Unit 4 Plastic Behaviour Of Structural Steel 2iu1u

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Plastic Behaviour of Structural Steel ( Unit - 4)

CONTENTS

Introduction Plastic theory Plastic hinge concept Plastic collapse load Conditions of Plastic analysis Theorems of Plastic collapse Methods of Plastic analysis Plastic analysis of continuous beams



Introduction The traditional analysis of structures is based on the linear elastic behaviour of materials, implying that the material follows Hooke’s law. (Stress is proportional to strain) It is also assumed that the deformations are small, implying that the original dimensions of the structure can be used in the analysis. This is also known as first order elastic analysis. (Cl. 4.4.2 pp - 24) IS 800 - 2007 permits plastic analysis as per the Cl. 4.5 (pp 25 and 26). However, the requirements specified in Cl. 4.5.2 shall be satisfied unless otherwise specified. • The yield stress of the grade of structural steel used shall not exceed 450 MPa. • The stress - strain characteristics of steel shall comply with IS : 2062 to ensure complete plastic moment redistribution. • The stress - strain diagram shall have a plateau at the yield stress level extending for at least six times the yield strain. • The ratio of ultimate tensile stress to the yield stress for the specified grade of steel shall not be less than 1.2 • The percentage elongation shall not be less than 15 and the steel shall exhibit strain hardening capabilities. (Steel confirming to IS : 2062 shall be deemed to satisfy the above requirements) • The shall be hot - rolled or fabricated using hot - rolled plates and sections. • The cross section of the shall be plastic (class 1 section) at plastic hinges and elsewhere at least compact sections. (class 2 section) Table 2 shall be followed in this regard. • The cross section shall be symmetrical about the axis perpendicular to the axis of the plastic hinge rotation indicating that the beams shall be symmetrical about y-y axis and columns shall be symmetrical about both y-y and z-z axes. • The shall not be subjected to impact and fluctuating loading requiring fracture and fatigue assessment. Stress - strain curves of structural steel A typical stress - strain curve of steel confirming to IS : 2062 is shown in the figure. where, fy = yield stress in MPa ey = yield strain fu = Ultimate stress in MPa esh = strain hardening strain emax = ultimate strain esh = 6 * ey , emax = 180 * ey and fu = 1.2 fy (Typical) From the stress - strain curve, steel yields considerably at a constant stress due to large flow of the material. This property known as ductility enables steel to undergo large deformations beyond the elastic limit without danger of fracture. This unique property of steel is utilized in plastic analysis of structures.



Stress - Strain Curve (Typical)

Perfectly Elasto - Plastic Material (Typical)



Calculation of failure loads in simple systems Consider a three bar system shown below of length and area of C/S of each bar as indicated. E is the modulus of elasticity of the material.

Elastic analysis (Strength of Materials approach): P1 is the force in outer bars P2 is the force in the middle bar Using ΣV = 0, (Vertical equilibrium equation) 2P1 + P2 = P (1) By compatibility, elongation of each bar is same P1L/AE = P2L/2AE from which P1 = P2/2 or P2 = 2P1 (2) Substituting (2) in (1), 2P1 + 2P1 = P or P1 = P/4 and P2 = P/2 In elastic analysis, as P2 > P1 the middle bar reaches the yield stress first and the system is assumed to fail. P2 = fyA and P1 = fyA/2 Yield load = 2P1 + P2 = 2fyA ----- Maximum load by elastic analysis Plastic analysis: In plastic analysis, it will be assumed that even though the middle bar reaches the yield stress, they start yielding until the outer bars also reaches the yield stress. (Ductility of steel and redistribution of forces) With this, all the bars would have reached yield stress and the failure load (or ultimate load or collapse load) is given by Collapse load, Pu = 2 fy A + fy A = 3fyA ------ Maximum load by plastic analysis



The collapse load calculated by plastic analysis is 1.5 times that of the elastic analysis. (Reserve strength) Plastic analysis can give economical solutions. Plastic Theory of Beams: The simple plastic theory makes use of the ductility of steel. (Large strain at collapse) The following assumptions are made in plastic bending of beams • • • • • • • • • • •

Structural steel is a ductile material capable of deforming plastically without fracture. The material is homogeneous and isotropic obeying Hooke’s law upto limit of proportionality (yield point) and then the stress is constant with increase in strain. The stress - strain curve can be represented by an ideal elasto - plastic material with properties of steel in compression and tension same. (yield stress and yield strain, modulus of elasticity etc.,) Cross - sections remain plane and normal to the longitudinal axis before and after bending. With this, the effect of shear force is ignored and the distribution of the strain across the depth of the c/s of the beam is linear. The effect of axial forces and residual stresses are ignored. The c/s of the beam is symmetrical about an axis parallel to the plane of bending. (y -y axis) are initially straight and instability does not develop before collapse occurs due to the formation of sufficient plastic hinges. Each layer of the beam is free to expand or contract independently with respect to the layer above or below it.(each layer is separated from one another) Deformations are sufficiently small so that θ = tan θ can be used in the calculations of the collapse load. The connections provide full continuity so that plastic moment can develop and transmitted through the connections. Strain energy due to elastic bending is ignored.

