Avoidance of brake squeal by a separation of the brake ... - tuprints
Avoidance of brake squeal by a separation of the brake ... - tuprints
Avoidance of brake squeal by a separation of the brake ... - tuprints
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4.3 Automotive <strong>brake</strong> disc with cooling channels<br />
between two cooling ribs and thus give <strong>the</strong> minimal and maximal distances<br />
between <strong>the</strong>m, which have to be kept due to cooling and material strength<br />
requirements. In contrast to <strong>the</strong> case with radial holes, <strong>the</strong> maximal and<br />
minimal distance constraints can be written in linear form, since <strong>the</strong> variation<br />
in radial direction is much smaller. The <strong>brake</strong> disc has to be statically and<br />
dynamically balanced leading to <strong>the</strong> nonlinear equality constraints<br />
c eq<br />
1 (r,ϕ) = ∑ N<br />
n=1 r ncosϕ n ,<br />
c eq<br />
2 (r,ϕ) = ∑ N<br />
n=1 r nsinϕ n ,<br />
(4.10)<br />
which can easily be derived, since <strong>the</strong> <strong>brake</strong> disc’s friction rings and each <strong>of</strong><br />
<strong>the</strong> cooling ribs are assumed to be homogeneous bodies <strong>of</strong> constant geometry<br />
rotating at a constant angular velocity. These constraints for static balancing<br />
represent <strong>the</strong> projection <strong>of</strong> <strong>the</strong> excentricity <strong>of</strong> <strong>the</strong> <strong>brake</strong> disc induced <strong>by</strong> <strong>the</strong><br />
placement <strong>of</strong> <strong>the</strong> cooling ribs onto x-direction (c eq<br />
1 ) and y-direction (ceq 2 ),<br />
respectively. Also, <strong>the</strong> dynamic balancing is automatically guaranteed due to<br />
<strong>the</strong> symmetry with respect to <strong>the</strong> middle plane <strong>of</strong> <strong>the</strong> disc.<br />
As has been introduced in section 4.1, <strong>the</strong> presented optimization problem<br />
is nonconvex and nonlinear with linear and nonlinear constraints and many<br />
local optima to be expected. The <strong>brake</strong> disc to be optimized is modeled using<br />
<strong>the</strong> method proposed in chapter 3. The underlying FE meshes <strong>of</strong> <strong>the</strong> friction<br />
rings and each cooling rib have been assembled using Abaqus with 3D solid<br />
isoparametric elements <strong>of</strong> quadratic shape function order (C3D20) leading to<br />
65250 DOF in <strong>the</strong> friction ring mesh and 4860 DOF for each cooling rib, fulfilling<br />
convergence requirements. The parameters <strong>of</strong> <strong>the</strong> filling material between<br />
<strong>the</strong> friction rings were chosen as Ẽ = 1.4 MPa and ˜ρ = 1 kg/m3 . Since <strong>the</strong><br />
limit frequency f lim is estimated to be 9 kHz, <strong>the</strong> first 21 eigenfrequencies<br />
<strong>of</strong> <strong>the</strong> <strong>brake</strong> disc with N = 39 cooling ribs are considered in <strong>the</strong> calculation.<br />
Solutions are treated as infeasible if one <strong>of</strong> <strong>the</strong> constraints c eq<br />
1<br />
and ceq 2<br />
is violated<br />
<strong>by</strong> an absolute value <strong>of</strong> 0.005 m. The parameters for <strong>the</strong> upper and<br />
lower bounds and <strong>the</strong> linear constraints can be found in Tab. 4.6. Due to <strong>the</strong><br />
properties <strong>of</strong> <strong>the</strong> optimization problem, deterministic optimization approaches<br />
cannot guarantee <strong>the</strong> finding <strong>of</strong> <strong>the</strong> global optimum, <strong>the</strong>refore, heuristic algorithms<br />
are indicated. In <strong>the</strong> following, <strong>the</strong>se two types <strong>of</strong> algorithms will be<br />
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