Abstract

Gasketed bolted flange joints are the most critical components in pipelines for their sealing and strength under operating conditions. Most of the work available in literature is under static loading, whereas in industry, cyclic loads are applied due to the vibrating machinery such as motors, pumps, sloshing in offshore applications and in the ships etc. In this study a three dimensional finite element analysis of a gasketed joint is carried out using a spiral wound gasket under bolt up and dynamic operating conditions (internal pressure, axial and bending) singly and in combination. The cyclic axial loads are concluded relatively more challenging for both the sealing and strength of the joint. Higher magnitudes of loads and frequencies are also observed more challenging to the joints performance.

Highlights

  • Gasketed pipe flange joints are widely used to connect pipe-to-pipe or pipe-to-otherequipment in industries including nuclear, petrochemical, processing, pressure vessels, and piping industries etc

  • The performance worsens under bolt-up plus harmonic axial loading

  • The value of the stress is observed to be increasing with increase in harmonic axial loading

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Summary

INTRODUCTION

Gasketed pipe flange joints are widely used to connect pipe-to-pipe or pipe-to-otherequipment in industries including nuclear, petrochemical, processing, pressure vessels, and piping industries etc. Most of the previous work is limited to bolt up, internal pressure, and static external loading only, but the actual conditions of the industry are dynamic in nature. These dynamic loads may be applied by various vibrating machinery like pumps, motors, and gear machinery. Vibrations may be due to sloshing effects and offshore applications These dynamic conditions are the actual risk to the strength and sealing capability of the pipe joints. A Flange joint of four-inch 900# class is used in the present study

Modeling and Meshing
Material Properties
BOUNDARY CONDITIONS
Harmonic axial loading only
Harmonic Bending Loading only
Internal Pressure plus Bending Loading
Harmonic Axial Loading only
Internal Pressure plus Harmonic Axial Loading
Internal Pressure plus Harmonic Bending Loading
Displacement versus Time at Flange
Internal Pressure plus Harmonic Bending Loading only
CONCLUSION

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