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Design and Analysis

The Influence of Connection Geometry on the Fatigue Life of National Pipe Thread Threaded Pipe Couplings

[+] Author and Article Information
Jeroen Van Wittenberghe

e-mail: Jeroen.VanWittenberghe@UGent.be

Patrick De Baets

e-mail: Patrick.DeBaets@UGent.be

Wim De Waele

e-mail: Wim.DeWaele@UGent.be

Jan De Pauw

Ghent University
Laboratory Soete
St.-Pietersnieuwstraat 41
9000 Ghent, Belgium
e-mail: Jan.DePauw@UGent.be

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received September 14, 2010; final manuscript received May 8, 2012; published online November 28, 2012. Assoc. Editor: Hakim A. Bouzid.

J. Pressure Vessel Technol 135(1), 011201 (Nov 28, 2012) (7 pages) Paper No: PVT-10-1137; doi: 10.1115/1.4007284 History: Received September 14, 2010; Revised May 08, 2012

In this paper, four-point bending experiments are performed to determine the fatigue life of several threaded pipe couplings. It is shown that fatigue life of these couplings can be improved by designing them with more uniform load distribution in the threads, achieved through reducing the global and local stiffness of the coupling. Finite element simulations of a 2D axisymmetric model show consistence between experimental observation and analytical modeling. A 3D finite element simulation, which includes nonlinear material behavior, elaborate contact properties and represents the coupling geometry more accurately, is also performed to evaluate the 2D axisymmetric finite element model.

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Figures

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Fig. 1

Tested configurations: (a) standard NPT, (b) NPT coupling with reduced box length, (c) NPT coupling with reduced box wall thickness, and (d) BSPT connection

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Fig. 3

Schematic section view of a test sample

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Fig. 2

Four-point bending fatigue setup

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Fig. 13

Comparison between (a) the 3D model under bending and (b) the 2D axisymmetric with a uniform axial tensile load of 100 MPa

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Fig. 14

von Mises stress along the inside wall of the pin and the outside wall of the box in case of a made up connection with an additional load

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Fig. 4

S-N curve for the standard NPT configuration obtained for a load ratio R = 0.1

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Fig. 9

Fatigue crack initiated at the LET of the pin in the BSPT connection

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Fig. 5

Fatigue crack initiated at the LET of the pin in the standard NPT connection

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Fig. 6

Fracture surface of the fatigue crack in a standard NPT sample

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Fig. 7

S-N curve for configurations B and C obtained for a load ratio R = 0.1

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Fig. 8

S-N curve for the BSPT configuration obtained for a load ratio R = 0.1

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Fig. 15

Load distribution of the different configurations

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Fig. 10

Comparison between (a) the 3D model and (b) the 2D axisymmetric model for make-up

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Fig. 11

von Mises stress along the inside wall of the pin and the outside wall of the box in case of make-up

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Fig. 12

Forces to simulate the four-point bending

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