Behaviour of beam under an increasing BM: Consider a beam having a symmetrical C/S subjected to an increasing BM. • With BM M1 < My ( yield moment) the stress and strain distributions across the depth will follow the elastic bending equation (Euler’s - Bernoulli’s equation) and is indicated in the figure below. All the fibres are stressed below the yield stress, fy.



•

With BM, M2 = My, the extreme fibres of the c/s begins to yield and the stress will be equal to fy .The stress and strain distributions across the depth will still follow the elastic bending equation (Euler’s - Bernoulli’s equation) and is indicated in the figure below. All the fibres other than extreme fibres are stressed below the yield stress, fy. The permissible stress (working stress) method is based on this behaviour with suitable factor of safety.

•

With further increase in BM, M3 > My, yielding spreads into inner fibres. The c/s is elasto - plastic and the internal moment of resistance can be computed, if required from the stress distribution shown below.

•

Finally, the yielding of fibres spreads almost for the entire c/s and the BM, M4 at this stage is called the plastic moment MP .The c/s is said to be fully plasticized. A plastic hinge is formed at this stage. After this, the deflection increases rapidly resulting in collapse or failure. The neutral axis, NA is now called the Equal Area Axis. An idealized stress distribution is shown below.



Basic Definitions: Plastic Moment, Mp: It is defined as the moment of resistance of a fully plasticized or yielded c/s. The entire c/s is under yield stress, fy. Mathematically, MP = fY Zpz fy is the yield stress of the material Zpz is the plastic section modulus of the c/s about z-z axis

Yield Moment, My: It is defined as the moment of resistance of a c/s whose extreme fibres only has reached yield stress, fy. Mathematically, My = fY Zez fy is the yield stress of the material Zez is the elastic section modulus of the c/s about z-z axis Plastic hinge: It is defined a point in a flexural member where full plastic moment has developed and is rotating at a constant moment, MP. The following characteristics are observed with respect to a plastic hinge : • • •

A plastic hinge is a zone of yielding in a flexural member, where the stress is equal to fY throughout the c/s. The length of the plastic hinge depends on the type of loading, c/s and conditions. However, in the analysis, it is assumed as point where all the plastic rotation takes place. At the point, where plastic hinge is formed, it will be rotating with a constant plastic moment, Mp



• • • • •

Plastic hinges are formed at points where concentrated loads are acting, fixed or continuous s in an indeterminate beam, ts in a rigid frame and at points of zero shear, when UDL or other varying loads are acting. Plastic hinge is formed in a member of lesser capacity, when two meet as in the case of a continuous beam. The first plastic hinge is formed at the point of maximum BM. The formation of plastic hinges allow redistribution of moments until plastic hinges are formed at all the critical sections. The formation of sufficient number of plastic hinges convert the structure into a mechanism where the given structure breaks into rigid links with large deformations. (Collapse)

Length of plastic hinge: It is the length in a beam over which the BM is greater than the yield moment, My Example 1

Consider a simply ed beam subjected to a central concentrated load which has yielded over the shaded area as shown. Let Lp and L be the length of the plastic hinge and span of the beam. From similar triangles, Lp / L = (Mp - My) / Mp = (1 - My / Mp) = [1 - 1/ (Mp / My)] = (1 - 1/S) where S = (Mp / My) is called the shape factor www.bookspar.com | VTU NOTES | QUESTION PAPERS | NEWS | RESULTS | FORUMS


Hence, Lp = (1 - 1/S) L For a rectangular section, S = 1.5 and Lp = 1/3 * L For typical I - sections, S = 1.14 and Lp = 0.123 L, say 1/8 * L Length of plastic hinge depends on the shape factor of the c/s Example 2 Consider a simply ed beam subjected to a UDL which has yielded over the shaded area as shown. Let Lp and L be the length of the plastic hinge and span of the beam.

