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Research Papers: Gas Turbines: Structures and Dynamics

Lateral Vibration Attenuation of Shafts Supported by Tilting-Pad Journal Bearing With Embedded Electromagnetic Actuators

[+] Author and Article Information
Henry Pizarro Viveros

e-mail: henry_piz@hotmail.com

Rodrigo Nicoletti

e-mail: rnicolet@sc.usp.br
Department of Mechanical Engineering,
School of Engineering of Sao Carlos,
University of Sao Paulo,
Trabalhador Sao-Carlense 400,
Sao Carlos 13566-590, Brazil

Contributed by the Structures and Dynamics Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received May 21, 2013; final manuscript received November 5, 2013; published online December 12, 2013. Assoc. Editor: Jerzy T. Sawicki.

J. Eng. Gas Turbines Power 136(4), 042503 (Dec 12, 2013) (12 pages) Paper No: GTP-13-1141; doi: 10.1115/1.4026038 History: Received May 21, 2013; Revised November 05, 2013

Hydrodynamic tilting-pad bearings with electromagnetic actuators are designed to take advantage of the load-carrying capacity of the hydrodynamic bearing together with the actuation capacity of the electromagnets. Hence, actuators can be downsized because they do not work as bearings as it is the case of magnetic bearings. In this work, one presents the numerical and experimental analysis of rotor vibration attenuation using a tilting-pad journal bearing with embedded electromagnetic actuators when proportional-derivative (PD) control is implemented. Experimental results in the frequency domain show reductions in shaft-vibration amplitude of 11% for the rotating speed of 600 rpm and 18% for the rotating speed of 1100 rpm, with good agreement of the mathematical model. The actuation capacity of the bearing in study is compared to the capacity of other active bearings in literature, showing that the present bearing is competitive in terms of specific control capacity.

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Figures

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Fig. 1

Hydrodynamic bearing with embedded electromagnetic actuators and tilting-pad. (a) Tilting-pad bearing; (b) pad with actuator (exploded view).

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Fig. 2

Test rig: (1) shaft, (2) self-aligning ball bearing, (3) tilting-pad bearing with embedded actuators, (4) electric motor, (5) universal joint, (6) inertial table, (7) proximity sensors, (8) excitation bearing, (9) hydraulic unit, (10) cooling system

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Fig. 3

Reference systems adopted and points of interest in the body

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Fig. 4

Flow chart of the algorithm for calculating the resultant forces on the shaft and on the pads

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Fig. 5

Test rig for measuring the force of the actuation system: (1) electromagnetic actuator, (2) cylinder, (3) load cell, (4) drive of the actuators

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Fig. 6

Electromagnetic force of the actuation system as a function of the applied reference voltage and frequency: comparison between experimental data and the fitted model. (a) Amplitude; (b) phase.

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Fig. 7

Position of the actuators in the bearing

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Fig. 8

Rotor-bearing frequency response functions in the passive condition (without control): excitation in Y direction (horizontal) in the rotating speeds of 600 and 1100 rpm—numerical and experimental results. (a) Y direction; (b) Z direction.

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Fig. 9

Scheme of the control and identification systems of the rotor-bearing system in the active condition (with control)

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Fig. 10

Rotor-bearing frequency response functions in the active condition (with control): excitation in Y direction (horizontal) in the rotating speed of 600 rpm—numerical and experimental results. (a) Y direction; (b) Z direction.

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Fig. 11

Rotor-bearing frequency response functions in the active condition (with control): excitation in Y direction (horizontal) in the rotating speed of 1100 rpm—numerical and experimental results. (a) Y direction; (b) Z direction.

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Fig. 12

Rotor unbalance response during run-up test (with control). (a) Response; (b) control signal.

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Fig. 13

Alternative design solution for the pads. (a) Body of the pad; (b) electromagnetic circuit.

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Fig. 14

Electromagnetic force of the E-shaped actuators as a function of the applied reference voltage and frequency: comparison between experimental data and the fitted model. (a) Amplitude; (b) phase.

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Fig. 15

Rotor-bearing frequency response functions in the passive and active conditions: excitation in Y direction (horizontal) in the rotating speeds of 600 and 1100 rpm—numerical results with E-shaped pads. (a) Y direction; (b) Z direction.

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Fig. 16

Specific control capacity of different types of active bearings

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