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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

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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