QQ section property, 327–332, 338, 347RRadial displacement, 606Radial interference, 609Radial stress, 132, 587, 591, 600–601,603–605, 607Radius of curvature, defined, 239Radius of gyration, defined, 673Ramp function, 225Rankine’s theory, 662Recovery, elastic, 50Redundant reactions, 446Redundants, 446–447, 461–463Released beam, 446–447, 461–465Reliability analysis, 78Residual strain, 50Residual stress, 697Resistance, in LRFD, 77Resistance strain gage, 555–556Resultant stress, 532–533, 535Rigid bar, defined, 32Rigid-body displacement, defined, 29Rigid element, defined, 4Rigidity, modulus ofdefined, 56, 138relationship to elastic modulus, 57, 562for selected materials, table, 825–827Roller supports, defined, 194Rosette analysis, 555–557Rotation, angle of, 411rpm, defined, 162SSafety, factor of, 68–69in AISC column formulas, 697–698Saint-Venant’s Principle, 84–85, 135,143, 283Saint-Venant’s theory of torsion, 186Secant formula, 690–695, 707Second moment of area, 139, 243, 790, 794Section modulus, 245, 255, 260, 265–268Section plane, defined, 2Serviceability limit states, 81Service loads, defined, 68Shear, directdouble, 9punching, 11–12single, 8Shear area, 8Shear centerfor channel section, 374–382defined, 373–374852for sections consisting of two rectangles,384–385for semi-circular section, 383–384Shear coupling coefficients, 577Shear flowin built-up beams, 346–352in closed sections, 189–191, 362–363due to torsion, 189–191in thin-walled sections, 359–362in thin-walled tubes, 189–191Shear forcedefined, 7–8diagrams, 196–204, 205–220, 224–234equations for, 829relationship to load and bendingmoment, 205–211Shear-force diagram, 196–204, 205–220,224–234Shear key, 10–11Shear modulusdefined, 56relationship to elastic modulus,57, 562for selected materials, table, 825–826Shear strain, 30, 37–38, 541–546absolute maximum, 547–548, 557maximum in-plane, 547–548relationship to shear stress, 56, 562sign convention for, 38, 544–545torsionalin circular sections, 137–138in noncircular sections, 187transformation equations, 543–544Shear stressabsolute maximum, 504–505,526–527, 537direct shear, 7–9equality on perpendicular planes, 24,482–483horizontal, 327–329, 331–332,338–339, 621in circular sections, 338in flanged sections, 338–339in rectangular sections, 331–332maximum, 566, 602, 608maximum in-plane, 502–505nominal, 183out-of-plane, 586–587relationship to shear strain, 56, 562sign convention for, 493strain-energy density for, 719–720in thin-walled sections, 355–359torsionalin circular sections, 138–139in noncircular sections, 186–191transformation equations, 491–492transverse, 328, 331–332, 338–339,621, 623in circular sections, 338in flanged sections, 338–339in rectangular sections, 331–332Short columns, 675, 697, 698Shrink-fit, 609Sign conventionfor angle of twist, 144for axial deformation, 86for beam deflections, 394for bending moments, 196, 244for curvature, 240for flexural strain, 240for internal bending moment, 196, 244for internal shear force, 196for internal torques, 143–144for Mohr’s circle (stress), 515for normal strains, 31, 544–545for normal stresses, 3, 481, 493for shear-force and bending-momentdiagrams, 196for shear strains, 38, 544–545for shear stresses, 493, 515for torsional rotation angles, 144Significant digits, 3–4Similar triangles, 33, 96, 108, 111, 123Simple beam, defined, 194–195Simply supported beamdeflection formulas, 822Simply supported beam, defined, 194–195Single shear, defined, 8Singularity functions, 224for concentrated forces, 225–226for concentrated moments, 225–226Slenderness ratio, defined, 673, 675, 685Snow load, 67Spherical pressure vessels, 586–588Stable beam, 446Stable equilibrium, 667–671State of stress, defined, 481Statically indeterminate memberswith axial loads, 103–115, 119–126with flexural loads, 445–452, 461–472with elastic supports, 468–472by integration methods, 447–452by superposition methods, 461–472using discontinuity functions, 454–459with torsional loads, 166–180Stem, defined, 255Step function, 224–225Strainabsolute maximum shear, 547–548, 557axial, 31, 56, 86–87, 659compressive, 31defined, 30
flexural, 239–240in-plane shear, 547–548normal, 30–32plane, 541–550, 547–548, 552–554pressure vessels, 591–592principal, 547–548principal, by Mohr’s circle, 552–554shear, 30, 37–38, 137–138, 142, 187,541–548, 552tensile, 31, 240torsional shear, 137–138, 142, 187volumetric, 563Strain element, defined, 540Strain energy, 656–660, 715, 717–718for axial loadings, 658–659elastic, 659–660Strain-energy density, 659–660, 718–720for normal stress, 718–719for shear stress, 719–720units of, 719Strain gages, 31, 555–556Strain hardening, 51, 55Strain invariance, 544Strain rosette, 555–557Strengthultimate, 51, 55ultimate, of selected materials, table,825–826yield, 51, 55yield, of selected materials, table,825–826Strength limit states, 81Stressallowable, 68–69average normal, 129, 504average shear, 8, 11, 189, 334, 348axial, 2, 84–85bearing, 12–14, 69–70biaxial, 