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Research Papers: Design and Analysis

Unique Design of Pressure Vessel With Tooth-Locked Quick-Actuating Closures Based on Finite Element Model Analysis

[+] Author and Article Information
Wenxian Su

Institute of Chemical Machinery
and Process Equipment,
University of Shanghai for Science
and Technology,
Shanghai 200093, China
e-mail: digestsu@163.com

Wanyi Geng

Institute of Chemical Machinery
and Process Equipment,
University of Shanghai for Science
and Technology,
Shanghai 200093, China
e-mail: gwyhsd@126.com

G. E. O. Widera

Professor
Emeritus of Mechanical Engineering
Marquette University,
Milwaukee, WI 53233
e-mail: geo.widera@marquette.edu

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received January 13, 2016; final manuscript received July 18, 2016; published online October 11, 2016. Assoc. Editor: Allen C. Smith.

J. Pressure Vessel Technol 139(3), 031201 (Oct 11, 2016) (8 pages) Paper No: PVT-16-1007; doi: 10.1115/1.4034407 History: Received January 13, 2016; Revised July 18, 2016

A novel method is developed for the design of pressure vessels with tooth-locked quick-actuating closures by considering the contact between the teeth and utilizing the surface-to-surface contact model with contact element and coulomb friction. Elastic and elastic–plastic analyses via the finite element method were employed. It is shown that these pressure vessels can meet the requirements of strength and fatigue.

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References

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Figures

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Fig. 1

General view of pressure vessel with tooth-locked quick-actuating closures

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Fig. 2

Sketch of tooth-locked quick-actuating closure vessel with spherical head: 1—spherical head, 2—upper flange, 3—lower flange, 4—sealing groove, and 5—cylindrical shell

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Fig. 3

Sketch of design parameters

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Fig. 4

Finite element model of tooth-locked quick-actuating closure device

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Fig. 5

Boundary condition for loading

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Fig. 6

Boundary condition for displacement

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Fig. 7

Sketch of critical planes of tooth-locked quick-actuating closure pressure vessel

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Fig. 8

Maximum principal strain distribution under collapse load

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Fig. 9

Von Mises stress distribution under collapse load

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Fig. 10

Deformation of tooth-locked quick-actuating closure pressure vessel

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Fig. 11

Collapse load defined by load–strain curve of spherical head vertex

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Fig. 12

Collapse load defined by load–strain curve of the connected section of upper flange with spherical head

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Fig. 13

Collapse load defined by load–strain curve of the connected section of lower flange with cylinder

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Fig. 14

Collapse load defined by load–strain curve of far from discontinuous structural section of the cylinder

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