Research Papers

Torsional Vibration Suppression by Roller Type Centrifugal Vibration Absorbers

[+] Author and Article Information
Yukio Ishida

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

Tsuyoshi Inoue

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

Tomohiko Fukami

 Toyota Industries Corporation, 2-1 Toyoda-cho, Kariya-shi, Aichi 448-8671, Japan

Motohiko Ueda

 Denso Corporation, 1-1 Showa-cho, Kariya, Aichi 448-8661, Japan

J. Vib. Acoust 131(5), 051012 (Sep 25, 2009) (10 pages) doi:10.1115/1.3147124 History: Received March 26, 2008; Revised January 27, 2009; Published September 25, 2009

Centrifugal pendulum vibration absorbers (CPVA) have been used for a long time as a method to suppress torsional vibration. Recently, roller type CPVA, that has a similar characteristic but simpler structure, have been investigated and started to be used in some automobile engines. However, only the linear dynamical characteristics of the roller type CPVA have been focused, and the influence of the nonlinearity affecting on vibration suppression has not been clarified. This study mainly focuses on the explanation of nonlinear dynamical characteristics of roller type CPVA. Especially, it clarifies the importance of consideration of nonlinearity in the design of the roller type CPVA, both theoretically and experimentally. Furthermore, the difference between the pendulum type CPVA and roller type CPVA are discussed from the viewpoint of the effect of vibration suppression.

Copyright © 2009 by American Society of Mechanical Engineers
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Figure 2

Position and forces of roller and rotor: (a) forces acting on the rotor and (b) forces acting on the roller

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Figure 3

Rolling motion of the roller

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Figure 4

Difference between pendulum type and roller type vibration absorbers

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Figure 5

Direction of friction force

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Figure 6

Time histories of driving torque T, moments MN, and MF

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Figure 7

Resonance curve for the case with centrifugal vibration absorber

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Figure 8

Time histories, orbit, and Poincaré map for steady state vibration and asynchronous vibration: (a) steady state vibration at ω=60.0 rad/sec and (b) asynchronous vibration at ω=64.0 rad/sec

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Figure 9

Spectra diagrams of superharmonic resonances (m=0.69 kg): (a) ω=21.5 rad/sec and (b) ω=34.5 rad/sec

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Figure 10

Influence of roller mass m: (a) m=0.40 kg, (b) m=0.68 kg, (c) m=0.70 kg, and (d) m=1.40 kg

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Figure 11

Influence of exciting torque: (a) case of m=0.69 kg and (b) case of m=1.40 kg

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Figure 12

System with rollers for Ω, 2Ω, and 3Ω

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Figure 13

Change of unstable solution for various value of the roller parameter R11

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Figure 14

System with rollers for Ω (with intentional variation of R11), 2Ω, and 3Ω

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Figure 15

Roller with stoppers

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Figure 16

Modeling of contact phenomenon: (a) restoring force and (b) damping force

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Figure 17

System with optimal condition of rollers and stoppers

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Figure 18

Experimental apparatus: (a) experimental setup, (b) rotor, and (c) roller pendulum

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Figure 19

Resonance curves of the case with centrifugal roller vibration absorbers (experiment): (a) two rollers and (b) four rollers

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Figure 20

Time histories of torsional vibration with centrifugal vibration absorbers ω=450 rpm (experiment)

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Figure 21

Influence of damping




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