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TECHNICAL PAPERS

Effect of Pad/Caliper Stiffness, Pad Thickness, and Pad Length on Thermoelastic Instability in Disk Brakes

[+] Author and Article Information
Dale L. Hartsock, James W. Fash

Ford Motor Company, Dearborn, MI 48121-2053

J. Tribol 122(3), 511-518 (Aug 19, 1999) (8 pages) doi:10.1115/1.555394 History: Received September 29, 1998; Revised August 19, 1999
Copyright © 2000 by ASME
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References

Figures

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Drawing of typical automotive brake
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Rotor deformed shape due to antisymmetric hot spots
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Representation of the model used by Lee and Barber and how the model changes by modifying the elastic modulus and coefficient of friction
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(a) Model used to calculate the deflections for the rigidly supported pad, configuration 1. (b) The model and boundary conditions used to determine the deflections in the pad with an attached backing plate that was either rigidly supported or unsupported. These deflections compared to the deflections of the half plane model established the multiplier for the elastic modulus.
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Case 1. Multiplier on elastic modulus to simulate actual pad thickness with the half plane model as a function of frequency and pad thickness. Poisson’s ratio=0.25.
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Case 2. For a rigidly supported 6 mm backing plate attached to the pad, the multiplier on the elastic modulus to simulate actual pad thickness with the half plane model as a function of frequency and pad thickness. Poisson’s ratio=0.25.
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Case 3. For an unsupported 6 mm backing plate attached to the pad, the multiplier on the elastic modulus to simulate actual pad thickness with the half plane model as a function of frequency and pad thickness. Poisson’s ratio=0.25.
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Case 4. For an unsupported 21 mm backing plate attached to the pad, the multiplier on the elastic modulus to simulate actual pad thickness with the half plane model as a function of frequency and pad thickness. Poisson’s ratio=0.25.
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Case 5. For an unsupported 70 mm backing plate attached to the pad, the multiplier on the elastic modulus to simulate actual pad thickness with the half plane model as a function of frequency and pad thickness. Poisson’s ratio=0.25.
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Critical speed for the Lee and Barber model with infinite half plane pad and with the elastic modulus changed to simulate the finite pad thickness of a standard brake
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Critical speed for the Lee and Barber model with infinite half plane pad and with the coefficient of friction changed to reflect partial rotor contact with the pad
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Critical speed for the original Lee and Barber model with infinite half plane pad and with the elastic modulus and coefficient of friction changed to reflect pad stiffness/thickness and partial rotor contact, respectively
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Nondimensional critical speed versus the frequency for various pad thickness for the modified and the original Lee and Barber model. The pad is rigidly supported in the case shown.

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