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Research Papers: Design and Analysis

Experimental Investigation on Buckling of Ellipsoidal Head of Steel Nuclear Containment

[+] Author and Article Information
Keming Li, Zekun Zhang, Chaohua Gu, Xiaoping Zhang

Institute of Process Equipment,
Zhejiang University,
Hangzhou 310027, China

Jinyang Zheng

Institute of Process Equipment,
Zhejiang University,
Hangzhou 310027, China;
State Key Laboratory of Fluid Power
and Mechatronic Systems,
Zhejiang University,
Hangzhou 310027, China
e-mail: jyzh@zju.edu.cn

Shenghua Liu, Honghui Ge

Shanghai Nuclear Engineering Research
and Design Institute,
Shanghai 200233, China

Caisheng Gu

Yixing Hokkai Head Plate Co., Ltd,
Yixing 214212, China

Guanghua Lin

Changzhou Saifu Chemical Engineering
Equipment Installation Co., Ltd,
Changzhou 213034, China

1Corresponding author.

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received March 25, 2017; final manuscript received September 16, 2017; published online October 19, 2017. Assoc. Editor: Steve J. Hensel.

J. Pressure Vessel Technol 139(6), 061206 (Oct 19, 2017) (9 pages) Paper No: PVT-17-1060; doi: 10.1115/1.4038013 History: Received March 25, 2017; Revised September 16, 2017

A containment of a nuclear power plant is a final barrier against the release of radioactive materials and withstands internal pressure due to an accident. Buckling is a critical failure mode of an ellipsoidal head of steel containment vessel under internal pressure. First, a vessel was designed to measure buckling pressure and shape of the ellipsoidal head. Second, an experiment was successfully performed on an ellipsoidal head which has a diameter of 4797 mm, a radius-to-height ratio of 1.728, and a thickness of 5.5 mm. The initial shape and deformations of the ellipsoidal head were measured by using three-dimensional (3D) laser scanners. The detailed buckling characteristics including shapes, deformations, strains of buckles, and buckling pressures were obtained. Finally, initial buckling pressures were predicted by nonlinear finite element analysis considering the initial measured and the initial perfect shapes of the ellipsoidal head, respectively. The agreement between the initial experimental buckling pressure and that predicted by the analysis considering the initial measured shape is good.

Copyright © 2017 by ASME
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References

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Figures

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Fig. 1

Test vessel geometry: (a) plan view and (b) section A-A

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Fig. 3

Ellipsoidal head geometry

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Fig. 4

Prediction of plastic collapse pressure of the ellipsoidal head: (a) true stress–strain curve of SA-738 Gr.B from ASME Section VIII-2, (b) meshed model, and (c) pressure-plastic strain curve

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Fig. 5

Stress analysis for the test vessel: (a) meshed model and (b) plot of von Mises plastic strain at design pressure

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Fig. 6

Protection against buckling for the spherical head: (a) meshed model and (b) buckling mode

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Fig. 7

Locations of strain gauges at the knuckle

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Fig. 8

A general view of the test vessel under test

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Fig. 9

The pressuring and measuring system

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Fig. 10

A contour for the buckles measured by the 3D laser scanners

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Fig. 11

Deformations of the buckle (236 deg)

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Fig. 12

Buckle occurrences

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Fig. 13

The buckles after the test: (a) 5 deg and 338 deg, (b) 312 deg and 286 deg, (c) 263 deg, 248 deg, 236 deg, and 228 deg, (d) 208 deg and 187 deg, (e) 108 deg and 80 deg, and (f) 55 deg and 35 deg

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Fig. 14

Distribution of strains at the knuckle at 1.70 MPa

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Fig. 15

Strains-pressure curves of gauge 19

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Fig. 16

Meshed model for predicting initial buckling pressure

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Fig. 17

Prediction of initial buckling pressure of the ellipsoidal head considering measured shape: (a) deformed shape and (b) pressure—radial displacement curves

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Fig. 18

Prediction of initial buckling pressure of the ellipsoidal head considering perfect shape: (a) deformed shape and (b) pressure—radial displacement curves

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