WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
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Inverse design of phononic crystals by tobology optimization 897<br />
While the above PDEs may be solved analytically for<br />
uniform and homogeneous beams, numerical methods like<br />
the FE Method must be resorted to when considering periodic<br />
in-homogeneous structures as will be the case here.<br />
Let a base cell of length d be divided into N finite elements.<br />
For longitudinal wave motion, the N þ 1 degrees<br />
of freedom (d.o.f) are the nodal longitudinal displacements,<br />
while for bending waves the 2(N þ 1) d.o.f. are the<br />
nodal transverse displacements and the rotation of the<br />
cross-section. For each of the two wave type problems, the<br />
global stiffness matrix K and mass matrix M for the base<br />
cell are assembled in the usual manner from the corresponding<br />
element matrices. For longitudinal waves the element<br />
matrices are 2 2 matrices using first order polynomials<br />
as shape function for u [15]. For bending waves, the<br />
element matrices are 4 4 matrices using third and second<br />
order polynomials as shape functions for w and q<br />
respectively [14]. According to Bloch theory [16], the periodic<br />
boundary condition at the ends of the base cell becomes<br />
for longitudinal waves<br />
uN ¼ u1 e ikB<br />
where k B ¼ kd is the Bloch parameter and k the wave<br />
number. Due to reasons of periodicity, 0 k B p. Similarly<br />
for bending waves, the periodic boundary conditions<br />
become<br />
wN ¼ w1 e ikB<br />
;<br />
qN ¼ q1 e ikB<br />
:<br />
These boundary conditions must be incorporated into the<br />
corresponding stiffness matrices.<br />
Assuming time harmonic motion with circular frequency<br />
w the two eigenvalue problems become<br />
Kiðk B Þ ui ¼ liMiui ; li ¼ w 2 i ; i ¼ L; B ð10Þ<br />
where ui contains the nodal values of the variables, L ¼<br />
longitudinal waves and B ¼ bending waves. The dependence<br />
on k B is shown explicitly.<br />
The stiffness and mass matrices K and M depend in<br />
general on the cross-sectional geometry, length of base cell<br />
and material parameters. Here we choose a fixed circular<br />
cross-section of radius r ¼ 0:5 cm, such that we end up<br />
with only the longitudinally varying material properties<br />
and the cell length as design variables. As discussed in the<br />
previous section, the goal is to find the distribution of two<br />
a priori chosen materials in the base cell, that results in the<br />
largest band gaps as calculated by (10). We choose a continuous<br />
design variable 0 z e 1, z e ¼ 1; ...; N for each<br />
element, that interpolates between the two chosen materials.<br />
In our model (10), there are three material parameters<br />
E, q and n introduced above. We thus have the following<br />
three material interpolation functions on the form (2)<br />
EðzeÞ¼ ð1 zeÞ E1 þ zeE2 ;<br />
qðzeÞ¼ ð1 zeÞ q1 þ zeq2 ;<br />
nðzeÞ¼ ð1 zeÞ n1 þ zen2 :<br />
The subscript i ¼ 1; 2 denotes one of the two materials.<br />
Finally, we also let the base cell length d be a design<br />
parameter, such that the cell length can be optimized.<br />
Table 1. Material properties for the two materials used in the numerical<br />
example.<br />
Material q [kg/m 3 ] E [GPa] n<br />
Aluminium 2830 70.9 0.34<br />
PMMA 1200 5.28 0.40<br />
The optimization problem<br />
For each of the two wave type problems, we can state the<br />
problem of maximizing the relative band gap between frequency<br />
bands j and j þ 1<br />
max<br />
z 2½0; 1Š N<br />
: Fðz; dÞ ¼2<br />
d 2½dmin; dmaxŠ<br />
min<br />
k B 2½0; pŠ wjþ1<br />
max<br />
k B 2½0; pŠ wj<br />
min<br />
kB 2½0; pŠ wjþ1 þ max<br />
kB 2½0; pŠ wj<br />
: ð11Þ<br />
For 1D problems, finding the minimum/maximum of the<br />
involved frequencies over k B in (11) can be avoided, since<br />
empirically it is known that the frequency bands are alternating<br />
monotonic (for the purpose of illustration, consult<br />
Fig. 1). Therefore the minimum band gap between two<br />
consecutive bands will occur at k B ¼ p for j ¼ 1; 3; 5; ...<br />
and at k B ¼ 0 for j ¼ 2; 4; 6; .... The maximization problem<br />
(11) is solved iteratively using the method of moving<br />
asymptotes MMA [17], which is based on a gradient descent<br />
approach.<br />
For the coupled problem of maximizing the overlap<br />
between band gaps for longitudinal and bending waves,<br />
the formulation becomes<br />
max<br />
z 2½0; 1Š N<br />
: Fðz; dÞ<br />
d 2½dmin; dmaxŠ<br />
¼ 2 min ðwL jþ1 ; wB iþ1 Þ max ðwL j ; wB i Þ<br />
min ðw L jþ1 ; wB iþ1 Þþmax ðwL j ; wB i Þ<br />
ð12Þ<br />
where i, i þ 1 denote the bending frequency bands and j,<br />
j þ 1 denote the longitudinal frequency bands.<br />
The FE problem (10) together with either (11) or (12)<br />
are the problem specific equivalents to (3) and (6) in the<br />
general formulation.<br />
Numerical examples<br />
We now study an actual maximization problem considering<br />
the two materials Aluminum (Material 1) and PMMA<br />
(Material 2) with material properties listed in Table 1.<br />
Comparing the two materials, Aluminum is the heavy and<br />
stiff material while PMMA is the light and soft material.<br />
As a first example, the relative band gap between the<br />
first and second frequency band (j ¼ 1) for longitudinal<br />
waves has been maximized. The resulting design is shown<br />
in Fig. 1. From (10) and (11) it can be shown, that the<br />
relative band gap sizes are independent of the base cell<br />
length. In the maximization algorithm this variable has<br />
been fixed at a value of d ¼ 8:70 cm for reasons that will<br />
be explained later. It is seen that the algorithm has chosen<br />
the two extreme materials 1 and 2 (corresponding to<br />
z e ¼ 0; 1 on the y-axis) instead of interpolations of the<br />
two. This is interpreted as favouring high contrast in the