566–568, 587, 590–591, 656,657, 659, 662circumferential, 308, 588–590, 598–605,607, 612–614compression, 141, 241, 282, 693–694,697, 707compressive, 12, 623, 707defined, 2flexural, 243, 245, 254, 270hoop, 588–591longitudinal, 588–591, 605maximum, 601–604maximum normal, 129, 140–141, 500,585, 662maximum shear, 8, 23, 138–142,183–186, 332, 499, 503, 506, 515,517, 536–537, 587, 602, 608,621–623, 634, 635maximum shear, by Mohr’s circle, 517nominal, 129–130, 132–133, 183,302–303normal, 479, 566, 575compression, 141, 241, 282, 693–694,697, 707compressive, 12, 623, 707defined, 2–3, 480and hydrostatic state stress, 565tensile, 132, 140, 141tension, 241, 254, 270, 282, 547–548out-of-plane shear, 586–587plane, 483–485, 488–490principal, 499–502principal, by Mohr’s circle, 517radial, 600–601, 603–605, 607residual, 697resultant, 532–533, 535shear, 7–8, 327–329, 331–332, 491–492,621, 623tangential, 586–591, 606tensile, 132, 140, 141, 613thermal, 119in thick-walled cylinders, 598–605torsional shear, 138–139, 186–189triaxial, 588, 659true, 51, 53two-dimensional, 483Stress concentrationunder axial loadings, 129–133defined, 85under flexural loadings, 302–305under torsional loadings, 183–185Stress-concentration factorsfor circular shafts, 183–185, 304for flat bars, 130–133, 303Stress distributionnormal stress, 3, 22, 70, 84–85, 130,241, 276, 282, 293, 320shear stress, 331, 339Stress elementdefined, 481generating, 483–485Stress invariance, 493, 505Stress–strain diagram, 45–55Stress–strain equations, for isotropicmaterials, 560–567Stress trajectory, 129–130, 621–623Stress transformation, 481, 488–496,499–517Strong axis, 255Structural shapes, standard, 255, 256,809–820Structural tees (T-shapes), 255, 256, 815–816Superposition, principle, 295, 313, 423–424,461–463, 561, 577–578, 636, 693Superposition methodfor combined loadings, 636for curved bars, 313for deflections of determinate beams,423–439for indeterminate beam analysis, 461–472Support settlement, defined, 396Symmetry conditions, 397tTable(s)of deflection and slopes of beams,822–823of discontinuity functions, 228of properties of materials,825–827of properties of plane figures, 791of properties of rolled-steel shapes,809–820of properties of wood construction materials,827Tangential stress, 132Temperature effects, 120, 574–576Tensile strain, 31, 240Tensile stress, 132, 140, 141, 613Tension, defined, 2Tension stress, 241, 254, 270, 282,547–548Tension test, 45–47Theories of failuremaximum-distortion-energy,658–661maximum-normal-stress, 662maximum-shear-stress, 657–658Mises equivalent stress, 661–662Mohr’s Failure Criterion, 662–663Thermal expansioncoefficient, for selected materials, table,825–826Thermal expansion, coefficient of, 41Thermal strain, 41Thermal stress, 119Thick-walled pressure vesselsdeformations in, 606–609equations, 831stress in, 598–605Thin-walled pressure vesselscylindrical, 588–591equations, 831spherical, 586–588Thin-walled sections, torsion, 189–191Torque, defined, 10, 135Torque–rotation diagram, 722Torque–twist relationship, 167, 168, 170,173, 178853
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A research-based,online learning en
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MECHANICS OF MATERIALS:An Integrate
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About the AuthorTimothy A. Philpot
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xPREFACEAnimation also offers a new
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xiiPREFACE• Appendix E Fundamenta
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xivPREFACEWhat Do Instructors recei
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ContentsChapter 1 Stress 11.1 Intro
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Chapter 14 Pressure Vessels 58514.1
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2STRESSAddressing these concerns re
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4STRESSnumber begins with the digit
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ExAmpLE 1.3A(1)50 mmB80 kNA 50 mm w
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8STRESSFIGURE 1.2b Free-bodydiagram
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mecmoviesExAmpLEm1.5 A pin at C and
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12STRESSJeffery S. ThomasFIGURE 1.5
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14STRESSFIGURE 1.6 Bearing stress f
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m1.3 Use shear stress concepts for
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applied to beam ABC? Use dimensions
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p1.24 The two wooden boards shown i
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1.5 Stresses on Inclined Sectionsme
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24STRESSSignificanceAlthough one mi
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Thus, to provide the necessary weld
