Search results for query: *

@mskds545 Yes, you are right, DNV-RP-C203 1 mm radius is only verified in local notch stress method and the associated specific fatigue curve. I agree that a structural stress method, or hot spot method, maybe preferable. ASME code currently does not provide this method. It is popular in...

I do find a reference about the 1 mm radius, follow the Link and scroll to the very bottom of the page.

I agree that the stress values are strongly dependent on the radius value. However, in the FEA model, an 1 mm radius bring an infinity stress to a sensible level, which makes the analysis useful. The actual radius varies greatly in reality. The radius will be different even at different spots...

A general practice is to model an 1 mm radius at the toe of the weld to avoid singularity. This practice matches the reality that absolute "sharp' edge does not exist in welding.

Normally the tensile residual stresses are very high at welded connections. Even superimposed with compressive stresses, the resultant stress may still in tension. That's why mean stress is NORMALLY not considered. However, for some cases, mean stress may be considered. See...

Calculate fatigue life of components first. If the fatigue life of a component is infinity, there is no need for inspection. Otherwise the frequency of inspection is determined by calculated fatigue life of the component.

If you consider air resistance, the stresses will go up significantly.

Let's get to the basics. No matter the bolt is axial tension or axial compression, the material will eventually fail by shear due to fatigue. Steel is a ductile material. Under repeated cyclic loading, the crystals will slip in the shear plane in a microscope scale, and eventually fail on the...

Look up Tab. {3.2}-1: Fatigue resistance values for structural details in steel and aluminium assessed on the basis of nominal stresses. The FAT classes below FAT63 are FAT56 and FAT50, etc. I believed that you had a typo FAT630.