Let x = Lp / 2 My = wu L / 2 * (L / 2 - x) - wu (L / 2 - x)2 / 2 = wu L2 / 4 - (wu L / 2) * x - wu / 2 * (L2 / 4 + x2 - L x) Cancelling (wu L / 2) * x, we have My = wu L2 / 8 - wu x2 / 2 = wu L2 / 8 - wu L2 / 8 * (4 x2 / L2) Noting Mp = wu L2 / 8, we have My = Mp (1 - 4 x2 / L2) My / Mp = (1 - 4 x2 / L2) 1 / S = (1 - 4 x2 / L2) 4 x2 / L2 = 1 - 1 / S x2 = L2 / 4 (1 - 1 / S) x = L / 2 √ (1 - 1 / S) Lp / 2 = L / 2 √ (1 - 1 / S) Lp = L √ (1 - 1 / S)



For a rectangular section, S = 1.5 and Lp = 0.577 * L For typical I - sections, S = 1.14 and Lp = 0.35 * L Length of plastic hinge depends on the shape factor of the c/s Note : From the above examples, it is observed that the length of the plastic hinge is dependent on the loading and shape factor. It is also dependent on the conditions. For propped cantilevers, fixed beams, continuous beams and rigid frames, it is still difficult to calculate the length of plastic hinges for different loadings and s. Hence, it is customary to assume the plastic hinge in the analysis as a point where all the plastic rotation takes place. Redistribution of Moments : In determinate structural systems like simply ed beams, cantilevers and overhang beams, only one plastic hinge will be formed at the point of maximum BM and the structure is assumed to collapse. The increase in load carrying capacity is only marginal and depends on the shape factor. However in indeterminate structural systems like propped cantilevers, fixed beams, continuous beams and rigid frames, there is further increase in load carrying capacity due to the redistribution of moments. This is called the reserve strength of the beam. This is mainly due to the property of ductility of steel. Redistribution of moments is explained with respect to a fixed beam subjected to UDL through out. The beam is shown in the figure below.

The maximum elastic BM occurs at the s and is equal to wL2 / 12 . As a first step, the plastic hinges are formed at the s and complete plasticization of the c/s takes place. But this do not mean failure or collapse occurs. This is because a plastic hinge at the centre should also be formed. (No. of plastic hinges in indeterminate structures = SI + 1) At this stage, the plastic hinges formed at the s will be rotating at constant moment, Mp due to ductility of the material. Collapse of the beam occurs only when complete plasticization occurs at the centre resulting greater load carrying capacity.



At collapse, using equilibrium method, we have wu L2 / 8 = 2 Mp wu = 16 Mp / L2 ----------- Collapse load for the beam At first yield, My = wy L2 / 12 at the s, (only extreme fibres will yield) wy = 12 My / L2 Reserve strength = wu / wy = (16 Mp / L2) / (12 My / L2) = 4 / 3 * Mp / My =4/3*S where S is the shape factor. For typical I - sections, S = 1.14 Reserve strength = 4 / 3 * 1.14 = 1.52 The beam is capable of carrying 52% more load beyond the first yield. In general, increase in load carrying capacity occurs in plastic analysis due to i) Plasticization of the section (formation of plastic hinges at critical sections) ii) Redistribution of moments Plastic Section modulus of a c/s: Consider a c/s symmetrical about the vertical y-y axis as shown below with the section fully plasticized.

A1 and A2 are the areas above and below the Neutral Axis (Equal Area Axis) fY is the yield stress in the material Compressive force above the NA = fy A1 Tensile force below the NA = fy A2 For equilibrium, the forces are equal fy A1= fy A2 from which A1 = A2 For a fully plasticized c/s, area above the NA = area below the NA In other words, A1 + A2 = A A1 + A 1 = A A1 = A2 = A/2 www.bookspar.com | VTU NOTES | QUESTION PAPERS | NEWS | RESULTS | FORUMS


The neutral axis (NA) of a fully plasticized section is called the equal area axis (EAA) The plastic moment of a fully plasticized section can be obtained by taking moments of the forces above and below the EAA about EAA. Mp = fy A1 Y1 + fy A2 Y2 = fy A/2 Y1 + fy A/2 Y2 = fy A/2 (Y1 + Y2) = fy Zpz where, Zpz = plastic section modulus of the c/s about z-z axis = [A/2 (Y1 + Y2)] The plastic section modulus of a c/s, Zpz is defined as the moment of the areas above and below EAA about the EAA. It is the resisting modulus of a completely plasticized section and is a geometric property. Shape factor, S: It is defined as the ratio of plastic moment, MP to yield moment, MY. Also, called form factor. Mathematically, S = MP / My = fY Zpz / fY Zez = Zpz / Zez It is also the ratio between the plastic section modulus to the elastic section modulus of a c/s and is a geometric property Shape factor of simple sections: 1. Rectangle: Consider a rectangle as shown

