Research Papers

Effect of Mesh Stiffness on the Dynamic Response of Face Gear Transmission System

[+] Author and Article Information
Zehua Hu

e-mail: huzehua0414@163.com

Jinyuan Tang

e-mail: jytangcsu@yahoo.com.cn

Siyu Chen

e-mail: csyd5053@yahoo.com.cn

Duncai Lei

e-mail: leiduncai2006@163.com
State Key Laboratory of High Performance
Complex Manufacturing,
Central South University,
Changsha, Hunan 410083, China

1Corresponding author.

Contributed by the Power Transmission and Gearing Committee of ASME for publication in the Journal of Mechanical Design. Manuscript received July 22, 2012; final manuscript received April 15, 2013; published online xx xx, xxxx. Assoc. Editor: Avinash Singh.

J. Mech. Des 135(7), 071005 (May 24, 2013) (7 pages) Paper No: MD-12-1371; doi: 10.1115/1.4024369 History: Received July 22, 2012; Revised April 15, 2013; Accepted April 29, 2013

The effect of mesh stiffness on the dynamic response of face gear transmission system combining with backlash nonlinearity is studied. First, a nonlinear time-varying (NLTV) and a nonlinear time-invariant (NLTI) dynamic models of face gear transmission system with backlash nonlinearity are formulated. The 6DOF motion equations of the face gear pair considering the mesh stiffness, backlash, contact damping and supporting stiffness are proposed. Second, the effect of mesh stiffness on the dynamic response of the face gear drive system is analyzed with the numerical method, where the mesh stiffness is expressed in two patterns as time-varying form and time-invariant form. According to the comparative study, some significant phenomena as bifurcation, chaos, tooth separation and occurrence of multijump are detected. The results show that different forms of mesh stiffness generate an obvious change on the dynamic mesh force.

Copyright © 2013 by ASME
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Fig. 1

Illustration of face gear transmission system: (a) Two-dimensional schematic figure and (b) three-dimensional schematic figure

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Fig. 2

Model of 6DOF face gear transmission system

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Fig. 3

Bifurcation diagram of face gear drive system (a) rotational speed 0–10,000 rpm; (b) rotational speed 2500–3500 rpm; and (c) rotational speed 5500–7500 rpm

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Fig. 4

Response curves of NLTV system

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Fig. 5

Phase plane of chaotic response at the rotational speed (6000 rpm)

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Fig. 6

Dynamic factor of face gear drive system

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Fig. 7

Dynamic mesh force of NLTV system and NLTI system

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Fig. 8

Frequency spectrum of velocity on line of action of NLTV system (a) and NLTI system (b)




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