Research Papers

A Metric to Evaluate and Synthesize Distributed Compliant Mechanisms

[+] Author and Article Information
Girish Krishnan

Department of Mechanical Engineering,
University of Michigan,
Ann Arbor, MI 48109 
e-mail: gikrishn@umich.edu

Charles Kim

Department of Mechanical Engineering,
Bucknell University,
Lewisburg, PA 17837 
e-mail: charles.kim@bucknell.edu

Sridhar Kota

Department of Mechanical Engineering,
University of Michigan,
Ann Arbor, MI 48109 
e-mail: kota@umich.edu

Contributed by the Design Automation Committee of ASME for publication in the Journal of Mechanical Design. Manuscript received November 29, 2011; final manuscript received September 23, 2012; published online November 21, 2012. Assoc. Editor: Shinji Nishiwaki.

J. Mech. Des 135(1), 011004 (Nov 21, 2012) (9 pages) Paper No: MD-11-1481; doi: 10.1115/1.4007926 History: Received November 29, 2011; Revised September 23, 2012

Compliant mechanisms with evenly distributed stresses have better load-bearing ability and larger range of motion than mechanisms with compliance and stresses lumped at flexural hinges. In this paper, we present a metric to quantify how uniformly the strain energy of deformation and thus the stresses are distributed throughout the mechanism topology. The resulting metric is used to optimize cross-sections of conceptual compliant topologies leading to designs with maximal stress distribution. This optimization framework is demonstrated for both single-port mechanisms and single-input single-output mechanisms. It is observed that the optimized designs have lower stresses than their nonoptimized counterparts, which implies an ability for single-port mechanisms to store larger strain energy, and single-input single-output mechanisms to perform larger output work before failure.

Copyright © 2013 by ASME
Your Session has timed out. Please sign back in to continue.



Grahic Jump Location
Fig. 1

Michell structure is the stiffest structure that supports the applied load with minimum volume. All the bars in the truss framework have the same stress.

Grahic Jump Location
Fig. 2

Examples in nature with uniform stress distribution: (a) A sea-anemone subjected to water currents [19], (b) a tree branch subjected to wind loads, (c) bending stress distribution at any given cross-section, and (d) determining the thickness of the beam with distance from the free end that uniformly distributes stresses along its length

Grahic Jump Location
Fig. 3

Comparison of three beams: (a) flexure with lumped compliance, (b) beam with uniform cross section, (c) tapered beam with uniform stress distribution, all having the same stiffness, and (d) comparison of the stress distribution throughout their length

Grahic Jump Location
Fig. 6

Cross-section refinement for a fixed-guided beam: (a) Initial beam with uniform cross-section, (b) optimized cross-section, and (c) optimized beam used in a double parallelogram flexure

Grahic Jump Location
Fig. 7

topology with deformed profile, and (c) stress distribution along the elements in the initial and optimized topology

Grahic Jump Location
Fig. 8

Evaluation of output work through transferred forces: (a) Input force producing input and output displacements, (b) transferred force applied in the opposite direction at the output restricts its displacement, and (c) output force versus displacement curve

Grahic Jump Location
Fig. 9

A beam with distributed load w N/m acting along its length

Grahic Jump Location
Fig. 10

Size optimization of a compliant gripper [24]: (a) Intial topology with uniform cross-section thickness, (b) optimized design with the cross-section alone allowed to vary, and (c) optimized design when cross-section thickness and undeformed beam curvatures are allowed to vary. The three designs have the same stiffness and amplification factor.

Grahic Jump Location
Fig. 11

Comparison of the optimized gripper designs from Fig. 10 in terms of (a) stress, (b) mechanical efficiency, and (c) total material volume

Grahic Jump Location
Fig. 12

An energy storage mechanism for a compliant stapler gun: (a) Problem specification with the initial design, (b) optimized design for high mechanical efficiency η and its deformed profile, (c) optimized design for maximum strain energy distribution np and its deformed profile, and (d) optimized design for maximum performance metric npm and its deformed profile




Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In