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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

Lee,  K., and Barber,  J. R., 1993, “Frictionally Excited Thermoelastic Instability in Automotive Disk Brakes,” ASME J. Tribol. 115, pp. 607–614.
Dow,  T. A., and Burton,  R. A., 1972, “Thermoelastic Instability of Sliding Contact in the Absence of Wear,” Wear 19, pp. 315–328.
Burton,  R. A., Nerlikar,  V., and Kilaparti,  S. R., 1973, “Thermoelastic Instability in a Seal-Like Configuration,” Wear 24, pp. 177–188.
Barber,  J. R., 1967, “The Influence of Thermal Expansion on the Friction and Wear Process,” Wear 10, pp. 155–159.
Barber,  J. R., 1969, “Thermoelastic Instabilities in the Sliding of Conforming Solids,” Proc. R. Soc. London, Ser. A 312, pp. 381–394.
Van Swaaij, J. L., 1979, “Thermal Damage to Railway Wheels,” Inst. Mech. Eng., Intl. Mech. Eng., Intl. Conf. on Railway Braking, York, p. 95.
Hewitt, G. G., and Musial, C., 1979, “The Search for Improved Wheel Materials,” Inst. Mech. Eng., Intl. Conf. on Railway Braking, York, p. 101.
Kreitlow, W., Schrodter, F., and Matthai, H., 1985, “Vibration and Hum of Disc Brakes Under Load,” SAE 850079.
Abendroth, H., 1985, “A New Approach to Brake Testing,” SAE 850080.
Anderson,  A. E., and Knapp,  R. A., 1989, “Hot Spotting in Automotive Friction Systems,” Int. Conf. Wear Materials, 2, pp. 673–680.
Thomas, E., 1988, “Disc Brakes for Heavy Vehicles,” Inst. Mech. Eng., Intl. Conf. on Disc Brakes for Commercial Vehicles, C464/88, pp. 133–137.
Barber,  J. R., Beamond,  T. W., Waring,  J. R., and Pritchard,  C., 1985, “Implications of Thermoelastic Instability for the Design of Brakes,” ASME J. Tribol. 107, pp. 206–210.
Ayala,  J. R. R., Lee,  K., Rahman,  M., Barber,  J. R., 1996, “Effect of Intermittent Contact on the Stability of Thermoelastic Sliding contact,” ASME J. Tribol. 118, pp. 102–108.
Lee, K., and Dinwiddie, R. B., 1998 “Conditions of Frictional Contact in Disk Brakes and Their Effects on Brake Judder,” SAE980598.
Lee, K., and Barber, J. R., 1995, “Effect of Intermittent Contact on the Thermoelastic Instability of Automotive Disk Brake Systems,” AMD-198 , Thermoelastic Problems and The Thermodynamics of Continua, ASME.
Barber, J. R., 1992, Elasticity, Kluwer Academic Publishers, MA, pp. 199–203.
Barber, J. R., 1997, personal communication.
Hecht, R. L., 1996, “Thermal Transport Properties of Gray Cast Iron Rotors,” SRM-96-013, Sept. 5.

Figures

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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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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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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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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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