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p1.40 Two wooden members are glued
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30STRAINposition vector between H a
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32STRAINIn developing the concept o
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mecmoviesExAmpLESm2.1 A rigid steel
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p2.4 Bar (1) has a length of L 1 =
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38STRAINIn this expression, θ′ i
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pRoBLEmSp2.11 A thin rectangular po
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SOLUTIONThe thermal strain for a te
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CHAPTER3Mechanical Propertiesof Mat
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(3)(7)(4)(5)(6)Fracture47THE TENSIO
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8049THE STRESS-STRAIN dIAgRAM7060St
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The elastic limit is the largest st
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80Aluminum alloy××53THE STRESS-ST
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The second measure is the reduction
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Values vary for different materials
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before the strain measurement. From
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mecmoviesExERcISEm3.1 Figure M3.1 d
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material is initially 800 mm long a
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CHAPTER4design Concepts4.1 Introduc
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the distributed uniform area loadin
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In some instances, engineers may ne
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both members will be stressed to th
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MecMoviesExAMpLESM4.1 The structure
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bPtPFIGURE p4.3Splice plateBarBarPP
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4.5 Load and Resistance Factor Desi
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79FrequencyLarger γ factors combin
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Limit StatesLRFD is based on a limi
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CHAPTER5Axial deformation5.1 Introd
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The increased normal stress magnitu
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AAAA87dEFORMATIONS IN AxIALLyLOAdEd
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displacement in the horizontal dire
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mecmoviesExAmpLEm5.2 The roof and s
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t = 8 mm, and E = 72 GPa, determine
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d 0to 2d 0 at the other end. A conc
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How are the rigid-bar deflections v
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ExAmpLE 5.4A tie rod (1) and a pipe
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Since the sum of the four interior
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5.5 Statically Indeterminate Axiall
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Step 3 — Force-Deformation Relati
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Successful application of the five-
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Plan the SolutionConsider a free-bo
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Structures with a Rotating Rigid Ba
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(1)Px Bx C113STATICALLy INdETERMINA
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ExERcISESm5.5 A composite axial str
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p5.29 In Figure P5.29, a load P is
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tube has an outside diameter of 1.5
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ExAmpLE 5.7An aluminum rod (1) [E =
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mecmoviesExAmpLEm5.14 A rectangular
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Equations (h) and (i) can be solved
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pRoBLEmSp5.39 A circular aluminum a
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polymer [E = 370 ksi; α = 39.0 ×
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Stress-concentration factor K3.02.8
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of the hole has decayed to a value
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TorsionCHAPTER66.1 IntroductionTorq
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with respect to an adjacent cross s
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the longitudinal axis of the shaft.
