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Research Papers: Design Innovation Papers

Design Limits for Buckling in the Creep Range

[+] Author and Article Information
Maan Jawad

President
Global Engineering and Technology, LLC,
5918 NE 304 Ave,
Camas, WA 98607
e-mail: maanjawad@aol.com

Donald Griffin

Consultant
208 Oakcrest,
Pittsburgh, PA 15236
e-mail: bardon87@aol.com

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNALOF PRESSURE VESSEL TECHNOLOGY. Manuscript received March 24, 2011; final manuscript received April 27, 2012; published online October 18, 2012. Assoc. Editor: William J. Koves.

J. Pressure Vessel Technol 134(6), 065001 (Oct 18, 2012) (9 pages) doi:10.1115/1.4007031 History: Received March 24, 2011; Revised April 27, 2012

A methodology is introduced for calculating the allowable buckling stress in equipment operating in the time-dependent (creep) range. Norton's equation coupled with various procedures such as the stationary stress method, classical creep buckling equations, and the isochronous stress–strain diagrams are utilized to obtain a practical design approach for equipment operating in the time-dependent range. Various components are investigated such as slender columns, cylindrical shells, spherical components, and conical transition sections.

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Copyright © 2012 by ASME
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References

Figures

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Fig. 1

Tensile data in the creep range (Jawad and Jetter, 2009)

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Fig. 2

Isochronous stress–strain curves for 2.25Cr-1Mo steel at 1000 °F (ASME III-NH)

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Fig. 3

Deflection in the creep range

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Fig. 4

External pressure chart for carbon and low alloy steels with yield stress of 30 ksi and higher (ASME II-D)

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Fig. 5

External pressure chart for 2 ¼ Cr-1Mo steel at 1000 °F

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Fig. 6

Collapse coefficients of cylindrical shells with pressure on sides and ends, edges simply supported, and μ = 0.3 (Jawad and Jetter, 2009)

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Fig. 7

Geometric chart for cylindrical shells under external or compressive loadings (ASME)

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