WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
WAVES AND VIBRATIONS IN INHOMOGENEOUS STRUCTURES ...
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The parameters used in this example are given as<br />
T ¼ 10 s; u0 ¼ 1m; t0 ¼ 2:5s; N ¼ 150;<br />
x0 ¼ 15:7 rad=s; Dt ¼ 0:06 s; b ¼ 0:1ðkg mÞ 1 ;<br />
d ¼ 1:5 s 2 ; E0 ¼ 1:25 N=m 2 :<br />
To be able to clearly separate input and reflected waves in the time<br />
series, inlet and outlet sections of 2 m with constant material properties<br />
are added on each side of the design domain of length 1 m.<br />
The material properties of the inlet and outlet sections are normalized<br />
to E ¼ 1N=m 2 and q ¼ 1kg=m 3 , so that the incoming wave<br />
propagates with the speed c ¼ 1m=s. In order to simulate wave<br />
propagation in this finite structure, fully absorbing boundaries are<br />
added at the input and output points by appropriate viscous<br />
dampers.<br />
Two materials can be distributed in the design domain: the normalized<br />
material used for the the inlet and output sections, and a<br />
material with a slightly higher stiffness E0 ¼ 1:25. The relatively<br />
small stiffness contrast is used in order to avoid problems with<br />
spurious oscillations (cf. Section 3.2). The presence of oscillations<br />
leads to incorrect sensitivity calculations that destabilize the optimization<br />
process. A small stiffness contrast combined with added<br />
stiffness proportional damping (b ¼ 0:1 used throughout this<br />
example) eliminate these problems while still displaying the main<br />
qualitative features.<br />
5.1. Static bandgap structure<br />
For comparison the structure is optimized for the static case, i.e.<br />
a spatial material distribution is obtained which cannot change in<br />
time. Similar design problems were considered recently for transient<br />
loading in [13]. Fig. 12 shows the optimized design and<br />
Fig. 13 shows the nodal displacements as a function of time at<br />
the input and the output points. In the time plots one can easily<br />
identify the input and reflected waves at the input point (top figure)<br />
and the transmitted wave at the output point (bottom figure).<br />
The optimized structure in Fig. 12 is a bandgap structure [8]<br />
with periodically layered inclusions of the stiffer material. Such a<br />
structure reflects the waves maximally and reduces the objective<br />
function to 76% compared to the undisturbed wave. For comparison<br />
it can be mentioned that in the case in which the design domain<br />
is completely filled with the stiffer material the objective<br />
function is only reduced to 93%. These computations have been<br />
performed with stiffness proportional damping corresponding to<br />
b ¼ 0:1. Without damping (b ¼ 0) the transmissions are 81% and<br />
99%, respectively.<br />
With a static structure the only way to further reduce U would<br />
be to either increase the material contrast or to increase the length<br />
of the design domain relative to the wavelength of the pulse. The<br />
latter choice would results in more inclusion layers that lead to<br />
an increased reflection of the wave.<br />
5.2. Space–time bandgap structure<br />
The design is now allowed to change in time as well as in space.<br />
The optimized static bandgap structure in Fig. 12 is used as a starting<br />
point for the dynamic structure. This is illustrated in Fig. 14<br />
where the space–time design domain is indicated. A temporal design<br />
interval of DT ¼ 1:5 s is chosen, which is sufficiently long to<br />
Fig. 12. Optimized structure for the ‘‘static” wave propagation problem.<br />
J.S. Jensen / Comput. Methods Appl. Mech. Engrg. 198 (2009) 705–715 711<br />
Fig. 13. Response for the optimized structure shown in Fig. 12. Top: input point<br />
displacement showing the input and reflected wave, bottom: output point<br />
displacement showing the transmitted wave.<br />
significantly modify the wave motion but still keeps the total number<br />
of design variables at a manageable level. The start and finish<br />
point for the optimization is chosen as T1 ¼ 4:25 s and<br />
T2 ¼ 5:75 s and the number of sub-intervals is M ¼ 225, thus<br />
the material properties in each element are allowed to change<br />
150 times per second. The spatial discretization is unchanged from<br />
the static case with 150 elements in the design domain. Thus, the<br />
two-dimensional design grid is composed of ‘‘square” elements<br />
1<br />
with the dimensions 150 s 1 m and a total of 33750 design<br />
150<br />
variables.<br />
The initial value of all design variables is chosen as xe ¼ 0:5,<br />
implying that the stiffness in all design elements is initially<br />
E ¼ 1:125 N=m2 . The optimized design is obtained after about<br />
100 iterations and is shown in Fig. 15. The structure is seen to be<br />
a kind of spatio-temporal laminate with space–time layered inclusions.<br />
Properties of spatio-temporal laminates are discussed, e.g. in<br />
[22,35,24].<br />
At each time instance the structure is layered in a similar way as<br />
the static bandgap structure. However, the inclusion layers move<br />
with a constant speed corresponding to the wave speed in the layered<br />
medium so that the wave peaks and valleys actually move together<br />
with the front of the inclusions. This is illustrated in Fig. 16,<br />
in which the material distribution is shown together with the wave<br />
motion at the two time instances t ¼ 5:0s and t ¼ 5:4s.<br />
Fig. 17 shows the input and output point time responses. The<br />
objective is reduced to 23% relative to the undisturbed input signal<br />
– thus, a significant reduction is noted compared to the static case<br />
(76%). The large reduction is not a consequence of an increased