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TECHNICAL PAPERS

Compliant Floating-Opposing-Arm (FOA) Centrifugal Clutch

[+] Author and Article Information
Nathan B. Crane

Department of Mechanical Engineering, 35-011, Massachusetts Institute of Technology, Cambridge, MA 02139e-mail: ncrane@mit.edu

Larry L. Howell, Brent L. Weight, Spencer P. Magleby

Mechanical Engineering Department, Brigham Young University, Provo, UT 84602

J. Mech. Des 126(1), 169-177 (Mar 11, 2004) (9 pages) doi:10.1115/1.1639378 History: Received November 01, 2001; Online March 11, 2004
Copyright © 2004 by ASME
Topics: Torque , Design
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References

Goodling,  E. C., 1974, “Fighting High Energy Costs with Centrifugal Clutches,” Mach. Des., 46(23), pp. 119–124.
St. John,  R. C., 1979, “Centrifugal Clutch Basics,” Power Transmission Design, 21(3), pp. 52–55.
Kellerman, R., and Fischer, J. L., 1976, “Centrifugal Clutch with One Piece Rotor,” United States Patent No. 3945478.
Dietzsch, G., Frers, G., Henning, K., and Lux, H., 1977, “Rotor for Centrifugal Clutch,” United States Patent No. 4016964.
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Roach, G. M., Lyon, S. M., and Howell, L. L., 1998, “A Compliant, Over-Running Ratchet and Pawl Clutch with Centrifugal Throw-Out,” Proceedings of the 1998 ASME Design Engineering Technical Conferences, DETC98/MECH-5819.
Roach, G. M., and Howell, L. L., 1999, “Evaluation and Comparison of Alternative Compliant Over-running Clutch Designs,” Proceedings of the 1999 ASME Design Engineering Technical Conferences, DETC99/DAC-8619.
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Howell,  L. L., and Midha,  A., 1994, “A Method for the Design of Compliant Mechanisms with Small-Length Flexural Pivots,” ASME J. Mech. Des., 116(1), pp. 280–290.
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Howell, L. L., 2001, Compliant Mechanisms, John Wiley and Sons, New York.
Ananthasuresh, G. K., Kota, S., and Gianchandani, Y., 1994, “A Methodical Approach to the Design of Compliant Mechanisms,” Solid-State Sensor and Actuator Workshop, Hilton Head Island, South Carolina, pp. 189–192.
Frecker,  M. I., Ananthasuresh,  G. K., Nishiwaki,  S., Kikuchi,  N., and Kota,  S., 1997, “Topological Synthesis of Compliant Mechanisms Using Multi-Criteria Optimization,” ASME J. Mech. Des., 119(2), pp. 238–245.
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Figures

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A FOA clutch in its undeflected position
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The PRBM of the clutch overlaid on the clutch geometry with the centrifugal forces shown
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(a) The applied forces and deflection path of a single shoe and its PRBM before contact. (b) The applied forces and deflected position of a pair of shoes and their PRBM after contact. (Deflections are shown much larger than actual deflections.)
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Explanation of variables used in the FOA clutch engagement model
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Parameters used in calculating TB factor for the FOA clutches. (a) External forces and appropriate position vectors. (b) Free body diagrams of the two links.
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Explanation of parameters used to define the prototype FOA clutches
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Clutch test setup. The tachometer measures the clutch speed. The clutch spins inside the stationary clutch drum. The output torque is measured by the reaction torque gauge mounted between the tailstock and the clutch drum. The clutch drum is mounted on the driving shaft with bearings.
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Torque capacity versus coefficient of friction for the FOA #3 clutch. The torque capacity approaches infinity when the coefficient of friction is at the critical value for self-locking.
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Drawing of general S-clutch configuration
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Two S-clutches from a Homelite Versatool string trimmer. The outer diameter of the clutches is 6.12 cm (2.41 inches).
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(a) The prototype FOA clutch for the string trimmer. (b) The FOA clutch mounted on the string trimmer.

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