Elastic section modulus,Zez = INA / extreme fibre distance = (bD3/12) / (D / 2) = bD2 / 6 www.bookspar.com | VTU NOTES | QUESTION PAPERS | NEWS | RESULTS | FORUMS


Plastic section modulus, Zpz = Moments of the areas above and below the E A A (equal area axis) about the E A A. ZP = [(bD / 2) x D/4] x 2 = bD2 / 4 S = Zpz / Zez = 1.5 2. I - section, say ISMB 600 @ 122.6 kg/m: Consider the I - section shown

zez = 3060.4 cm3 (From hand book; Table I, pp - 4,5 ) = 3060.4 x 103 mm3 zpz = [ 210 x 20.8 x (600/2 - 20.8/2) + 12 x (600/2 - 20.8) x (600/2 - 20.8)/2 ] x 2 = 3465.38 x 103 mm3 (The value given in Table 46; pp - 138 is 3510.63 x 103 mm3) Shape factor, S = Zpz / Zez = 1.132 (The value given in Table 46; pp - 138 is 1.147) If the above c/s is used over an effective span of 8m, the permissible UDL on the beam is calculated as Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 250 x 3060.4 x 103 = 765.1 x 106 N mm = 765.1 kN m Plastic Moment, Mp = fY Zpz = 250 x 3465.38 x 103 = 866.35 x 106 N mm = 866.35 kN m Working bending moment, M = Mp / 1.5 = 577.57 kN m



If the permissible UDL on the beam is w/unit length, w L2 / 8 = M w x 82/8 = 577.57 w = 72.2 kN/m (including self weight) On similar lines, if central concentrated load is required, W L / 4 + wself weight * L2 / 8 = M W * 8 / 4 + 1.23 x 82 / 8 = 577.57 W = 283.87 kN If the c/s is symmetrical about the horizontal z - z axis or NA, then both NA and EAA will co inside. 3. T - section say ISNT 150: Consider the T section as shown.

Zez = 54.6 cm3 (From hand book; Table VI pp - 18,19) The section is unsymmetrical about the NA and hence the EAA has to be located. Total area of the c/s = 29.08 cm2 = 2908 mm2 (From hand book; Table VI, pp - 18,19) A1 = A2 = A / 2 = 1454 mm2 If EAA is at distance y from top, we have 150 * y = 1454 y = 9.69 mm The plastic section modulus is calculated by taking moments of the area above and below the EAA about EAA. Zpz = 150 * 9.69 * 9.69 / 2 + 150 * 0.31 * 0.31 / 2 + 10 * 140 * (140 / 2 + 0.31) = 105.48 x 103 mm3 (0.31 = 10 - 9.69 ; 140 = 150 - 10) S = Zpz / Zez = 1.93 Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 250 x 54.6 x 103 = 13.65 x 106 N mm = 13.65 kN m www.bookspar.com | VTU NOTES | QUESTION PAPERS | NEWS | RESULTS | FORUMS


Plastic Moment, Mp = fY Zpz = 250 x 105.48 x 103 = 26.37 x 106 N mm = 26.37 kN m Working bending moment, M = Mp / 1.5 = 17.58 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. 4. Channel Section, say ISMC 400 @ 49.4 kg/m Consider the channel section as shown.

The elastic properties of the section is obtained from Table II, pp 6 - 7 of ISI handbook [SP (6) - 1)] Zez = 754.1 cm3 = 754.1 x 103 mm3 The beam is symmetrical about z - z axis and hence, NA and EAA co inside. Zpz = (100 * 15.3 * 192.35 + 8.6 * 184.7 * 184.7 / 2) * 2 = 881.97 x 10 mm3 [192.35 = (400 / 2) - 15.3 / 2 ; 184.7 = (400 / 2) - 15.3] S = Zpz / Zez = 1.17 Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 250 x 754.1 x 103 = 188.53 x 106 N mm = 188.53 kN m Plastic Moment, Mp = fY Zpz = 250 x 881.97 x 103 = 220.5 x 106 N mm = 220.5 kN m



Working bending moment, M = Mp / 1.5 = 147 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. 5. Built up section, ISMB600 @ 122.6kg/m with 320 x 40 plates symmetrically placed Consider the built up section as shown.

