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Research Papers: Materials and Fabrication

Principal Stress-Based Equation for Multi-Axial Fatigue Analysis of Preloaded Threaded Fasteners

[+] Author and Article Information
Amir Kazemi

Department of Mechanical Engineering,
Oakland University,
2721 Patrick Henry Street, Apt 512,
Auburn Hills, MI 48326
e-mail: akazemi@oakland.edu

Sayed A. Nassar

Fellow ASME
Distinguished University Professor
Room 348,
Engineering Center (EC),
Oakland University,
Rochester, MI 48309
e-mail: nassar@Oakland.edu

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received August 20, 2017; final manuscript received December 4, 2017; published online February 22, 2018. Assoc. Editor: Reza Adibiasl.

J. Pressure Vessel Technol 140(2), 021405 (Feb 22, 2018) (10 pages) Paper No: PVT-17-1160; doi: 10.1115/1.4039124 History: Received August 20, 2017; Revised December 04, 2017

A novel principal stress-based high cycle fatigue (HCF) model is proposed for preloaded threaded fasteners under cyclic tensile-shear loads. The model uses the fastener principal stress amplitude in order to construct a singular multi-axial S–N curve from the conventional uniaxial S–N curve with zero mean stress of bolt along with some experimental data. An material testing system (MTS) fatigue testing system is used first to generate the fastener preload by applying a direct tensile-shear load using a special fixture. Subsequently, the same system is used for applying combined cyclic tensile-shear loading of the fastener at various levels of mean stress. Results show that for the same level of axial stresses, the multi-axial loading would significantly reduce bolt fatigue life as compared to that of uniaxially loaded bolt. Moreover, only one S–N curve would be able to predict the multi-axial HCF of preloaded threaded fasteners, when the maximum principal stress amplitude is used. Detailed discussion of the proposed model results and test data are provided.

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Figures

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Fig. 1

Proposed multi-axial SN curve versus uniaxial fatigue SN curve

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Fig. 2

Test fixture for multi-axial loading [26]

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Fig. 3

Mounted multi-axial loading fixture onto MTS fatigue testing system [26]

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Fig. 6

Effect of loading angle θ on the SN curve for bolt mean stress = 196 MPa

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Fig. 13

Bolt fatigue SN curves for different loading angles at 484 MPa mean stress, based on maximum principal stress amplitude

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Fig. 7

Effect of loading angle θ on the SN curve for bolt mean stress = 326 MPa

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Fig. 8

Effect of loading angle θ on the SN curve for bolt mean stress = 484 MPa

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Fig. 9

Axial-shear stress components

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Fig. 10

Maximum principal stress amplitude

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Fig. 11

Bolt fatigue SN curves for different loading angles at 196 MPa mean stress, based on maximum principal stress amplitude

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Fig. 12

Bolt fatigue SN curves for different loading angles at 326 MPa mean stress, based on maximum principal stress amplitude

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Fig. 4

Static uniaxial and shear fracture modes

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Fig. 5

Fatigue failures at different loading orientations

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Fig. 14

Bolt fatigue SN curves based on maximum principal stress amplitude

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Fig. 15

Bolt fatigue SN curves based on von-Mises stress amplitude

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Fig. 16

Experimental validation data of fatigue life estimation

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