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Figure 4 Comparison of the buckling modes for the 51 mm-thick sphere under external pressure.
(A) Buckling Mode 0 (COQMULT),
(B) Buckling Mode 2 (COQMULT),
(C) Buckling Mode 0, β = 1 (QUA8),
(D) Buckling Mode 0, β=0.0001 (QUA8).
From:
Alain G. Combescure (LaMCoS, INSA-Lyon, Université de Lyon, CNRS UMR 5259, 18-20 rue des Sciences, F69621 Villeurbanne, France),
“Modeling elastic-plastic buckling of sandwich axisymmetric shells: on the limits of "shell" models and analytical solutions”, Advanced Modeling and Simulation in Engineering Sciences, Vol 1, No. 2, 2014, doi:10.1186/2213-7467-1-2 http://www.amses-journal.com/content/1/1/2
ABSTRACT: The objective of this paper is to answer the question: "Can a 'shell' model always be used to predict the elastic buckling of a shell?" This paper shows that such a model leads to significantly overestimated critical loads in the case of sandwich shells and gives an explanation for this overestimation. A dependable model is proposed and applied to a few structures of revolution, for which it is shown that shell analyses are sometimes overly on the unsafe side. Of course, in such cases, 3D analysis is possible, but the associated computation cost is several orders of magnitude higher than that of the Fourier series analysis proposed in this paper.
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