The elastic properties of the section is obtained from Table XIV, pp 54 - 55 of ISI handbook [SP (6) - 1)] Zez = 10420.5 cm3 = 10420.5 x 103 mm3 The beam is symmetrical about z - z axis and hence, NA and EAA co inside Zpz = 3510.63 x 103 + (320 * 40 * 320) * 2 = 11702.63 x 103 mm3 (The value of Zpz of ISMB 600 @ 122.6kg/m is 3510.63 cm3 obtained from Table 46 of IS : 800 - 2007 pp - 138; 320 = 600 / 2 + 40 / 2 ) S = Zpz / Zez = 1.123 Mean thickness of flange = (320 * 40 + 210 * 20.8) / 320 = 53.65 mm (Table XIV gives mean thickness of flange = 53.3 mm) (210 and 20.8 = width of flange and thickness of flange of ISMB 600 @ 122.6kg/m) Mean thickness > 40 mm fy = 230 MPa (Table 1 - IS: 800 - 2007, pp - 14)



Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 230 x 10420.5 x 103 = 2396.72 x 106 N mm = 2396.72 kN m Plastic Moment, Mp = fY Zpz = 230 x 11702.63 x 103 = 2691.6 x 106 N mm = 2691.6 kN m Working bending moment, M = Mp / 1.5 = 1794.4 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. 6. Plate girder section, say Two 500 x 40 flange plates (one on each side), Four flange angles (two on each side) and One web plate 1600 x 16 Consider the section as shown.



The elastic properties of the section is obtained from Table XX, pp 84 - 85 of ISI handbook [SP (6) - 1)] Zez = 56782.9 cm3 = 56782.9 x 103 mm3 The beam is symmetrical about z - z axis and hence, NA and EAA co inside Zpz = (500 * 40 * 820 + 200 * 18 * 791 * 2 + 18 * 182 * 691 * 2 + 16 * 800 * 400) * 2 = 63485.26 x 103 mm3 (820 = 1600 / 2 + 40 / 2 ; 791 = 1600 / 2 + 18 / 2 ; 182 = 200 - 18 ; 691 = 1600 / 2 - 18 182 / 2 ; 800 = 1600 / 2 ; 400 = 800 / 2) S = Zpz / Zez = 1.118 Mean thickness of flange = (500 * 40 + 200 * 18 * 2) / 500 = 54.4 mm (Table XX gives mean thickness of flange = 55 mm) Mean thickness > 40 mm fy = 230 MPa (Table 1 - IS: 800 - 2007, pp - 14) Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 230 x 56782.9 x 103 = 13060.07 x 106 N mm = 13060.07 kN m Plastic Moment, Mp = fY Zpz = 230 x 63485.26 x 103 = 14601.61 N mm = 14601.61 kN m Working bending moment, M = Mp / 1.5 = 9734.41 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. 7. Box section, say 300 x 600 outer dimensions with 12 mm as uniform thickness

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Consider the section as shown. The beam is symmetrical about z - z axis and hence, NA and EAA co inside Zez = Izz / ymax = [300 * 6003 / 12 - (300 - 12 * 2) * (600 -12 * 2)3 / 12] / (600 / 2 ) = 3.35 x 106 mm3 Zpz = (300 * 12 * 294 + 12 * 288 * 144 * 2) * 2 = 4.11 x 106 mm3 (294 = 600 / 2 - 12 / 2 ; 288 = 600 / 2 - 12 ; 144 = 288 / 2) S = Zpz / Zez = 1.227 fy = 250 MPa (Table 1 - IS: 800 - 2007, pp - 14) Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 250 x 3.35 x 106 = 837.5 x 106 N mm = 837.5 kN m Plastic Moment, Mp = fY Zpz = 250 x 4.11 x 106 = 1027.5 x 106 N mm = 1027.5 kN m Working bending moment, M = Mp / 1.5 = 685 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. 8. Unsymmetrical I section Consider an Unsymmetrical c/s as shown



