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Research Papers: Design and Analysis

A New Stress Intensification Factor of Pipe-In-Pipes Based on Finite Element Analyses

[+] Author and Article Information
Se-Chang Kim, Jae-Boong Choi, Moon Ki Kim

School of Mechanical Engineering,
Sungkyunkwan University,
2066 Seobu-ro, Jangan-gu,
Suwon 16419, South Korea

Hyun-Su Kim

Power Engineering Research Institute,
KEPCO E&C,
269 Hyeoksin-ro,
Gimcheon 39660, South Korea

Nam-Su Huh

Department of Mechanical System
Design Engineering,
Seoul National University of
Science and Technology,
232 Gongneung-ro, Nowon-gu,
Seoul 01811, South Korea
e-mail: nam-su.huh@seoultech.ac.kr

1Corresponding author.

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received November 20, 2016; final manuscript received March 13, 2017; published online April 21, 2017. Assoc. Editor: Kunio Hasegawa.

J. Pressure Vessel Technol 139(4), 041205 (Apr 21, 2017) (10 pages) Paper No: PVT-16-1218; doi: 10.1115/1.4036427 History: Received November 20, 2016; Revised March 13, 2017

For the design of a transmission piping system, a stress intensification factor (SIF) is generally used for the stress calculations of piping components due to external forces, and the solutions for the single-walled piping components can be found in the existing design codes. However, it is quite difficult to obtain the reliable estimations for pipe-in-pipes (PIPs) from the existing solutions, because the PIPs show significantly different behaviors compared to the single-walled piping components due to the restraint effect induced by the outer pipe of the PIP. In this paper, the estimation schemes for the stress behaviors of the PIPs were proposed based on the detailed finite element (FE) analyses. In order to quantify the restraint effect, the FE analyses were conducted by considering various geometric variables of the PIPs under an internal pressure and a global bending moment. Based on the FE results, the tabular and closed-form solutions of the SIFs of PIPs were newly proposed. Finally, the proposed SIF estimations were validated against numerical results.

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References

Figures

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Fig. 1

Configurations of pipe-in-pipe components

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Fig. 4

Variation of stress at the bulkhead part according to the number of elements in thickness direction of the inner pipe (Ne)

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Fig. 2

Schematics of PIP employed in this study

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Fig. 10

Effects of the fillet radius of the bulkhead on the axial stress at the stress concentration locations under (a) internal pressure and (b) global bending moment (Rm/t = 10, Rm,o/Rm = 1.75, to/t = 0.5)

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Fig. 7

Comparisons of the proposed estimations with the FE results of PIPs under internal pressure: (a) iP,s and (b) iP,b (Rm/t = 10)

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Fig. 8

Comparisons of the proposed estimations with the FE results of PIPs under global bending moment: (a) iM,s and (b) iM,b (Rm/t = 10)

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Fig. 6

Normalized axial stress distributions and SCLs for stress linearization at the bulkhead part under (a) internal pressure and (b) global bending moment (Rm/t = 10, Rm,o/Rm = 1.75, to/t = 0.5)

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Fig. 5

Distributions of the axial stress of the PIP along longitudinal direction of inner pipe and their comparisons with those of single-walled pipe under (a) internal pressure and (b) global bending moment (Rm/t = 10, Rm,o/Rm = 1.75, to/t = 0.5)

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Fig. 9

Effects of the bulkhead thickness on the axial stress atthe stress concentration locations under (a) internal pressure and (b) global bending moment (Rm/t = 10, Rm,o/Rm = 1.75, to/t = 0.5)

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Fig. 3

FE model of the bulkhead part of the PIP

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