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τStressxyτntσn141STRESSES ON ObL
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If a torsion member is subjected to
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ExAmpLE 6.1A hollow circular steel
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Plan the SolutionTo determine the l
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Plan the SolutionThe internal torqu
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mecmoviesExAmpLESm6.4 Determine the
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p6.10 The mechanism shown in Figure
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Furthermore, since gears have teeth
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will be dictated by the ratio of ge
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mecmoviesExAmpLEm6.13 Two solid ste
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6.8 power Transmission161POwER TRAN
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m6.17 A motor shaft is being design
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pulley is a belt having tensions F
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Step 2 — Geometry of Deformation:
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Polar moments of inertia for the al
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Successful application of the five-
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Plan the SolutionAA free-body diagr
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From Equation (e), the allowable in
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Next, consider a free-body diagram
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Polar moments of inertia for the sh
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m6.21 A composite torsion member co
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zD(3)Ay(1)L1,L3N BBL 2(a) Determine
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Stress concentrations also occur at
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For the case of the rectangular bar
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and the angle of twist for a 12 in.
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ExAmpLE 6.13A rectangular box secti
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CHAPTER7Equilibrium of beams7.1 Int
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beam (also called a simple beam). A
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ExAmpLE 7.1Draw the shear-force and
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The negative value for A y indicate
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Plot the FunctionsPlot the function
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ExAmpLE 7.5Draw the shear-force and
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yw aw byw 0xxABCABabLFIGURE p7.4FIG
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w(x) = w G at G. At A, where the di
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the left and right sides of a thin
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General procedure for constructing
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Construct the Bending-Moment Diagra
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ExAmpLE 7.7Draw the shear-force and
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j M(6) = 0 kN ⋅ m (Rule 4: ∆M =
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of M diagram = shear force V). The
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m7.3 Dynamically generated shear-fo
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p7.21-p7.22 Use the graphical metho
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x - a 0x - a 1x - a 2225dISCONTINuI
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conditions. The reactions for stati
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120 kN ⋅ m concentrated moment: F
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SolutioNWhen we refer to case 4 of
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Uniformly distributed load between
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y5 kN20 kN.my12 kN.m18 kN/mAB3 m 3
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CHAPTER8bending8.1 IntroductionPerh
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has a constant bending moment M, an
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The most common stress-strain relat
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All such moment increments that act
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The sense of σ x (either tension o
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A i(mm 2 )y i(mm)y i A i(mm 3 )(1)
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ExAmpLE 8.2The cross-sectional dime
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m8.7 Determine the centroid locatio
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zFIGURE p8.8p8.9 An aluminum alloy
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WidthWidthWidthDepthXYthicknessXWeb
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700 lb1,500 lb4 in.1 in.200 lb/ft1
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M = −6,000 lb · ft. For this neg
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mecmoviesExAmpLESm8.9 Determine the
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p8.16 A W18 × 40 standard steel sh
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8.5 Introductory Beam Design for St
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M (14,400 lb ⋅ ft)(12 in./ft)∴
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pRoBLEmSp8.26 A small aluminum allo
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Equivalent BeamsBefore considering
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Transformed-Section methodThe conce
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This equation reduces to∫A∫ydA
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ExAmpLE 8.7A cantilever beam 10 ft
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Bending Stresses at the intersectio
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(a) the normal stress in each mater
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283CM = PeF+ =bENdINg duE TO ANECCE
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and the combined normal stress on s
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Combined Stress at KThe combined st
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m8.23 Pipe AB (with outside diamete
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p8.54 The bracket shown in Figure P
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yFlangeyyz CM zWebM zM zCompressive
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These curvature expressions can now
