests,” Internoise97 , INCE: 14, Budapest, Aug.
Carucci, V. A., and Mueller, R. T., 1982, “Acoustically Induced Piping Vibration in High Capacity Pressure Reducing Systems,” ASME No. 82-WA/PVP-8, New York, NY.
Eisinger,  F. L., 1997, “Designing Piping Systems Against Acoustically-Induced Structural Fatigue,” ASME J. Pressure Vessel Technol., 119, pp. 375–383.
Eisinger, F. L., 1998, “Piping Systems Providing Minimal Acoustically-induced Structure Vibration and Fatigue,” United States Patent No. 5,711,350.
Nguyen-Duy, P., and Lanouette, C., 1985, “Analyse des défailances survenues à la tuyauterie de dérivation au condenseur, Gentilly 2,” Hydro-Quebec Research Institute, Varennes, Quebec, Canada.
Nguyen-Duy, P., and Lanouette, C., 1987, “Rupture d’une prise de tuyauterie UI-4331-509-II-20 de la centrale G-2,” Hydro-Quebec Research Institute, Varennes, Quebec, Canada.
Chiu, R., and Masood, Z., 1989, “Stress Analysis of Condenser Steam Discharge Piping in Gentilly Nuclear Power Station No. 2,” Technical Report No. CJ-10157, Stone & Webster Canada Ltd, Toronto, Canada.
Yung,  J. Y., and Lawrence,  F. V., 1985, “Analytical and Graphical Aids for the Fatigue Design of Weldments,” Fatigue Fract. Eng. Mater. Struct., 8, pp. 223–241.
Hajjar, Z., Blanchette, Y., Pastorel, H., Lanouette, C., and Nguyen-Duy, P., 1995, “Mesure des sollicitations et calcul de la vie en fatigue des conduites de dérivation de vapeur au condenseur 4331-507-II-20", 4331-510-II-20" et 4331-501-II-30" de la centrale nucléaire Gentilly 2,” Hydro-Quebec Research Institute, Varennes, Quebec, Canada.
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Ziada, S., 1996, “Systematic Methods to Reduce Control Valve Noise,” Technical Report No. STT.TB96.024, Sulzer Innotec Limited, Winterthur, Switzerland.
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Figures

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Layout of the steam dump piping system—1) fresh steam pipe (from steam generators); 2) isolation valves; 3) control valves; 4) 16 NPS pipes; 5) 20 NPS pipes; 6) 30 NPS pipes leading to condenser; S1 to S6: location of strain gages
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Geometry of the original valve—the seat diameter is 255 mm and the maximum valve lift is 100 mm
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Typical spectra of the dynamic axial strain at location S6—(a) original stem, total rms amplitude of strain=43.2 μ; and (b) modified stem, total rms amplitude=11.8 μ
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Typical spectra of the dynamic tangential strain at location S6—(a) original stem, total rms amplitude of strain=44.5 μ; and (b) modified stem, total rms amplitude=15.7 μ
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Comparison of average dynamic stress amplitude before (dark symbols) and after (open symbols) modifying the valve stem. Top, middle, and bottom figures for location S1, S5, and S6, respectively. ▪, □, axial stress; •, ○, tangential (hoop) stress.
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Stress cycle distributions for the axial stress at Site S5 and 52 percent valve lift showing the effect of low and high-pass filters. The filter used had a cut-off frequency of 1 kHz.
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Geometry of the modified stem—1) first stage of pressure reduction consists of 12 slits each 42 mm in width; 2) second stage consists of 408 orifices ranging from 11 to 17 mm in diameter
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Typical spectra of the noise generated inside the downstream pipe by the original and the modified stems. The results are obtained from small-scale model tests by means of pressurized air. Valve lift=100 percent, pressure ratio=3.
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Total acoustic efficiency (related to total sound power) of the original and the modified stems, given as a function of the pressure ratio. The results are obtained from small-scale model tests by means of pressurized air. Valve lift=100 percent.
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Amplitude of vibration velocity (rms) measured on the coupling block of the valve stem and in the radial direction. ♦, original stem; ○, two-stage stem; ▵, single-stage stem.
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Comparison of average dynamic stress amplitude on the pipe, with different stems in the valve. Location S5, axial stress. ○, original stem; □, two-stage stem; ▵, single-stage stem.

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