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Research Papers: Design and Analysis

An Analytical Symplecticity Method for Axial Compression Plastic Buckling of Cylindrical Shells

[+] Author and Article Information
Jiabin Sun

e-mail: jiabin-sun@163.com

State Key Laboratory of Structure Analysis of Industrial Equipment,
Department of Engineering Mechanics,
Dalian University of Technology,
Dalian 116024, China

C. W. Lim

Department of Civil and
Architectural Engineering,
City University of Hong Kong,
Hong Kong, Kowloon, China

1Corresponding author.

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the Journal of Pressure Vessel Technology. Manuscript received August 9, 2012; final manuscript received May 24, 2013; published online September 16, 2013. Assoc. Editor: Spyros A. Karamanos.

J. Pressure Vessel Technol 135(5), 051204 (Sep 16, 2013) (8 pages) Paper No: PVT-12-1126; doi: 10.1115/1.4024687 History: Received August 09, 2012; Revised May 24, 2013

This study is mainly concerned with the analytical solutions of plastic bifurcation buckling of cylindrical shells under compressive load. The analysis is based on the J2 deformation theory with a linear hardening and proportional loading is adopted in the calculation. A symplectic solution system is established and Hamilton's governing equations are derived from the Hamilton variational principle. The basic problem in plastic buckling is converted into solving for the symplectic eigenvalues and eigensolutions, respectively. The obtained results reveal that boundary conditions have a very limited influence on bucking loads but its influence on buckling modes and plastic borders cannot be neglected. Meanwhile, it is demonstrated that the shell material properties significantly affect the plastic buckling behavior. This proposed symplectic method is shown to be a rigorous approach. It also provides a uniform and systematic way to any other similar problems.

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References

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Figures

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Fig. 1

Geometric parameters for a cylindrical shell under a compressive load

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Fig. 2

Comparisons of critical stress (a) and axial half-wavelength (b) with the existing results

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Fig. 3

Buckling loads N¯cr with respect to L for cases C1-S4

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Fig. 4

Buckling loads N¯cr with respect to L for different yield stresses

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Fig. 5

Buckling loads N¯cr with respect to L for different tangent moduli

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Fig. 6

Buckling loads N¯cr with respect to H for different lengths

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Fig. 7

Circumferential wave numbers n with respect to L for cases C2 and C4 (H=1/35)

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Fig. 8

Buckling modes with L = 0.5 for cases C1-S4

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Fig. 9

Buckling modes with L = 4 for cases C1-S4

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Fig. 10

Buckling modes with L = 4 for different yield stresses

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Fig. 11

Buckling modes with L = 4 for different tangent moduli

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Fig. 12

Buckling modes with L = 4 for different thicknesses

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Fig. 13

Plastic buckling borders for cases C1-S4

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Fig. 14

Plastic buckling borders for different yield limits

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Fig. 15

Plastic buckling borders for different tangent moduli

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