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Research Papers

Analysis of the Dynamic Behavioral Performance of Mechanical Systems With Multi–Clearance Joints

[+] Author and Article Information
S.M. Megahed

Mem. ASMEmegaheds2@asme.org

A.F. Haroun

Mem. ASMEAharoun@eng.cu.edu.egMechanical Design & Production Engineering Department, Faculty of Engineering,  Cairo University, 1 El Gamma St., Giza 12613 – EgyptAharoun@eng.cu.edu.eg

J. Comput. Nonlinear Dynam 7(1), 011002 (Jul 22, 2011) (11 pages) doi:10.1115/1.4004263 History: Received December 20, 2010; Accepted May 16, 2011; Published July 22, 2011; Online July 22, 2011

In this investigation, the effect of revolute joints’ clearance on the dynamic performance of mechanical systems is reported. A computation algorithm is developed with the aid of SolidWorks/CosmosMotion software package. A slider-crank mechanism with one and two clearance-joints is studied and analyzed when working in vertical and in horizontal planes. The simulation results point out that the presence of such clearance in the joints of the system understudy leads to high peaks in the characteristic curves of its kinematic and dynamic performance. For a multiclearance joints mechanism, the maximum impact force at its joints takes its highest value at the nearest joint to the input link. This study also shows that, when the mechanism works in horizontal plane, the rate of impacts at each clearance-joint increases and consequently the clearance-joints and actuators will deteriorate faster.

Copyright © 2012 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

(a) Massless link approach, (b) Spring–damper approach, and (c) Contact force approach

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Figure 2

(a) Revolute joint with clearance (b) Joint contact forces

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Figure 3

Damping coefficient versus penetration

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Figure 4

Flow chart of the computational algorithm

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Figure 5

Slider-crank mechanism with two clearance-revolute joints

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Figure 6

Slider displacement deviation from the ideal case at ω = 480 rpm (Vertical plane case)

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Figure 7

Slider displacement deviation from the ideal case at ω = 480 rpm (Horizontal plane case)

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Figure 8

Slider velocity at ω = 480 rpm (Vertical plane case)

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Figure 9

Slider velocity at ω = 480 rpm (Horizontal plane case)

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Figure 10

Slider acceleration at ω = 480 rpm (Vertical plane case)

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Figure 11

Slider acceleration at ω = 480 rpm (Horizontal plane case)

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Figure 12

Applied crank torque at ω = 480 rpm (Vertical plane case)

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Figure 13

Applied crank torque at ω = 480 rpm (Horizontal plane case)

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Figure 14

Normal contact force on the c-cr joint at ω = 960 rpm

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Figure 15

Path of the journal center relative to the bearing center at ω = 480 rpm in horizontal plane: (a) s–cr joint, and (b) c–cr joint

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Figure 16

Path of the journal center relative to the bearing center at ω = 480 rpm in horizontal plane: (a) s–cr joint, and (b) c–cr joint

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Figure 17

Normal contact force on the c–cr joint at ω = 480 rpm and at ω = 960 rpm (Vertical plane case)

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Figure 18

Normal contact forces at c-cr and s-cr clearance-joints at ω = 960 rpm in horizontal plane

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