Mechanical Properties of Materials


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1 Mechanical Properties of Materials Strains Material Model Stresses Learning objectives Understand the qualitative and quantitative description of mechanical properties of materials. Learn the logic of relating deformation to external forces. 31
2 Tension Test Machine Tension Test Tensiontest Specimens P L o d o L o + δ P ε δ = σ L o P = = A o P πd o 4 Normal Stress σ σ u Ultimate Stress σ f Fracture Stress σ y Offset Yield Stress σ p A Proportional Limit I B Loading Unloading Reloading C D E Rupture O Offset strain H Plastic Strain F Elastic Strain G Normal Strain ε Total Strain 32
3 Definitions The point up to which the stress and strain are linearly related is called the proportional limit. The largest stress in the stress strain curve is called the ultimate stress. The stress at the point of rupture is called the fracture or rupture stress. The region of the stressstrain curve in which the material returns to the undeformed state when applied forces are removed is called the elastic region. The region in which the material deforms permanently is called the plastic region. The point demarcating the elastic from the plastic region is called the yield point. The stress at yield point is called the yield stress. The permanent strain when stresses are zero is called the plastic strain. The offset yield stress is a stress that would produce a plastic strain corresponding to the specified offset strain. A material that can undergo large plastic deformation before fracture is called a ductile material. A material that exhibits little or no plastic deformation at failure is called a brittle material. Hardness is the resistance to indentation. The raising of the yield point with increasing strain is called strain hardening. The sudden decrease in the area of crosssection after ultimate stress is called necking. 33
4 Material Constants σ Β B Slope = E t Normal Stress σ Slope = E A Slope = E s E = Modulus of Elasticity E t = Tangent Modulus at B E s = Secant Modulus at B O Normal Strain ε σ = Eε Hooke s Law E Young s Modulus or Modulus of Elasticity Poisson s ratio: ν = ε lateral ε longitudnal τ = Gγ G is called the Shear Modulus of Elasticity or the Modulus of Rigidity 34
5 3.23 A circular bar of length 6 inch and diameter of 1 inch is made from a material with a Modulus of Elasticity of E=30,000 ksi and a Poisson s ratio of ν=1/3. Determine the change in length and diameter of the bar when a force of 20 kips is applied to the bar. 35
6 3.27 An aluminum rectangular bar has a crosssection of 25 mm x 50 mm and a length of 500 mm. The Modulus of Elasticity of E = 70 GPa and a Poisson s ratio of ν = Determine the percentage change in the volume of the bar when an axial force of 300 kn is applied to the bar. 36
7 Logic in structural analysis Displacements Kinematics 1 External Forces and Moments Strains 4 Equilibrium Material Models 2 Static Equivalency Internal Forces and Moments 3 Stresses 37
8 3.43 A roller slides in a slot by the amount δ P = 0.25 mm in the direction of the force F. Both bars have an area of crosssection of A = 100 mm 2 and a Modulus of Elasticity E = 200 GPa. Bar AP and BP have lengths of L AP = 200 mm and L BP = 250 mm respectively. Determine the applied force F. B A 75 o 30 o P F Fig. P
9 3.46 A gap of inch exists between the rigid bar and bar A before the force F is applied as shown in Figure The rigid bar is hinged at point C. Due to force F the strain in bar A was found to be µ in/in. The lengths of bar A and B are 30 and 50 inches respectively. Both bars have an area of crosssection A= 1 in 2 and Modulus of Elasticity E = 30,000 ksi. Determine the applied force F. C 75 o B F 24 in 36 in A 60 in Fig. P
