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TECHNICAL PAPERS

Suppression of Persistent Rotor Vibrations Using Adaptive Techniques

[+] Author and Article Information
Alex L. Matras

Department of Aerospace Engineering Sciences, University of Colorado, Boulder, CO 80309-0429Alex.Matras@colorado.edu

George T. Flowers

Department of Mechanical Engineering, Auburn University, Auburn, AL 36849-5341flowegt@auburn.edu

Robert Fuentes

 Boeing-SVS, Inc., Albuquerque, NM 87109-5858robert.j.fuentes@boeing.com

Mark Balas

Department of Electrical Engineering, University of Wyoming, Laramie, WYMBalas@uwyo.edu

Jerry Fausz

 Air Force Research Laboratory, Kirtland AFB, NM 87117-5776jerry.fausz@kirtland.af.mil

J. Vib. Acoust 128(6), 682-689 (Jun 23, 2006) (8 pages) doi:10.1115/1.2345668 History: Received February 20, 2004; Revised June 23, 2006

Recent work in the area of adaptive control has seen the development of techniques for the adaptive rejection of persistent disturbances for structural systems. They have been implemented and tested for large-scale structural systems, with promising results, but have not been widely applied to smaller-scale systems and devices. Rotor systems are subject to a variety of persistent disturbances (for example, due to mass imbalance, blade-pass effects) that occur at the rotor running speed or multiples of the running speed. The frequencies of such disturbance forces are generally known, but their magnitudes tend to vary over time. Adaptive techniques to counter the effects of such disturbances would appear to be a promising strategy in this regard. In order to assess the effectiveness of adaptive disturbance rejection for rotor applications and identify issues associated with implementation, an adaptive disturbance rejection control is developed, implemented, and tested for a magnetic-bearing-supported rotor system. Some conclusions and insights concerning the application of this method to rotor system vibration suppression are presented and discussed.

Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Simple 1-DOF mass model

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Figure 2

Controller schematic

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Figure 3

(a) Output response to 50Hz excitation with ADR control (ΔH=5I3×3). (b) Position response to 50Hz excitation with ADR control (ΔH=5I3×3).

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Figure 4

(a) Output response to 200Hz excitation with ADR control (ΔH=5I3×3). (b) Position response to 200Hz excitation with ADR control (ΔH=5I3×3).

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Figure 5

System response to 50Hz excitation with ADR control (ΔH=100I3×3)

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Figure 6

System response to 200Hz excitation with ADR control (ΔH=100I3×3)

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Figure 7

Gp gain for 200Hz excitations

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Figure 8

System response to 50Hz excitation with ADR control (ΔH=5I3×3, Kc=0)

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Figure 9

System response to 500Hz excitation with ADR control (ΔG=10, Kc=0)

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Figure 10

Gp gain for 200Hz excitations (ΔG=10, Kc=0)

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Figure 11

Photograph of experimental setup

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Figure 12

Schematic of experimental setup

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Figure 13

(a) Time trace of position, without ADR (30Hz running speed). (b) FFT of position, without ADR.

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Figure 14

(a) Time trace of position with ADR. (b) FFT of position with ADR.

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Figure 15

FFT of position without ADR (20Hz running speed)

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Figure 16

FFT of position with ADR

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