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By D. Barton, S. Earle

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The linear stiffness and damping are k1, to k5 and c1 to c5 respectively, and the rotary stiffiiess and damping are ktl to kt3 and ct1 to ct3 respectively. The excitation forces acting on the brake components are the piston forces Fp and the frictional forces Fl and F2. The excitation moments are the product of the friction forces F1 and F2 by the half rotor and pad thicknesses. The friction forces can be written as following; The applied piston force is assumed to increase linearly with time and is given as; Where ts is the stopping time.

Three roots with a positive real part or a positive squeal propensity are displayed. For a zero coefficient of friction the system is stable. 500 Hz for a variation of the relative length of the pad. part of the eigenvalue. As indicated in figure 4 the increase in friction can forces two modes to couple. The imaginary parts coalesce while the real parts diverge into one positive and one negative. Only particular modes and modes sufficiently close may couple while other modes don't couple no matter how close they are.

6 ACKNOWLEDGEMENTS The authors gratefully acknowledge the financial support from the Swedish board for Technical Development (NUTEK), Volvo Technological Development for providing test materials and Claes Kuylenstierna for valuable discussions. 7 REFERENCES 1. , Influence of Disc Topography on Generation of Brake Squeal. Wear, 1999, 225-229, p. 629-639. C. , Interim Report on Disc Brake Squeal. M. I. R. A, 1959, 1959/4. , Friction-induced noise and vibration of disc brakes. Wear, 1989, 133, p. 39-45.

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