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Research Papers

Vibration Suppression of Rotating Machinery Utilizing Discontinuous Spring Characteristics (Stationary and Nonstationary Vibrations)

[+] Author and Article Information
Yukio Ishida

Department of Mechanical Science and Engineering, School of Engineering, Nagoya University, Nagoya, Aichi 464-8603, Japanishida@nuem.nagoya-u.ac.jp

Jun Liu

Department of Mechanical Science and Engineering, School of Engineering, Nagoya University, Nagoya, Aichi 464-8603, Japanliu@nuem.nagoya-u.ac.jp

J. Vib. Acoust 130(3), 031001 (Apr 03, 2008) (7 pages) doi:10.1115/1.2889919 History: Received February 07, 2006; Revised October 26, 2006; Published April 03, 2008

In rotating machinery, resonance phenomena occur with large amplitude in the vicinities of the major critical speeds. In this paper, a new vibration suppression method utilizing a discontinuous spring characteristic is proposed. This spring characteristic is achieved using additional springs with preload. This method has the following advantages. (1) In designing these additional springs, we need not adjust their parameter values to the optimal ones, which are determined by rotor stiffness and the system damping. (2) The amplitude of vibration can be suppressed to any desired small level. (3) This method is also effective for nonstationary vibration. Although the method has a disadvantage that an almost periodic motion occurs above the major critical speed, two countermeasures are proposed to diminish it. The characteristics of the vibration suppression are demonstrated theoretically and experimentally.

Copyright © 2008 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Theoretical model: (a) state of rest and (b) whirling motion

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Figure 2

Discontinuous spring characteristics in the x-direction

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Figure 3

Without a preload in additional spring

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Figure 4

Resonance curves with and without additional springs

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Figure 5

System with additional spring preloaded

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Figure 6

Time histories: (a) almost periodic motion and (b) steady-state vibration

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Figure 7

Case with large damping coefficient C2

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Figure 8

Case with a directional difference in stiffness

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Figure 9

Case with a directional difference in clearance

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Figure 10

Experimental setup

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Case with no additional spring (experimental result)

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Figure 12

Case with equal additional springs (δ=2mm, experimental result)

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Figure 13

Case with equal additional springs (δ=1mm, experimental result): (a) resonance curve, (b) almost periodic motion (ω=510rpm), and (c) stationary motion (ω=643rpm)

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Figure 14

Case with a directional difference in stiffness (δ=1mm, experimental result)

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Figure 15

Case with a directional difference in clearance (δ=1mm, experimental result)

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Figure 16

Nonstationary response in a system with directional difference in stiffness

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