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Design Innovation

Minimum Material Design for Propane Cylinder End Closures

[+] Author and Article Information
Y. Kisioglu1

Department of Mechanical Education, Kocaeli University, Umuttepe, 41380 Kocaeli, Turkeyykisioglu@kou.edu.tr

J. R. Brevick

Department of Industrial and Systems Engineering, The Ohio State University, Columbus, OH 43210

G. L. Kinzel

Department of Mechanical Engineering, The Ohio State University, Columbus, OH 43210

1

Corresponding author.

J. Pressure Vessel Technol 130(1), 015001 (Jan 08, 2008) (9 pages) doi:10.1115/1.2826458 History: Received June 26, 2006; Revised December 11, 2006; Published January 08, 2008

This study addresses the design of DOT-4BA refillable cylinders using both experimental and numerical approaches. Using traditional design methods, these cylinders often experience buckling on the bottom end closure during pressure testing. A finite element analysis (FEA) design tool was developed using axisymmetric material nonlinear conditions to predict the buckling of the cylinder bottom end closures. The FEA model was also used to evaluate the influence of variations in end-closure geometry, material thickness, and strength on buckling. In addition, an optimization algorithm was employed to minimize end-closure material (weight) without buckling when they are subjected to their specified test pressure. Experimental studies were conducted via hydrostatic pressure tests with water at the R&D laboratories of a cylinder manufacturer. The axisymmetric nonlinear FEA models were developed successfully, and the obtained results are compared with experimental test results from cylinder manufacturer case studies.

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Copyright © 2008 by American Society of Mechanical Engineers
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Figures

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Figure 1

The DOT-4BA refillable propane cylinders and the geometry of the convex-end closure (1)

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Figure 2

The 2D axisymmetric BCs of the FEA model and design parameters of the end closure

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Figure 3

Loading conditions and maximum deflections of the entire model

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Figure 4

The geometrical and after buckling models of the convex-end enclosure

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Figure 5

Maximum deformation just before buckling of the convex-end enclosure

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Figure 6

The deflection behaviors for the selected nodes of the end closure

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Figure 7

The optimum values of the DVs, Rk (RCRWN) and Rc (RKNCK)

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Figure 8

The optimum values of the DV, thickness (TH)

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Figure 9

The optimum values of the SVs

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Figure 10

SVs for maximum equivalent and principal stresses

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Figure 11

The objection function (the minimum material of the end closure)

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Figure 12

Maximum deformation of the end closure before buckling using the optimum design parameters

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Figure 13

The new buckling pressure value using the optimum thickness (TH) value

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