von Mises yield criterion for tube loaded by internal and external pressures and axial stress.
von Mises yield criterion for tube loaded by internal and external pressure and axial stress, ISO 13679 or API RP 5C5 representation.
von Mises yield criterion expressed in terms of internal and external pressure and effective stress.
Stress along the pipe's circumference, perpendicular to the axial direction, when pressure is applied.
Effective stress acting in the radial direction, perpendicular to the longitudinal axis of the pipe.
The direction of the longitudinal stress in a pipe is parallel to the longitudinal axis of its centerline axis.
The component of axial stress not due to bending, assumed uniform across any cross section.
The axial stress due to solely to bending. The stress can be positive (tension) or negative (compression), depending on the location of the point in the cross section.
The torsional shear stress is acting in the circumferential direction on the pipe cross section.
The equivalent stress based on internal and external pressures, axial force, torsional moment and bending defined as a tube curvature.
The equivalent stress based on internal and external pressures, axial force, and bending and torsional moments.
The equivalent stress based on internal and external pressures, axial force, torsional moment and absence of bending.
A design equation for internal pressure of the pipe body at yield with capped-end conditions.
A design equation for internal pressure of the pipe body at yield with open-end conditions.
A design equation for axial tensile force of the pipe body at yield.
The collapse design equation for load cases with dominated external pressure. This approach combines theoretical, numerical and statistical tools.
The collapse design equations for THICK/THIN pipes under external pressure. This approach is based on geometric charts for A and B factors.
The design equations obtaining the critical external pressure of an unstiffened perfect cylindrical shell. This approach includes 4 analytical formulations.
The component of axial stress + bending for each Bolt, assumed even location of the bolt pattern over PCD. Calculations disregard the strength of the other parts of the test cell except the Bolts.
The component of axial stress for the threaded section, assumed pressurized threads. Calculations disregard the strength of the other parts of the test cell except the threads.
The component of axial stress for the threaded section, assumed non-pressurized threads. Calculations disregard the strength of the other parts of the test cell except the threads.
Differential pressure is translated into piston force to shear the ring over the full diameter.
Differential pressure is translated into piston force to shear the ring with cutouts over the full diameter.
Differential pressure is translated into piston force to shear the pins installed equally over the full diameter.
Both threaded pin and box make contact at the internal and external shoulders. Additional torque is translated into axial stress across the thread relief of the pin and box.
Threaded pin makes contact at the internal shoulder. Additional torque is translated into axial stress across the thread relief of the box.
Threaded box makes contact at the external shoulder. Additional torque is translated into axial stress across the thread relief of the pin.
Model of the stress-strain curve is considering the strain hardening characteristics with input values at specified temperature.
Smooth bar design fatigue curves for different materials with the known stress amplitude.
Screening options, using Method A or Method B, determine the need for fatigue analysis.
Model of the de-rating young's modulus property of a material due to evaluated temperature.
Model of the de-rating yield strength property of a material due to evaluated temperature.
Model of the de-rating ultimate tensile strength property of a material due to evaluated temperature.
