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TECHNICAL PAPERS

Design of Vibration Absorbers for Structures Subject to Multiple-Tonal Excitations

[+] Author and Article Information
P. W. Wang

Department of Mechanical Engineering, National Chung Cheng University, Chia-Yi, 621, Taiwan, ROC

C. C. Cheng

Department of Mechanical Engineering, National Chung Cheng University, Chia-Yi, 621, Taiwan, ROCimeccc@ccu.edu.tw

J. Vib. Acoust 128(1), 106-114 (Nov 11, 2005) (9 pages) doi:10.1115/1.2159032 History: Received September 01, 2004; Revised November 11, 2005

The purpose of this paper is to introduce a systematic method of designing a vibration absorber that affects vibration attenuation at multiple frequencies. This vibration absorber is a nonprismatic beam with natural frequencies intentionally designed to coincide with the frequencies of excitation, e.g., the rotating speed of a rotary machine and its harmonic orders. Therefore, it can reduce the vibration response due to rotor eccentric, rotor shaft bending, mechanical looseness, etc. The thickness profile of the nonprismatic beam can be approximated discretely by a large amount of block masses. Each block mass behaves as an elastic structure member, and its thickness can be determined systematically using the impedance technique proposed in this paper. A design is given to demonstrate the methodology, and the result is experimentally validated.

Copyright © 2006 by American Society of Mechanical Engineers
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Figures

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Figure 1

Vibration absorber subjected to a harmonic force

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Figure 2

Schematic representation of a nonprismatic beam used as a vibration absorber

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Figure 3

Schematic representation of a nonprismatic beam subjected to a harmonic excitation

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Figure 4

Schematic representation of the force caused by the block mass acting on the nth beam segment of the beam

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Figure 5

A physical model equivalent to that of Fig. 3

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Figure 6

Comparison of block mass impedances with and without including the bending stiffness

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Figure 7

The design of vibration absorber with its thickness determined using the impedance model including the bending stiffness of block mass

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Figure 8

The design of vibration absorber with its thickness determined using the impedance model without including the bending stiffness of block mass

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Figure 9

Prototypes of vibration absorbers corresponding to the design shown in Fig. 7 and Fig. 8

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Figure 10

Schematic diagram of the experimental setup

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Figure 11

Frequency responses of the vibration absorbers shown in Figs.  78

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Figure 12

Performance test of vibration absorber

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Figure 13

Impedances of the block mass and the beam

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Figure 14

Influences of the block mass on the beam impedance

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Figure 15

(a) The block mass is stretched and compressed by a beam and (b) a model equivalent to (a)

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