Metal Fatigue Analysis Handbook: Practical Problem-solving by Yung-Li Lee

By Yung-Li Lee

Understand why fatigue occurs and the way to version, simulate, layout and try for it with this useful, industry-focused reference

Written to bridge the expertise hole among academia and undefined, the Metal Fatigue research Handbook provides cutting-edge fatigue theories and applied sciences along traditionally used practices, with operating examples integrated to supply an informative, sensible, entire toolkit of fatigue research.

Prepared by means of knowledgeable workforce with broad commercial, study and professorial event, the e-book might help you to understand:

  • Critical elements that reason and have an effect on fatigue within the fabrics and buildings when it comes to your work
  • Load and tension research as well as fatigue damage―the latter being the only concentration of many books at the subject
  • How to layout with fatigue in brain to fulfill sturdiness requirements
  • How to version, simulate and attempt with assorted fabrics in several fatigue scenarios
  • The value and obstacles of alternative types for inexpensive and effective testing

Whilst the publication specializes in theories everyday within the car undefined, it's also an awesome source for engineers and analysts in different disciplines similar to aerospace engineering, civil engineering, offshore engineering, and business engineering.

  • The simply booklet out there to deal with cutting-edge applied sciences in load, pressure and fatigue harm analyses and their software to engineering layout for durability
  • Intended to bridge the expertise hole among academia and - written by means of knowledgeable crew with broad business, learn and professorial adventure in fatigue research and checking out
  • An complex mechanical engineering layout instruction manual inquisitive about the wishes engineers inside car, aerospace and comparable business disciplines

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Extra resources for Metal Fatigue Analysis Handbook: Practical Problem-solving Techniques for Computer-aided Engineering

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Road Load Analysis Techniques in Automotive Engineering 11 corresponding multibody system has become practical with advances in computer technology and the development of supporting computational methods. In spite of many notable advances in multibody dynamics analyses, there is no common view about which method is the best for specific applications, computational efficiency, or governing dynamic equation acquisition. There are adherents of Lagrangian methods, Newton–Euler methods, virtual work methods, Gibbs–Appell equations, and Kane’s equations.

5 St,y,max = maximum tensile yield strength Sτ,E = endurance limit for shear stress at 106 cycles Sτ,FL = fatigue limit in shear = shear stress amplitude at 108 cycles Smax = maximum stress Smin = minimum stress S′f = fatigue strength coefficient S′σ,f = fatigue strength coefficient in normal stress σe = fictitious or pseudo stress σe ðxÞ = pseudo stress distribution along x σeE = pseudo endurance limit σemax = maximum pseudo stress at x = 0 T = temperature in degrees Celsius tc = coating layer thickness in μm V = volume of the section of a component xxix Nomenclature Chapter 5 αS = sensitivity shear-to-normal stress parameter αDV = hydrostatic stress sensitivity αNP = nonproportional hardening coefficient for material dependence αoct = hydrostatic stress sensitivity factor αVM = mean stress sensitivity factor in the von Mises failure criterion α * = center of the smallest von Mises yield surface C = constant to make fNP unity under 90o out-of-phase loading Δε = strain range Emeso = Young’s modulus in mesoscopic level Φ = phase angle between two loadings ε e ðtÞ = macroscopic elastic strain tensor at a time instant t εemeso ðtÞ = mesoscopic elastic strain tensor at a time instant t εpmeso ðtÞ = mesoscopic plastic strain tensor at a time instant t η = material constant fGD = scaled normal stress factor fNP = nonproportional loading path factor for the severity of loading paths G = factor to account the stress gradient effect k = σE,R=−1/τE Kb,t = elastic stress concentration factor due to bending kF = normal stress sensitivity factor ko = monotonic strength coefficient Kt,t = elastic stress concentration factor due to torsion k′ = cyclic strength coefficient no = monotonic strain hardening exponent n′ = cyclic strain hardening exponent φ = inclination angle between x′ and z axis φ* = interference plane angle with respect to the x-y plane ρ * = residual stress tensor in the mesoscopic scale smeso,1 ðtÞ = largest mesoscopic deviatoric principal stress at a time instant t smeso,3 ðtÞ = smallest mesoscopic deviatoric principal stress at a time instant t SðtÞ = macroscopic deviatoric stress tensor at a time instant t s meso ðtÞ = mecroscopic deviatoric tensor at a time instant t SFðtÞ = safety factor at a time instant t [σ]xyz = stress matrix relative to a global xyz coordinate system [σ]x′y′z′ = stress matrix relative to a local x′y′z′ coordinate system xxx Nomenclature σ1 = maximum principal stress σ1,a = maximum principal stress amplitude σ3,a = minimum principal stress amplitude σa = applied in-phase normal stress amplitude σE,R=−1 = fully reversed fatigue limit for normal stress σh = hydrostatic stress σeq,m = equivalent mean stress σmeso,h ðtÞ = mesoscopic hydrostatic stress at a time instant t σn,max = maximum normal stress on a critical plane σPS,a = the maximum principal stress amplitude (= σ1,a ) σt,u = ultimate tensile strength σt,y = yield strength in tension σVM,a = von Mises stress amplitude σVM,a ðΦ = 90°Þ = 90° out-of-phase von Mises stress amplitude σVM,a ðΦ = 0°Þ = in-phase von Mises stress amplitude σVM,m = von Mises mean stress σVM,a,NP = equivalent nonproportional stress amplitude σx = normal stress in a local x-y coordinate σex = pseudo normal stress in x axis σey = pseudo normal stress in y axis σ′f = fatigue strength coefficient !

A i . δ! δW = ∑ Fi . δ! r i + ∑ C i . δ! r i − ∑ mi! 5) i If arbitrary virtual displacements are assumed to be in directions that are orthogonal to the constraint forces, the constraint forces don’t do work. Such displacements are said to be consistent with the constraints. This leads to the formulation of d’Alembert’s principle, which states that the difference between applied forces and inertial forces for a dynamic system does not do virtual work: δW = ∑ðFi − mi ai Þ . 6) i There is also a corresponding principle for static systems called the principle of virtual work for applied forces.

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