Research Papers

Suppression of Brake Squeal Using Shunted Piezoceramics

[+] Author and Article Information
Marcus Neubauer

Institute of Dynamics and Vibrations, Leibniz University of Hannover, 30167 Hannover, Germanyneubauer@ids.uni-hannover.de

Robert Oleskiewicz

Department of Mechatronics, Faculty of Mechanical Engineering, Koszalin University of Technology, Koszalin PL75-620, Polandr.oleskiewicz@wp.pl

J. Vib. Acoust 130(2), 021005 (Jan 30, 2008) (8 pages) doi:10.1115/1.2827983 History: Received October 06, 2006; Revised November 15, 2007; Published January 30, 2008

Due to increased interest in comfort features, considerable effort is spent by brake manufacturers in order to suppress brake squeal. This process can be shortened by eliminating the remaining squealing with shunted piezoceramics that are embedded into the brake system. The piezoceramics offers the unique ability to convert mechanical energy into electrical energy and vice versa. The damping performance is determined by the connected shunt. This paper presents a multibody system model of a brake, which is capable of reproducing important features of brake squeal. It includes the dynamics of a piezoceramics that is shunted with a passive LR shunt or a negative capacitance LRC shunt. Analytical stability analysis is carried out to obtain optimal shunt parameters. The performance increase with a negative capacitance is studied in detail. The simulations are validated with measurements on an automotive disk brake.

Copyright © 2008 by American Society of Mechanical Engineers
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Figure 1

Multibody system of the brake

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Figure 3

Disk eigenform with m=4, n=1

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Figure 4

Imaginary part versus real part of the eigenvalues of the uncontrolled brake

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Figure 5

Model of shunted piezoceramics

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Figure 6

Amplification and phase shift of piezoforce versus excitation frequency Ω for various resistances R; passive LR shunt

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Figure 7

Amplification and phase shift of piezoforce versus excitation frequency Ω for various capacitance ratios δ; passive LR and semiactive LRC shunts

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Figure 8

Energy dissipation per vibration period versus normalized excitation frequency; passive LR and semiactive LRC shunts; ζ=const.

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Figure 9

Negative capacitance board; C=−R1∕R2Cpos

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Figure 10

Stability of the system for LRC combinations with various capacitance ratios δ

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Figure 11

Stability of the brake model for LR shunt (δ=0) and for LRC shunts with δ1=−0.6 and δ2=−0.88

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Figure 13

Sound pressure and SPL during one measurement with stepwise varied inductance

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Figure 14

Sound pressure and short time FFT for a tuned shunt

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Figure 15

SPL reduction for passive LR shunt and semiactive LRC shunts (δ1=−0.66, δ2=−0.86)




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