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Research Papers: Design and Analysis

A Creep Buckling Design Method of Elliptical Heads Based on the External Pressure Chart

[+] Author and Article Information
Fang Liu

School of Mechanical and Power Engineering,
East China University of
Science and Technology,
130 Meilong Road,
Shanghai 200237, China
e-mail: 1107937101@qq.com

Jian-Guo Gong

School of Mechanical and Power Engineering,
East China University of
Science and Technology,
130 Meilong Road,
Shanghai 200237, China
e-mail: jggong@ecust.edu.cn

Fu-Hai Gao

China Institute of Atomic Energy,
Beijing 102413, China
e-mail: golfhigh@163.com

Fu-Zhen Xuan

School of Mechanical and Power Engineering,
East China University of
Science and Technology,
130 Meilong Road,
Shanghai 200237, China
e-mail: fzxuan@ecust.edu.cn

1Corresponding author.

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received August 16, 2018; final manuscript received February 28, 2019; published online March 21, 2019. Assoc. Editor: Kiminobu Hojo.

J. Pressure Vessel Technol 141(3), 031203 (Mar 21, 2019) (12 pages) Paper No: PVT-18-1161; doi: 10.1115/1.4043009 History: Received August 16, 2018; Revised February 28, 2019

The buckling design criteria of elliptical heads in ASME VIII-1, ASME NH, and RCC-MRx are reviewed and compared. Accordingly, an external pressure chart (EPC) based buckling design approach is developed for elliptical heads in the creep range. Results indicate that for instantaneous buckling design, RCC-MRx predicts higher allowable pressure compared with ASME NH, which is ascribed to the smaller design factor. The proposed method produces a similar result with that given by ASME VIII-1. By contrast, the proposed method leads to a reasonably conservative result with the factor n of 0.03 for the creep buckling design. While the simplified method in RCC-MRx provides an over-conservative solution.

Copyright © 2019 by ASME
Topics: Pressure , Creep , Design , Buckling
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References

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Figures

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Fig. 1

Creep buckling design diagram for 316 L–N at 550 °C

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Fig. 2

External pressure chart for 2.25Cr–1Mo steel at 538 °C

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Fig. 3

External pressure chart for 316 L

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Fig. 4

Mesh model of elliptical head (a/b =2)

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Fig. 5

Effect of number of elements on critical pressure (a/b =2)

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Fig. 6

Effect of number of elements on critical pressure (t/a =1.4 × 10−3)

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Fig. 7

Critical pressure Pc for various defect index δ (a/b =2)

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Fig. 8

Critical pressure Pc for various defect index δ (t/a =1.4 × 10−3)

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Fig. 9

Buckling behavior of ellitipical heads (deformation scale factor = 10): (a) first-order mode by eigenvalue analysis (a/b = 2, t/a = 1.4 × 10−3); (b) nonlinear buckling analysis (a/b = 2, t/a = 1.4 × 10−3); (c) first-order mode by eigenvalue analysis (a/b = 2, t/a = 2.6 × 10−3); (d) nonlinear buckling analysis (a/b = 2, t/a = 2.6 × 10−3); (e) pressure–displacement curve (a/b = 2, t/a = 1.4 × 10−3); and (f) pressure-displacement curve (a/b = 2, t/a = 2.6 × 10−3)

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Fig. 10

Allowable pressure Pa for various ratios of thickness to semimajor axis t/a (a/b =2)

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Fig. 11

Allowable pressure Pa for various ratios of semimajor axis to semiminor axis a/b (t/a =1.4 × 10−3)

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Fig. 12

Comparison of critical pressure predicted by EPC, ASME VIII-1 and experiment

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Fig. 13

Allowable pressure Pa for different creep time T (a/b =2, t/a =1.4 × 10−3, and n =0.03)

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Fig. 14

Allowable pressure Pa for various ratios of thickness to semimajor axis t/a (a/b =2, T =10,000 h, and n =0.03)

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Fig. 15

Allowable pressure Pa for various ratios of semimajor axis to semiminor axis a/b (t/a =1.4 × 10−3, T =10,000 h, and n =0.03)

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Fig. 16

Critical pressure Pc for various ratios of thickness to semimajor axis t/a (a/b =2)

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Fig. 17

Critical pressure Pc for various ratios of semimajor axis to semiminor axis a/b (t/a =1.4 × 10−3)

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Fig. 18

Comparison of critical pressure for 2.25Cr–1Mo and 316 L–N (a/b =2 and t/a =1.4 × 10−3)

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Fig. 19

Effect of factor n on allowable buckling pressure (a/b =2 and t/a =1.4 × 10−3)

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