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TECHNICAL PAPERS: Gas Turbines: Structures and Dynamics

Frequency Response Analysis of an Actively Lubricated Rotor/Tilting-Pad Bearing System

[+] Author and Article Information
Rodrigo Nicoletti

Ford Motor Co., Complexo Industrial Ford Nordeste, Camacari 42810-900, Brazile-mail: rnicolle@ford.com

Ilmar Ferreira Santos

Department of Mechanical Engineering, Technical University of Denmark, Lyngby 2800, Denmarke-mail: ifs@mek.dtu.dk

J. Eng. Gas Turbines Power 127(3), 638-645 (Jun 24, 2005) (8 pages) doi:10.1115/1.1850940 History: Received October 01, 2003; Revised March 01, 2004; Online June 24, 2005
Copyright © 2005 by ASME
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References

Santos, I. F., 1994, “Design and Evaluation of Two Types of Active Tilting-Pad Journal Bearings,” IUTAM Symposium on Active Control of Vibration, Bath, England, “Mechanical Engineering Publications Limited, London,” pp. 79–87.
Santos,  I. F., and Russo,  F. H., 1998, “Tilting-Pad Journal Bearings With Electronic Radial Oil Injection,” ASME J. Tribol., 120(3), pp. 583–594.
Santos,  I. F., and Nicoletti,  R., 1999, “THD Analysis in Tilting-Pad Journal Bearings Using Multiple Orifice Hybrid Lubrication,” ASME J. Tribol., 121(4), pp. 892–900.
Santos,  I. F., and Nicoletti,  R., 2001, “Influence of Orifice Distribution on the Thermal and Static Properties of Hybridly Lubricated Bearings,” Int. J. Solids Struct., 38(10–13), pp. 2069–2081.
Nicoletti,  R., and Santos,  I. F., 2003, “Linear and Non-Linear Control Techniques Applied to Actively Lubricated Journal Bearings,” J. Sound Vib., 260(5), pp. 927–947.
Santos,  I. F., and Scalabrin,  A., 2003, “Control System Design for Active Lubrication With Theoretical and Experimental Examples,” ASME J. Eng. Gas Turbines Power, 125(1), pp. 75–80.
Wu, W., and Pfeiffer, F., 1998, “Active Vibration Damping for Rotors by a Controllable Oil-Film Bearing,” Proc. of IFToMM International Conference on Rotor Dynamics, Darmstadt, Germany, “Vieweg-Verlag Braunschweig, Wiesbaden,” pp. 431–443.
Bently, D. E., Grant, J. W., and Hanifan, P., 1999, “Active Controlled Hydrostatic Bearings for a New Generation of Machines,” ASME Paper No. 2000-GT-354.
Santos,  I. F., and Watanabe,  F. Y., 2003, “Feasibility of Influencing the Dynamic Fluid Film Coefficients of a Multirecess Journal Bearing by Means of Active Hybrid Lubrication,” J. Brazilian Soc. Mech. Sci. Eng.,15(2), pp. 154–163.
Santos,  I. F., and Watanabe,  F. Y., 2004, “Compensation of Cross-Coupling Stiffness and Increase of Direct Damping in Multirecess Journal Bearings Using Active Hybrid Lubrication, Part I: Theory,” ASME J. Tribol., 126(1), pp. 146–155.
Lund,  J. W., 1964, “Spring and Damping for the Tilting Pad Journal Bearings,” ASLE Trans., 7(4), pp. 342–352.
Lund, J. W., and Thomsen, K. K., 1978, “A Calculation Method and Data for the Dynamic Coefficients of Oil-Lubricated Journal Bearings,” Topics in Fluid Film Bearing and Rotor Bearing System Design and Optimization, S. M. Rhode, P. E. Allaire, and C. J. Maday (eds.), ASME, New York, pp. 1–28.
Springer, H., 1980, “Dynamische Eigenschaften von Gleitlagern mit beweglischen Segmenten,” VDI-Berichte, N. 381, pp. 177–184.
Someya, T., 1989, Journal Bearing Data Book, Springer-Verlag, Berlin.
Allaire,  P. E., Parsell,  J. A., and Barret,  L. E., 1981, “A Pad Perturbation Method for the Dynamic Coefficients of Tilting Pad Journal Bearings,” Wear, 72, pp. 29–44.
Santos, I. F., Scalabrin, A., and Nicoletti, R., 2001, “Ein Beitrag zur Aktiven Schmierungstheorie,” Schwingungen in rotierenden Machinen VI, H. Irretier, R. Nordmann, and H. Springer, eds., Vieweg Verlag, Vol. 5, pp. 21–30.
Santos,  I. F., Nicoletti,  R., and Scalabrin,  A., 2004, “Feasibility of Applying Active Lubrication to Reduce Vibration in Industrial Compressors,” ASME J. Eng. Gas Turbines Power, 126(4), pp. 848–854.
Parsell,  J. A., Allaire,  P. E., and Barret,  L. E., 1983, “Frequency Effects in Tilting Pad Journal Bearing Dynamic Coefficients,” ASLE Trans., 26(2), pp. 222–227.

Figures

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Actively lubricated tilting-pad bearing and oil injection system
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Schematic view of the injection system connected to one of the bearing pads
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Active lubricated bearing test rig: (1) electric motor, (2) self-aligning ball bearing, (3) rigid shaft; (4) excitation bearing, (5) eddy current probes, (6) active lubricated tilting-pad bearing and (7) servo valves
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Points of acting forces (R ,O ,E ,H ) and auxiliary reference frames used in the model of the rigid shaft-disk subsystem
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Oil film coefficients Kyy,Kzz,Dyy,Dzz of the TPJB under conventional lubrication condition as a function of the excitation frequency ω and two Sommerfeld numbers So corresponding to the angular velocities of Ω=900 rpm (15 Hz) and Ω=1800 rpm (30 Hz)
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Frequency response functions of the rotor-bearing system in the passive case for Ω=900 rpm (15 Hz), horizontal direction
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Frequency response functions of the rotor-bearing system in the Passive case for Ω=1800 rpm (30 Hz), horizontal direction
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Active oil film force as a function of the input signal in the servo valve (y direction) in a quasi-static condition test when the rotor operates at the angular velocity of 1200 rpm (20 Hz)
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Experimental FRFs of the rotor-bearing system in the passive and active cases for Ω=900 rpm (15 Hz), horizontal direction
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Experimental FRFs of the rotor-bearing system in the passive and active cases for Ω=1800 rpm (30 Hz), horizontal direction
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Comparison between theoretical and experimental FRFs of the rotor-bearing system in the active case for Ω=900 rpm (15 Hz), horizontal direction
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Comparison between theoretical and experimental FRFs of the rotor-bearing system in the active case for Ω=1800 rpm (30 Hz), horizontal direction
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Oil film coefficients K̄yy,K̄zz,D̄yy,D̄zz of the TPJB under active lubrication condition as a function of the excitation frequency ω, proportional gain GP, and Sommerfeld number So corresponding to the angular velocity of Ω=900 rpm (15 Hz)
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Oil film coefficients K̄yy,K̄zz,D̄yy,D̄zz of the TPJB under active lubrication condition as a function of the excitation frequency ω, proportional gain GP and Sommerfeld number So corresponding to the angular velocity of Ω=1800 rpm (30 Hz)

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