Introduction to Mechanics of Deformable Solids |
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Page 98
... equation in P7 , P8 , and P9 , provided of course that a force - elongation relation exists . It does for linear - elastic bars with zero or known initial stress . For zero initial stress & has the form PL / AE + aL0c , where , is the ...
... equation in P7 , P8 , and P9 , provided of course that a force - elongation relation exists . It does for linear - elastic bars with zero or known initial stress . For zero initial stress & has the form PL / AE + aL0c , where , is the ...
Page 386
... equation ( 15.3 : 1 ) . No external force should be applied at F ( Fig . 15.4b ) . The residual system Q ' , R ' , S ' is in equilibrium ; P13 R ' , P11 = Q ' , Pis = S ' ; and virtual work gives = P14 P15 0 = P15 AE 6. ( PE ) + P. ( PE ) ...
... equation ( 15.3 : 1 ) . No external force should be applied at F ( Fig . 15.4b ) . The residual system Q ' , R ' , S ' is in equilibrium ; P13 R ' , P11 = Q ' , Pis = S ' ; and virtual work gives = P14 P15 0 = P15 AE 6. ( PE ) + P. ( PE ) ...
Page 395
... equation of virtual work . Equation ( 15.3 : 7 ) is simply = IB Q'VA - Q'UB + [ Q ' ( XB ― XA ) ] 0B = [ ** [ Q ' ( x [ ** [ Q ′ ( x − xa ) ] M dx ΕΙ Theorem II is proved as well as forced upon you by virtual - work considerations ...
... equation of virtual work . Equation ( 15.3 : 7 ) is simply = IB Q'VA - Q'UB + [ Q ' ( XB ― XA ) ] 0B = [ ** [ Q ' ( x [ ** [ Q ′ ( x − xa ) ] M dx ΕΙ Theorem II is proved as well as forced upon you by virtual - work considerations ...
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applied assemblage axes axial force beam behavior cantilever centroid circumferential column compatibility components of stress constant creep cylinder deflection diameter direction displacement elastic-perfectly plastic elongation equations of equilibrium factor of safety free-body sketch homogeneous idealization increase inelastic initial interior pressure isotropic J₂ Kelvin Kelvin material limit linear Maxwell linear-elastic linear-viscoelastic linear-viscous load maximum Maxwell material modulus Mohr's circle neutral axis nonlinear normal stress outer P₁ P₂ perfectly plastic perpendicular plane plastic-limit principal stresses Prob problem pure bending radial radius ratio rectangular residual stress rigid end plates rotation shaft shear strain shear stress shell shown in Fig simple shear solution statically determinate steel stress and strain stress-strain curve stress-strain relations Suppose surface symmetry T₁ T₂ temperature tensile tensile stress thick-walled time-dependent torque torsion uniform unloading versus viscous yield curve yield stress Young's modulus zero ΕΙ σα σο στ