10 3.49 The pins in the truss shown in Fig. P3.49 are displaced by u and v in the x and y direction respectively, as given. All rods in the truss have an area of crosssection A= 100 mm 2 and a Modulus of Elasticity E= 200 GPa. u A = mm v A = 0 u B = mm v B = mm u C = mm v C = mm u D = mm v D = mm u E = mm v E = mm u F = mm v F = mm u G = mm v G = mm u H = mm v H = mm Determine the external force P 4 and P 5 in the truss shown in Fig. P3.49 y P 3 x P 4 G P 2 H P 5 F P A B C D E 3 m 3 m 3 m 3 m Fig. P
11 Isotropy and Homogeneity Linear relationship between stress and strain components: ε xx = C 11 σ xx + C 12 σ yy + C 13 σ zz + C 14 τ yz + C 15 τ zx + C 16 τ xy ε yy = C 21 σ xx + C 22 σ yy + C 23 σ zz + C 24 τ yz + C 25 τ zx + C 26 τ xy ε zz = C 31 σ xx + C 32 σ yy + C 33 σ zz + C 34 τ yz + C 35 τ zx + C 36 τ xy γ yz = C 41 σ xx + C 42 σ yy + C 43 σ zz + C 44 τ yz + C 45 τ zx + C 46 τ xy γ zx = C 51 σ xx + C 52 σ yy + C 53 σ zz + C 54 τ yz + C 55 τ zx + C 56 τ xy γ xy = C 61 σ xx + C 62 σ yy + C 63 σ zz + C 64 τ yz + C 65 τ zx + C 66 τ xy An isotropic material has a stressstrain relationships that are independent of the orientation of the coordinate system at a point. A material is said to be homogenous if the material properties are the same at all points in the body. Alternatively, if the material constants C ij are functions of the coordinates x, y, or z, then the material is called nonhomogenous. E For Isotropic Materials: G = ( + ν) 311
12 Generalized Hooke s Law for Isotropic Materials The relationship between stresses and strains in threedimensions is called the Generalized Hooke s Law. ε xx = [ σ xx νσ ( yy + σ zz )] E ε yy = [ σ yy νσ ( zz + σ xx )] E ε zz = [ σ zz νσ ( xx + σ yy )] E γ xy = τ xy G γ yz = τ yz G G = E ( + ν) γ zx = τ zx G ε xx ε yy ε zz = E 1 ν ν ν 1 ν ν ν 1 σ xx σ yy σ zz 312
13 Plane Stress and Plane Strain Plane Stress σ xx τ xy 0 τ yx σ yy Generalized Hooke s Law ε xx γ xy 0 γ yx ε yy 0 ν 0 0 ε zz =  ( σ E xx + σ yy ) Plane Strain ε xx γ xy 0 γ yx ε yy Generalized Hooke s Law σ xx τ xy 0 τ yx σ yy σ zz = νσ ( xx + σ yy ) Plane Stress Plane Strain 313
14 3.78 A 2in x 2 in square with a circle inscribed is stressed as shown Fig. P3.78. The plate material has a Modulus of Elasticity of E = 10,000 ksi and a Poisson s ratio ν = Assuming plane stress, determine the major and minor axis of the ellipse formed due to deformation. 10 ksi 20 ksi Fig. P3.78 Class Problem 1 The stress components at a point are as given. Determine ε xx assuming (a) Plane stress (b) Plane strain σ xx σ yy = = 100 MPa( T) 200 MPa( C) τ xy = 125 MPa E = ν = GPa 314
15 Failure and factor of safety Failure implies that a component or a structure does not perform the function it was designed for. K safety Failure producing value Computed( allowable)value =
16 3.106 An adhesively bonded joint in wood is fabricated as shown. For a factor of safety of 1.25, determine the minimum overlap length L and dimension h to the nearest 1/8th inch. The shear strength of adhesive is 400 psi and the wood strength is 6 ksi in tension. 10 kips h h L Fig. P in h 10 kips 316
17 Common Limitations to Theories in Chapter 47 The length of the member is significantly greater (approximately 10 times) then the greatest dimension in the crosssection. We are away from regions of stress concentration, where displacements and stresses can be threedimensional. The variation of external loads or changes in the crosssectional area is gradual except in regions of stress concentration. The external loads are such that the axial, torsion and bending problems can be studied individually. 317
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