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Coordinates of Points H and KThe (y
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Similarly, the moment of inertia I
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p8.63 A downward concentrated load
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the factor K depends only upon the
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SolutioNThe ultimate strength σ U
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MO307bENdINg OF CuRVEd bARSr or iθ
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Table 8.2 Area and Radial Distance
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Plan the SolutionBegin by calculati
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SuperpositionOften, curved bars are
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We now set the stress at point A (r
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p8.86 The curved tee shape shown in
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320SHEAR STRESS IN bEAMSy9 kN(2)xAB
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ExAmpLE 9.1M A = 11.0 kN·mAz(1)B(2
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84.2 MPa (C)y126.4 MPa (C)116.7 kN6
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326SHEAR STRESS IN bEAMSadA′MI zy
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328SHEAR STRESS IN bEAMSEquation (f
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SHEAR STRESS IN bEAMSyzzacbV(a) Box
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332SHEAR STRESS IN bEAMSThe shear s
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To determine the average horizontal
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p9.3 The beam segment shown in Figu
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9.6 Shear Stresses in Beams of circ
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36 kNVyMzxShear Stress FormulaThe m
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56 mmy13.5 mm 8.5 mm (3) K (4)z(5)7
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pRoBLEmSp9.11 A 0.375 in. diameter
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p9.23 A W14 × 34 standard steel se
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348SHEAR STRESS IN bEAMSNail ANail
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Plan the SolutionWhenever a cross s
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ExAmpLE 9.6An alternative cross sec
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ExERcISESm9.9 Five multiple-choice
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at intervals of s along each side o
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358SHEAR STRESS IN bEAMSCFdxtC′(2
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360SHEAR STRESS IN bEAMStb2stbdsd2y
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362SHEAR STRESS IN bEAMSIt is usefu
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PointSketchyy - ′(mm)A′(mm 2 )Q
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For this FBD, the calculation of Q
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ExAmpLE 9.971 mm89 mm280 mmV10 mm 1
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Point Sketch Calculation of Q = y
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be expressed as the product of the
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374SHEAR STRESS IN bEAMSThe exact l
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376SHEAR STRESS IN bEAMSd2d2FIGURE
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ExAmpLE 9.11Derive an expression fo
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Note that, since the shape is thin
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AByOzPED1.038 in.0.643 in.(a) Load
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τydAϕdϕyShear StressThe variatio
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p9.36 A plastic extrusion has the s
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p9.48 The beam cross section shown
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yePer3 in.z38 in. O38 in.10 in.5 in
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10.2 moment-curvature RelationshipW
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394bEAM dEFLECTIONS+ M + MPositive
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10.4 Determining Deflections by Int
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398bEAM dEFLECTIONS5. Boundary and
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Beam Deflection and Slope at AThe d
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Elastic Curve EquationSubstitute th
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Boundary ConditionsBoundary conditi
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integration over the interval a ≤
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mecmoviesExERcISEm10.1 Beam Boundar
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P10.11 For the beam and loading sho
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Elastic Curve EquationSubstitute th
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414beam deflectionsintegration give
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(a) Beam Deflection at AAt the tip
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Integrate again to obtain the beam
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The inclusion of the reaction force
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p10.24 The simply supported beam sh
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vwPvwvPALBv Bx=ALB( v B ) wx+ALB( v
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m10.5 Superposition Warm-up. A seri
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Beam deflection at C: The beam defl
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Avv30 kipsa= 13 ft b=7 ftBC D4 ft 6
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Next, consider the overhang span be
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By inspection, the rotation angle a
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v A70 kNAv210 kN.mBθ BCv Cθ D3 m
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Case 3—uniformly Distributed load
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m10.12 Use the superposition method
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v30 kNv12 kips2 kips/ftxxABHABC3 m
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p10.53 The simply supported beam sh
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446STATICALLy INdETERMINATEbEAMSM A
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— 1 w 0 Lv2M AA xAB2LA y 3L—3 B
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obtained from the continuity condit
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Solve for ReactionsSolve Equation (
