Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
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826 ELIA EFRAIM AND MOSHE EISENBERGER<br />
after transformation to the nondimensional coordinate ξ, we obtain the equations <strong>of</strong> motion in term <strong>of</strong><br />
the displacements as<br />
K (0) (ξ, ω)U(ξ) + K (1) (ξ)U ′ (ξ) + K (2) (ξ)U ′′ (ξ) = 0, (14)<br />
where primes refer to derivatives with respect to ξ, <strong>and</strong> the terms in the matrices K (0) , K (1) , <strong>and</strong> K (2) are<br />
given in the Appendix. The solution is obtained using the exact element method algorithm [Eisenberger<br />
1990] by assuming the solution as infinite power series<br />
U(ξ) =<br />
∞�<br />
uiξ i , (15)<br />
i=0<br />
<strong>and</strong> following the procedure in [Eisenberger 1990] we get the five basic shape functions for each case<br />
<strong>of</strong> unit displacement on the shell edges. Based on the values <strong>of</strong> the shape functions <strong>and</strong> their derivatives<br />
at the two edges <strong>of</strong> the segment (ξ = 0; ξ = 1) we get the terms in the dynamic stiffness matrix as the<br />
resultant forces along the unit angle segment <strong>of</strong> the perimeter <strong>of</strong> the shell, as shown in Figure 2, as<br />
S1<br />
S6<br />
S2<br />
S7<br />
S3<br />
S8<br />
S4<br />
S9<br />
S5<br />
S10<br />
�<br />
�<br />
�<br />
�<br />
�<br />
�<br />
�<br />
�<br />
= Nφ�<br />
ξ=0<br />
ξ=1<br />
�<br />
�<br />
�<br />
= Nφθ � ξ=0<br />
ξ=1<br />
�<br />
�<br />
�<br />
= Qφ�<br />
ξ=0<br />
ξ=1<br />
�<br />
�<br />
�<br />
= Mφ�<br />
ξ=0<br />
ξ=1<br />
= Mφθ<br />
�<br />
�<br />
�<br />
� ξ=0<br />
ξ=1<br />
= E<br />
1 − µ 2<br />
=<br />
= κ E<br />
E<br />
2(1 + µ)<br />
2(1 + µ)<br />
� R ′ p �<br />
µu +<br />
R0<br />
R p�<br />
u<br />
R0<br />
′ � � � �<br />
R p<br />
���<br />
+ µnv + (1 + µ) w ,<br />
R0<br />
ξ=0<br />
ξ=1<br />
�<br />
−nu − R′ p� � �<br />
���<br />
,<br />
ξ=0<br />
�<br />
− R p<br />
R0<br />
R0<br />
v + R p�<br />
v<br />
R0<br />
′<br />
u + R p�<br />
w<br />
R0<br />
′ + ψs<br />
E<br />
=<br />
(1 − µ 2 h<br />
)<br />
3 �<br />
µ<br />
12<br />
R′ p� ψφ +<br />
R0<br />
R p�<br />
R0<br />
E h<br />
=<br />
2(1 + µ)<br />
3 �<br />
−nψφ −<br />
12<br />
R′ p� R0<br />
ψ ′ φ<br />
ψθ +<br />
ξ=1<br />
� �<br />
���<br />
,<br />
ξ=0<br />
ξ=1<br />
+ µnψφ<br />
� R p<br />
R0<br />
�<br />
�ψ ′ θ<br />
� �<br />
���<br />
,<br />
ξ=0<br />
ξ=1<br />
� �<br />
���<br />
.<br />
ξ=0<br />
ξ=1<br />
The dynamic stiffness matrix for a segment, having ten degrees <strong>of</strong> freedom, five on each edge, is<br />
then assembled for the structure in the usual procedure <strong>of</strong> structural analysis. The natural frequencies <strong>of</strong><br />
vibration are found as the values <strong>of</strong> the frequency that will cause the assembled dynamic stiffness matrix<br />
<strong>of</strong> the structure to become singular.<br />
When the cut-outs size becomes relatively small (R p,in/R p,out < 0.1) the shape functions series converges<br />
rather slowly <strong>and</strong> have relatively large number <strong>of</strong> terms. Therefore, in order speed the convergence<br />
process one can divide the shell into sections with ratio R p,in = 0.3R p,out for each section. So, by adding<br />
a small number <strong>of</strong> elements one can solve for shells with very small cut-outs (e.g., three elements for<br />
R p,in = 0.03R p,out <strong>and</strong> four elements for R p,in = 0.01R p,out).<br />
4. Numerical examples<br />
In order to obtain a high-precision solution for vibration problems <strong>of</strong> thick spherical shells, numerical<br />
calculations have been performed for a spherical shells with different thickness-radius ratios, <strong>and</strong> various<br />
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