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TECHNICAL PAPERS

Electric-Hydraulic Actuator Design for a Hybrid Squeeze-Film Damper-Mounted Rigid Rotor System With Active Control

[+] Author and Article Information
Her-Terng Yau1

Department of Electrical Engineering, Far-East College, No. 49, Jung-Hwa Road, Hsin-Shih Town Tainan 744, Taiwan, R.O.C.pan1012@ms52.hinet.net

Chieh-Li Chen

Department of Aeronautics and Astronautics, National Cheng Kung University Tainan, Taiwan

1

Corresponding author.

J. Vib. Acoust 128(2), 176-183 (Aug 01, 2005) (8 pages) doi:10.1115/1.2149396 History: Received September 14, 2004; Revised August 01, 2005

When a squeeze-film damper-mounted rigid rotor system is operated eccentrically, the nonlinear forces are no longer radially symmetric and a disordered dynamical behavior (i.e., quasi-periodic and chaotic vibration) will occur. To suppress the undesired vibration characteristics, the hybrid squeeze-film damper bearing consisting of hydrostatic chambers and hydrodynamic ranges is proposed. In order to change the pressure in hydrostatic chambers, two pairs of electric-hydraulic orifices are used in this paper. The dynamic model of the system is established with the consideration of the electric-hydraulic actuator. The complex nonsynchronous vibration of squeeze-film dampers rotor-bearing system is demonstrated to be stabilized by such electric-hydraulic orifices actuators with proportional-plus-derivative (PD) controllers. Numerical results show that the nonchaotic operation range of the system will be increased by tuning the control loop gain.

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Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 2

The pressure distribution of HSFD in axis direction

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Figure 1

Cross section of a rigid rotor supported by a HSFD with active control

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Figure 12

Rotor trajectory of bearing center at s=6.0 with Kp=0.1

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Figure 11

The time responses of u¯(1) and u¯(2) at s=6.0 with Kp=0.01 changes to Kp=0.1 from nondimensional time ϕ=1570

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Figure 10

The time responses of rotor trajectories at s=6.0 with Kp=0.01 changes to Kp=0.1 from nondimensional time ϕ=1570

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Figure 9

The time response of u¯(1) and u¯(2) at s=6.0 with Kp=0.01

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Figure 8

The maximum Lyapunov exponent of rotor trajectory plotted as a function of the number of drive cycles at s=6.0 with Kp=0.01

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Figure 7

Aperiodic motion of bearing center at s=6.0 with Kp=0.01; (a) rotor trajectory; (b) Poincaré map in X(nT)-Y(nT) plane; (c) and (d) Time response of rotor trajectory

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Figure 6

The bifurcation diagram of bearing center trajectory with Kp=0.01

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Figure 5

The change of flow rate in ith oil chamber

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Figure 4

The flow rate control structure of HSFD (only show the 2th oil chamber)

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Figure 3

The pressure distribution of HSFD in rotational direction (−a⩽z⩽a)

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