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11.4 Use of Discontinuity Functions
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Integrate again to obtain the beam
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EI dvdx∫Integrate the beam load e
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v20 kips 30 kips 20 kipsA B C D E7
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462STATICALLy INdETERMINATEbEAMSThe
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corresponding beam deflection will
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Substitute these values into Equati
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By2 6 436(200,000 N/mm )(351 × 10
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The only unknown term in this equat
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The only unknown term in this equat
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p11.24-p11.26 For the beams and loa
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v90 kN/m30 kN/m(1)ABCx40 kN3 m5.5 m
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p11.49 Two steel beams support a co
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12.2 Stress at a General point in a
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12.3 Equilibrium of the Stress Elem
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484STRESS TRANSFORMATIONSsuch as th
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pRoBLEmSp12.1 A compound shaft cons
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p12.9 A steel pipe with an outside
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The forces acting on the vertical a
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tynθxσn dAFigure 12.10b is a free
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ExAmpLE 12.3y842 MPa550 MPa16 MPaxA
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The angle θ from the redefined x a
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p12.19 Two steel plates of uniform
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500STRESS TRANSFORMATIONSprincipal
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502STRESS TRANSFORMATIONSIf the nor
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504STRESS TRANSFORMATIONSIn words,
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yFIGURE 12.15506There is nevershear
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ExAmpLE 12.5y9 ksi7 ksix11 ksiConsi
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planes whose normal is perpendicula
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ExERcISEm12.4 Sketching Stress tran
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514STRESS TRANSFORMATIONSmecmovies
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516STRESS TRANSFORMATIONSLabel the
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mecmoviesExAmpLEm12.10 Coach Mohr
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P 2(-7.22, 0)(-5, 6 ccw) yτ(2, 9.2
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in the x-y coordinate system is rot
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t73.7°τy (-16, 53)R = 55.22C (-31
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ExAmpLE 12.11y(-14, 0)y(-14, 0)14 k
- Page 550 and 551:
ExERcISESm12.10 Coach Mohr’s Circ
- Page 552 and 553:
p12.46 Figure P12.46 shows Mohr’s
- Page 554 and 555:
12.11 General State of Stress at a
- Page 556 and 557:
534STRESS TRANSFORMATIONSIn Equatio
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536STRESS TRANSFORMATIONSthird prin
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538STRESS TRANSFORMATIONSyσp2Arbit
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Strain TransformationsCHAPTER1313.1
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542STRAIN TRANSFORMATIONSyyyγ xy d
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544STRAIN TRANSFORMATIONSThus, diag
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tnFinally, to compute the shear str
- Page 570 and 571:
Table 13.2 Absolute maximum Shear S
- Page 572 and 573:
The in-plane principal directions c
- Page 574 and 575:
552STRAIN TRANSFORMATIONS13.6 mohr
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y24.2°279 μεπ2579 μεx- 858 μ
- Page 578 and 579:
556STRAIN TRANSFORMATIONSPlasticbac
- Page 580 and 581:
Equation for gage b:2 2− 900 = e
- Page 582 and 583:
pRoBLEmSp13.25-p13.30 The strain ro
- Page 584 and 585:
yyyτ xyτ yzτ zxxxxzFIGURE 13.13a
- Page 586 and 587:
564STRAIN TRANSFORMATIONSHence, the
- Page 588 and 589:
SolutioN(a) Normal stresses: From E
- Page 590 and 591:
Then solve for γ xy :2 2380 = (
- Page 592 and 593:
(b) Principal and Maximum in-Plane
- Page 594 and 595:
(b) Principal and Maximum in-Plane
- Page 596 and 597:
y103.7 MPa40.2 MPa18.5°x63.5 MPa14
- Page 598 and 599:
1εz = [ σ z − νσ ( x + σ y )
- Page 600 and 601:
σ xyFinally, suppose the material
- Page 602 and 603:
pRoBLEmSp13.31 An 8 mm thick brass
- Page 604 and 605:
Problem e a e b e c E νycP13.47
- Page 606 and 607:
p13.65 A solid plastic [E = 45 MPa;
- Page 608 and 609:
586PRESSuRE VESSELSThe wall compris
- Page 610 and 611:
588PRESSuRE VESSELSττ abs max = p
- Page 612 and 613:
590PRESSuRE VESSELSStresses on the
- Page 614 and 615:
592PRESSuRE VESSELSFor the outer su
- Page 616 and 617:
31.9 MPay63.8 MPat13.81 MPax30°39.
- Page 618 and 619:
p14.5 The normal strain measured on
- Page 620 and 621:
p14.20 The cylindrical pressure ves
- Page 622 and 623:
600PRESSuRE VESSELSSince the ends o
- Page 624 and 625:
602PRESSuRE VESSELSσ θτ maxσ r4
- Page 626 and 627:
604PRESSuRE VESSELSFor convenience,
- Page 628 and 629:
14.6 Deformations in Thick-Walled c
- Page 630 and 631:
Maximum Shear StressThe principal s
- Page 632 and 633:
610PRESSuRE VESSELScould be cooled
- Page 634 and 635:
Maximum Circumferential Stress in t
- Page 636 and 637:
212.5 MPa134.4 MPa145.2 MPa76.2 MPa
- Page 638 and 639:
CHAPTER15Combined Loads61615.1 Intr
- Page 640 and 641:
6.92 ksiz6.92 ksiHAHy11.54 ksi8.49
- Page 642 and 643:
p15.5 A solid 1.50 in. diameter sha
- Page 644 and 645:
622COMbINEd LOAdSPP2P2FIGURE 15.1 S
- Page 646 and 647:
internal bending moment acting at t
- Page 648 and 649:
60 kNShear Force and Bending Moment
- Page 650 and 651:
ExAmpLE 15.3A steel hollow structur
- Page 652 and 653:
1.216 ksiH1.216 ksiH1.373 ksi30.3°
- Page 654 and 655:
Figure P15.13b/14b are d = 240 mm,
- Page 656 and 657:
p15.25 A load P = 75 kN acting at a
- Page 658 and 659:
636COMbINEd LOAdS b. Bending moment
- Page 660 and 661:
20.05 MPacbyM z = 3.85 kN·m20.05 M
- Page 662 and 663:
102,400 N · mm = 102.4 N · m. Sim
- Page 664 and 665:
yK12.02 MPax45°12.02 MPaStress tra
- Page 666 and 667:
The equivalent moments at the secti
- Page 668 and 669:
Hy3,000 lb448 psiKThe 3,000 lb shea
- Page 670 and 671:
z8.45 kN·m15.6 kN·mHK10.8 kN·mEq
- Page 672 and 673:
Torsion shear13.438 MPaBeam shear3.
