By David Barton

A suite of topical papers on car brakes from a convention geared up by means of the Yorkshire Centre of the auto department of the IMechE. The convention serious about the newest improvement and seeked to deal with the most important difficulties dealing with the demanding department of car engineering.

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Extra info for Brakes 2000: Automotive Braking Technology for the 21st Century

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Two modes couple at the same frequency and the real parts splits into a positive and a negative value. 515 Hz. The thick solid line in the middle is the disc, the thin lines are the pads, the heavy solid lines the caliper parts and the two short lines the pistons. Calculations with this model have been made using 22 assumed modes on the disc and 6 on each of the pads. This choice leaves a total of 40 degrees of freedom in the model and it is based on the convergence of the solutions. 1 Solutions with positive real part Figure 3 shows the result of a calculation with baseline parameter values, but without damping.

The average error for a Euler-Bernoulli beam without foundation is 14% while the average error with the disc mounting modelled as a foundation is 11%. 41 Figure 2 Results from an Euler-Bernoulli beam model compared with frequencies of a real disc. 2 Modelling the pads and caliper The pads are also modelled by Euler-Bernoulli beams but with free-free boundary conditions. The stiffness EPIP, p = 2,3 is chosen to represent the modal properties obtained from measurements on the pads alone in the best possible manner.

The model presented here combines the continuous elements representing brake rotor and linings with discrete elements representing the pistons and the caliper. The aim of this work is to preserve a simplified modelling approach which allows for conceptual understanding of the squeal generation mechanism and still to incorporate a wider range of effects inf luencing the system response. New features in the presented modelling approach is the inclusion of pistons and caliper and of damping. NOMENCLATURE A\ G Cross section area of disc [] b Differential damping operator Cij f Width of disc rp Gyration radius Damping matrix elements t Thickness of lining E1 Youngs modulus of disc Eigenfrequency u Thickness of backplate EpIp Stiffness of pad p = 2,3 h Thickness of disc w Lateral displacement EI Youngs modulus of lining k' Cross section formfactor G1 Shear modulus of disc kij Stiffness matrix elements I1 Moment of inertia of disc kl km Lining stiffness d m Stiffness of spring L Disc equiv.

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