Design of Machine and Structural PartsA fully developed and very practical presentation of the subject of form design of machine components is provided in this book, including how to recognize what form or shapes cause what stress patterns and how to apply the information to an overall design. Techniques are presented that guide the design engineer to the correct kind of element to use without the need of calculations; how to choose shapes that produce efficient stress patterns. Also included is a brief review of strength/design procedures; the nature of efficient and inefficient stress patterns are covered, general principles of component design, optimizing strength-to-weight ratios, considerations for buckling and impact and the design of joints. |
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Page 74
... differential equation for the stress function of a cross section for a torqued bar has the same form as the differential equation for the shape of a stretched membrane , originally flat , which is held at the edges of the cross section ...
... differential equation for the stress function of a cross section for a torqued bar has the same form as the differential equation for the shape of a stretched membrane , originally flat , which is held at the edges of the cross section ...
Page 75
... differential equation of the shear stress function of a cross section for a torsionally loaded bar is given by [ 25 , p . 295 ] 226 ax2 a26 + ду = F = -2G0 where is called the stress function of x and y and 0 is the angle of twist ...
... differential equation of the shear stress function of a cross section for a torsionally loaded bar is given by [ 25 , p . 295 ] 226 ax2 a26 + ду = F = -2G0 where is called the stress function of x and y and 0 is the angle of twist ...
Page 111
... differential equation for torsion deflection is [ 8 , p . 293 ] d2u + jT du = 0 dx2 El dx ( 8-18 ) ( 8-19 ) The general solution to this first - order differential equation in terms of du / dx is du dx Tx Tx = A cos - jA sin ΕΙ EI ...
... differential equation for torsion deflection is [ 8 , p . 293 ] d2u + jT du = 0 dx2 El dx ( 8-18 ) ( 8-19 ) The general solution to this first - order differential equation in terms of du / dx is du dx Tx Tx = A cos - jA sin ΕΙ EI ...
Contents
INTRODUCTION TO FORM DESIGN | 1 |
EFFICIENT AND INEFFICIENT STRESS PATTERNS | 27 |
DESIGNING FOR RIGIDITY | 36 |
Copyright | |
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Common terms and phrases
avoirdupois bending moment bending stress bh³ body bolt cantilever beam compression Considerations of Stress contact stress contact surface cross section cross-sectional area crowned tooth cylinders deflection diameter efficient Engineering Considerations equations example flow of force flux force flow free-body diagram geometry given Hertz Hertz contact stress hole inch inefficient stress patterns inertia joint elements joule Juvinall k₁ k₂ keyway kilogram lbf/in length load distribution material maximum stress McGraw-Hill membrane analogy meter modulus of elasticity moment of inertia neutral axis newton newton/meter² normal stress notch plate portion principle R₁ R₂ ratio relative stiffness rigid rivet round bar shape refinement shear stress shown in Figure shows spline spot contact spring constant spring model sprocket steel Stiffeners Strain strap strength Strength of Materials strength-to-weight stress concentration stress distribution tensile tensile stress tension thread torque transverse transverse-shear tube uniform shear uniform stress