- Page 674 and 675:
m15.5 Determine the stresses acting
- Page 676 and 677:
p15.34 Forces P x = 580 lb and P y
- Page 678 and 679:
z 2z 1dimensions of the assembly ar
- Page 680 and 681:
658COMbINEd LOAdSIf the naming conv
- Page 682 and 683:
660COMbINEd LOAdSfrom which it foll
- Page 684 and 685:
662COMbINEd LOAdSSimilarly, Equatio
- Page 686 and 687:
(b) What is the value of the Mises
- Page 688 and 689:
p15.54 A thin-walled cylindrical pr
- Page 690 and 691:
668COLuMNSStability of EquilibriumT
- Page 692 and 693:
670COLuMNSSummaryBefore a compressi
- Page 694 and 695:
672COLuMNSIf we let2Pk =(16.2)EIthe
- Page 696 and 697:
674COLuMNS7060σY =50=σ cr4030σY
- Page 698 and 699:
The Euler buckling load for this co
- Page 700 and 701:
Spacer blockFIGURE p16.676 mm 76 mm
- Page 702 and 703:
16.3 The Effect of End conditionson
- Page 704 and 705:
682COLuMNSwhere the first two terms
- Page 706 and 707:
684COLuMNSAnother way of expressing
- Page 708 and 709:
LateralbracingxCBP17.5 ft17.5 ftzSt
- Page 710 and 711:
xBPBuckling About the Strong AxisTh
- Page 712 and 713:
p16.19 The aluminum column shown in
- Page 714 and 715:
692COLuMNSIn this case, a relations
- Page 716 and 717:
694COLuMNSwhich can be further simp
- Page 718 and 719:
Pexp16.26 A steel [E = 200 GPa] pip
- Page 720 and 721:
698COLuMNSFor short and intermediat
- Page 722 and 723:
ExAmpLE 16.52 in.zSpacer blocky2 in
- Page 724 and 725:
Since KL/ry > 133.7, the column is
- Page 726 and 727:
The reduced Euler buckling stress t
- Page 728 and 729:
Determine the allowable axial load
- Page 730 and 731:
708COLuMNSwhere the compressive str
- Page 732 and 733:
Both tensile and compressive normal
- Page 734 and 735:
ExAmpLE 16.940 kNexA 6061-T6 alumin
- Page 736 and 737:
pRoBLEmSp16.42 The structural steel
- Page 738 and 739:
716ENERgy METHOdSThe total energy o
- Page 740 and 741:
718ENERgy METHOdSydV = dx dy dzzxxS
- Page 742 and 743:
720ENERgy METHOdSSince the volume o
- Page 744 and 745:
The maximum force P that can be app
- Page 746 and 747:
17.5 Elastic Strain Energy for Flex
- Page 748 and 749:
segment AB of the beam. The second
- Page 750 and 751:
p17.8 A solid stepped shaft made of
- Page 752 and 753:
730ENERgy METHOdSNote that the nega
- Page 754 and 755:
732ENERgy METHOdSSignificance: In t
- Page 756 and 757:
From the positive root, the maximum
- Page 758 and 759:
Note: Throughout the previous chapt
- Page 760 and 761:
The right-hand side of this equatio
- Page 762 and 763:
(b) If the rod has a constant diame
- Page 764 and 765:
Note: Throughout the previous chapt
- Page 766 and 767:
assembly. The solid bronze post has
- Page 768 and 769:
17.7 Work-Energy method for Single
- Page 770 and 771:
F 1(1)BSolutioNThe internal axial f
- Page 772 and 773:
17.8 method of Virtual WorkThe meth
