By Dieter Radaj, Michael Vormwald
In 5 chapters, this quantity provides contemporary advancements in fatigue overview. within the first bankruptcy, a generalized Neuber notion of fictitious notch rounding is gifted the place the microstructural aid components rely on the notch establishing perspective in addition to the loading mode. the second one bankruptcy specifies the notch tension issue together with the stress power density and J-integral suggestion whereas the SED procedure is utilized to universal fillet welded joints and to thin-sheet lap welded joints within the 3rd bankruptcy. The forth bankruptcy analyses elastic-plastic deformations within the close to crack tip quarter and discusses motive force parameters. The final bankruptcy discusses thermomechanical fatigue, rigidity, and pressure levels.
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Additional resources for Advanced Methods of Fatigue Assessment
Comparing the maximum stresses in mode 2 and mode 1 (Eq. 8 Limit Value Formulae for the Mode Two Stress Intensity Factor The stress intensity factor KII can be determined from a slender comparison notch (elliptical, parabolic, hyperbolic, keyhole or U-shaped) as the limit value of the maximum notch stress times the square root on the notch radius q when the latter becomes smaller and smaller (q ? 0 equivalent to q/a ( 1 or q/b ( 1). Based on the equations above for js and jr0 ; the following relationships, valid as limit value formulae, can be used: Elliptical (internal) notch: pﬃﬃﬃﬃﬃﬃ KII ¼ 2:5981smax pq; pﬃﬃﬃﬃﬃﬃ KII ¼ 1:0r0max pq ð1:90Þ pﬃﬃﬃﬃﬃﬃ KII ¼ 1:4142r0max pq ð1:91Þ pﬃﬃﬃﬃﬃﬃ KII ¼ 1:5708r0max pq ð1:92Þ pﬃﬃﬃﬃﬃﬃ KII ¼ 0:3489r0max pq ð1:93Þ Parabolic (external) notch: pﬃﬃﬃﬃﬃﬃ KII ¼ 3:6742smax pq; Hyperbolic (external) notch: pﬃﬃﬃﬃﬃﬃ KII ¼ 4:0816smax pq; Keyhole (internal) notch: pﬃﬃﬃﬃﬃﬃ KII ¼ 1:4021smax pq; U-shaped (internal) notch (FE analysis by F.
Summarising the numerical results, the following trends have been found for the support factor in the case of out-of-plane shear loading: • the factor s depends on the real radius q, starting with lower values for q = 0, but converging to a plateau value for q [ qÃ ; 34 1 Generalised Neuber Concept of Fictitious Notch Rounding Fig. 18 Geometry and dimensions of the V-notch specimen considered in the FE analyses, torsional loaded round bar with circumferential V-notch, q = 0 compared with q = qf; the nominal stresses sÃng relating to the gross cross-sectional area; (Berto et al.
By considering different failure criteria combined with plane stress and plane strain conditions, respectively, a comparison has been carried out between the effective stress concentration factor K t given by Eq. 29) and the stress concentration factor Kt(qf) evaluated with fictitious notch rounding, Eq. 30), modified by j. In both cases, the stresses in the specimens are obtained from the FE analysis. The first step is to evaluate Eq. 29), considering the normal or equivalent stress obtained by FE analysis along the bisector of the pointed V-notch.