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TECHNICAL PAPERS

Topology Synthesis of Compliant Mechanisms for Nonlinear Force-Deflection and Curved Path Specifications

[+] Author and Article Information
A. Saxena, G. K. Ananthasuresh

Department of Mechanical Engineering and Applied Mechanics, University of Pennsylvania, Philadelphia, PA 19104-6315

J. Mech. Des 123(1), 33-42 (Sep 01, 1999) (10 pages) doi:10.1115/1.1333096 History: Received September 01, 1999
Copyright © 2001 by ASME
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References

Figures

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Topological synthesis of a micro displacement amplifier. (a) Design specifications; F=500 μN (b) convergence history for topology optimization (c) full section design of the displacement amplifier (d) displaced profile; geometric advantage is 6.2 (e) optimal topology for F=100 μN.
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Design domain for two-point compliant crimper force-deflection synthesis
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Two-point force-deflection synthesis of a compliant crimper (a) optimal topology for design case I (b) convergence history
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Two-point force-deflection synthesis of a compliant crimper (a) optimal topology for design case II (b) convergence history
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Two-point force-deflection synthesis of a compliant crimper (a) optimal topology for design case III (b) convergence history
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Comparison of nonlinear force-deflection characteristics of the crimper designs ( Figs. 8910)
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Design specifications for prescribed curved output path
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(a) Design domain for compliant pliers (b) optimal pliers topology for specifications in Table 2 (c) output displacement trajectory for the optimal topology
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(a) Optimal pliers topology for specifications in Table 3 (b) output displacement trajectory for the optimal topology
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(a) Design domain for the floppy drive loading mechanism (b) optimal topology (c) output displacement trajectory
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Synthesis capabilities using nonlinear finite element analysis (a) quantitative accuracy for large deformations (b) prescribed nonlinear force-deflection specifications (c) curved output paths
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A bar with geometrically nonlinear deformation
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(a) Linear and nonlinear force-deflection relationship for the one-dimensional bar in Fig. 2 (b) tangent stiffness matrix, Kt and its constituents (E=2×105 N/mm2,A=250 mm2,yo=25 mm,l=2500 mm,Ks=1.35 N/mm)
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(a) Geometrically nonlinear analysis of a cantilever beam in Matlab for a vertical end force of −20 N. (b) Comparison of the output port deformation for a symmetric half of the deformed compliant crimper.
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Design sensitivity comparison with the displacement inverter example (a) input-output specifications (b) finite element mesh (c) comparison between analytical and finite difference sensitivities for the output displacement, maximum error=0.02%

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