- Page 774 and 775:
752ENERgy METHOdSIf the material be
- Page 776 and 777:
754ENERgy METHOdSwhich is the mathe
- Page 778 and 779:
756ENERgy METHOdSThe virtual intern
- Page 780 and 781:
both P 1 and P 2 from the truss, ap
- Page 782 and 783:
Following is the table produced by
- Page 784 and 785:
SolutioNCalculate the member length
- Page 786 and 787:
764ENERgy METHOdSObtain the total v
- Page 788 and 789:
766ENERgy METHOdSthe real external
- Page 790 and 791:
ExAmpLE 17.141,400 N900 NCalculate
- Page 792 and 793:
1Ax 1 or x 2vmDraw a free-body diag
- Page 794 and 795:
p17.36 Determine the vertical displ
- Page 796 and 797:
p17.54 Determine the minimum moment
- Page 798 and 799:
776ENERgy METHOdSFor the general ca
- Page 800 and 801:
ExAmpLE 17.16Determine the vertical
- Page 802 and 803:
SolutioNWe seek the horizontal defl
- Page 804 and 805:
782ENERgy METHOdSprocedure for Anal
- Page 806 and 807:
Castigliano’s second theorem appl
- Page 808 and 809:
Finally, derive the following equat
- Page 810 and 811:
p17.63 The truss shown in Figure P1
- Page 812 and 813:
APPENDIXAgeometric Propertiesof an
- Page 814 and 815:
792gEOMETRIC PROPERTIESOF AN AREAyy
- Page 816 and 817:
mecmoviesExAmpLESA.2 Animated examp
- Page 818 and 819:
796gEOMETRIC PROPERTIESOF AN AREAfo
- Page 820 and 821:
ExAmpLE A.340 mmDetermine the momen
- Page 822 and 823:
ExAmpLE A.440 mmDetermine the produ
- Page 824 and 825: yy′yOxxdAθθcos θx′xy′sin
- Page 826 and 827: 804gEOMETRIC PROPERTIESOF AN AREANo
- Page 828 and 829: 806gEOMETRIC PROPERTIESOF AN AREAI
- Page 830 and 831: I xy(38.8, 32.3) y1.654 in.yR = 38.
- Page 832 and 833: YttffdXXt wYb fDesignationAreaADept
- Page 834 and 835: YttffdXXt wYb fDesignationAreaADept
- Page 836 and 837: x-XYttffXt wdYAmerican Standard cha
- Page 838 and 839: b fdttffXYXy-t wYDesignationAreaADe
- Page 840 and 841: dXYXtYbDesignationHSS304.8 × 203.2
- Page 842 and 843: YxZXyXαYZDesignationMasspermeterAr
- Page 844 and 845: Simply Supported BeamsBeam Slope De
- Page 846 and 847: Average Properties ofSelected Mater
- Page 848 and 849: Table D.1b Average properties of Se
- Page 850 and 851: Fundamental Mechanicsof Materials E
- Page 852 and 853: orσx + σ y σx − σ yσ n = + c
- Page 854 and 855: Answers to Odd NumberedProblemsChap
- Page 856 and 857: (c) φ E/C = 0.1408 rad(d) T A = 23
- Page 858 and 859: P7.35 (a)wx ( ) =−5kN −x − 0
- Page 860 and 861: (c)Chapter 8P8.1 σ = 1.979 ksiP8.3
- Page 862 and 863: P10.7 v B = −8.27 mmP10.9 (a)wx 0
- Page 864 and 865: P12.35 (a) 25.6 MPa(b) 23.1° clock
- Page 866 and 867: P13.63 (a) Db = 1.272 mm,Dc = 0.254
- Page 868 and 869: P17.41 (a) D F = 18.54 mm ←(b) D
- Page 870 and 871: Biaxial stress, 566-568, 587, 590-5
- Page 872 and 873: GGage length, 46, 47, 51, 54Gears,
- Page 876: Torsionof circular shafts, 135-151e