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Free Damped Vibrations of Sandwich Shells of Revolution 185<br />
u= N = [ N , N ,..., N ] =∑ N<br />
() e 1 2 6 () e i i<br />
i= 1<br />
6<br />
(32)<br />
where<br />
T<br />
() e = 1 2 6<br />
{ , ,..., }<br />
(33)<br />
are generalised displacements of the finite element and<br />
<br />
T (1) (1) (1) (1) (1) (3) (3) (3) (3)<br />
i = u0 v<br />
i 0<br />
w<br />
i 0 γ i x γ i ϕ<br />
u<br />
i 0<br />
v<br />
i 0<br />
γ i x<br />
γ<br />
i ϕi<br />
{ , , , , , , , , }<br />
(34)<br />
is the vector of the displacement parameters at node i. Here<br />
N<br />
i<br />
= Ni<br />
I<br />
9<br />
(35)<br />
where N i are the shape functions for node i expressed in terms of local triangular<br />
coordinate system (L 1 ,L 2 ,L 3 ) of the finite element and I 9 istheunit9×9matrix.<br />
UNDAMPED VIBRATION<br />
The Hamilton’s principle given by Equation (21) is discretised as<br />
∫<br />
N<br />
t e<br />
2<br />
t1<br />
∑( δUl −δTl −δ Wel) dt = 0<br />
l=<br />
1<br />
(36)<br />
where N e is the total number of finite elements and the subscript l represents the<br />
contribution of the lth element. Equation (36) can be expressed in terms of the displacements<br />
and rotation angles (u 0 ,v 0 ,w 0 ,γ x ,γ ϕ ). Following the standard finite element<br />
technique, we obtain the discretised equations in terms of nodal degrees of<br />
freedom x:<br />
Mẋ̇ + Kx = F<br />
(37)<br />
where M, K, x, F are the global mass and stiffness matrices, the displacement and<br />
load vector, respectively. For free vibration problems F = 0 and Equation (37) becomes<br />
2<br />
( K− M)<br />
=<br />
0<br />
(38)<br />
where is the natural frequency and is the corresponding mode shape of the<br />
structure.