Research Papers: Design and Analysis

Incorporation of Friction Coefficient in the Design Equations for Elevated Temperature Tanks

[+] Author and Article Information
Sridhar Sathyanarayanan

Graduate Student
Faculty of Engineering and Applied Science,
Memorial University of Newfoundland,
St. John's, NF, A1B 3X5, Canada
e-mail: ssridhar@mun.ca

Seshu M. R. Adluri

Assoc. Professor
Faculty of Engineering and Applied Science,
Memorial University of Newfoundland,
St. John's, NF, A1B 3X5, Canada
e-mail: adluri@mun.ca

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received January 2, 2012; final manuscript received April 24, 2012; published online March 18, 2013. Assoc. Editor: William J. Koves.

J. Pressure Vessel Technol 135(2), 021205 (Mar 18, 2013) (8 pages) Paper No: PVT-12-1002; doi: 10.1115/1.4007042 History: Received January 02, 2012; Revised April 24, 2012

Storage tanks operating at elevated temperatures (200 °F to 500 °F) need to consider stresses due to thermal expansions and restraints, due to the tank shell and bottom plate interactions and operating conditions in addition to the design requirements for ambient temperature tanks. Appendix M of API Standard 650 provides additional requirements and guidelines for the design of tanks operating at elevated temperatures. These are based on Karcher's method which gives a simplified procedure for determining the stresses (strain range) in the tank wall and bottom plate. A factor named “C” is used for defining the ratio of actual expansion against free expansion of the tank. Such partial expansion causes significant thermal stresses. API uses these stresses to estimate the low cycle fatigue life of the tanks. At present, a range of C values (0.25–1.0) is allowed by API without clear guidelines for selecting a suitable value. In the absence of such guidelines, a set value (like 0.85) is being used irrespective of the tank dimensions and temperature change. The restraint against free expansion is mainly a result of the friction between bottom plate, the foundation medium and the ring wall (if present). We can estimate the C factor by relating it to the friction coefficient. This is explored in the present study. This paper evaluates the current procedure and suggests an alternate method by incorporating the friction coefficient directly in the stress equations, instead of the C-factor. Use of friction coefficient provides an improved basis for selecting C and avoids some of the difficulties.

Copyright © 2013 by ASME
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Fig. 2

Friction forces below the bottom plate

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Fig. 1

Mechanism of plastic hinges (for rigid foundations)

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Fig. 3

Bending stress (Mx) in the tank wall including the effect of friction (μ = 0.5)

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Fig. 4

Hoop stress in the tank wall including the effect of friction (μ = 0.3)

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Fig. 5

Bending stress for various values of C and μ

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Fig. 6

Bending stress at different temperatures (μ = 0.7)

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Fig. 7

Temperature influence on C-factor

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Fig. 8

Influence of C-factor on fatigue life




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