The section is unsymmetrical about the NA and hence the EAA has to be located. The NA has to be calculated as section properties are not available in SP (6) Let yt be the distance of NA from the top yt = [200 * 10 * 10 / 2 + 10 * 180 * (180 / 2 + 10) + 100 * 10 * (200 - 10 / 2)] / Total area, A = (200 * 10 + 180 * 10 + 100 * 10) = 80.21 mm yb = distance of NA from the bottom = 200 - 80.21 = 119.79 mm INA = [200 * 103 / 12 + 200 * 10 * (80.21 - 5)2] + [10 * 1803 / 12 + 10 * 180 * (100 - 80.21)2] + [100 * 103 /12 + 100 * 10 * (195 - 80.21)2] = 30.08 x 106 mm4 Zez = INA / ymax = 30.08 x 106 / 119.79 = 251.11 x 103 mm3 Let the EAA be at distance y from the top 200 * 10 + 10 * (y - 10) = Total area / 2 = 4800 / 2 = 2400 y = 50 mm Zpz = 200 * 10 * 45 + 10 * 40 * 20 + 10 * 140 * 70 + 100 * 10 * 145 = 341 x 103 mm3 S = Zpz / Zez = 1.358 fy = 250 MPa (Table 1 - IS: 800 - 2007, pp - 14) Yield Moment, MY = fY Zez (Assuming fy =250 MPa) = 250 x 251.11 x 103 = 62.78 x 106 N mm = 62.78 kN m Plastic Moment, Mp = fY Zpz = 250 x 341 x 103 = 85.25 x 106 N mm = 85.25 kN m Working bending moment, M = Mp / 1.5 = 56.83 kN m If UDL or other loads are required, maximum BM which depends on the type of loading and span is equated to working bending moment. Mechanisms: It can be defined as a situation in a structure in which sufficient number of plastic hinges are formed so as to cause collapse without further increase in the load carrying capacity. (collapse load) Mechanism breaks the structure into rigid links. When a mechanism is formed the structure is subjected to large rotations and deflections. In an indeterminate structure, number of plastic hinges = SI makes the structure determinate and additional plastic hinge transforms the structure into a mechanism resulting in collapse. Mechanism results in instability of the structure with large deformations. The type of mechanism depends on the structure. Different types of mechanisms are indicated in the figures.



Plastic Collapse load It is the load corresponding to the collapse of a structure due to the formation of sufficient number of plastic hinges transferring the structure into a mechanism. It is also called ultimate load or limit load. The number of plastic hinges at collapse = SI +1, where SI = Static indeterminacy of the structure. The collapse of a structure can be a partial, complete or over complete collapse depending on number of plastic hinges In a structural system, if only a part of the structure fails, making the structure as a whole useless, then the collapse is said to be partial and the corresponding load is taken as the partial collapse load. Number of plastic hinges in a partially collapsed structure is < SI +1. In rigid frames, if a beam fails, then it is called a partial collapse. www.bookspar.com | VTU NOTES | QUESTION PAPERS | NEWS | RESULTS | FORUMS


In a structural system, if complete collapse of the structure occurs, then the corresponding collapse load is taken as the true collapse load. Number of plastic hinges at collapse is = SI + 1. Usually, the value of the collapse load corresponds to any one mechanism which gives the lowest load. In a structural system, if collapse of the structure occurs due to formation of more than the necessary plastic hinges , then the collapse is considered as over complete collapse and the corresponding load is said to be over complete collapse load.. Number of plastic hinges at collapse is > SI + 1. Two or more mechanisms give the same collapse load. This can happen in symmetrically loaded structures, where the plastic hinges do not lie on the axis of symmetry. Conditions in Plastic Analysis: In elastic analysis of structures, the conditions to be satisfied are : Equilibrium conditions - ΣV = 0 ; ΣH = 0 and ΣM = 0 Compatibility conditions - Continuity of slopes and deflections BM < Yield Moment with suitable factor of safety In plastic analysis of structures, the conditions to be satisfied are : Equilibrium conditions - ΣV = 0 ; ΣH = 0 and ΣM = 0 Mechanism condition or formation - Sufficient number of plastic hinges shall be formed to transfer the structure into a mechanism Plastic moment condition - BM at any point shall not exceed the plastic moment, Mp of the section (M < or = Mp) If all the three conditions are satisfied in plastic analysis, then we get the true collapse load. However, if any two conditions are satisfied, we get a load which is either below or above the true collapse load. Theorems in Plastic analysis : Based on the number of conditions satisfied, we have three theorems in plastic analysis. Static Theorem (Lower bound theorem): This theorem states that the load computed from any distribution of BMDs in equilibrium with external loads (safe and statically issible BMD) so that the maximum BM in any member shall not exceed its plastic moment, Mp (M < or = Mp) is less than or equal to the true collapse load. This theorem leads to equilibrium or static method of plastic analysis. This theorem also called the safe theorem satisfies equilibrium and plastic moment condition. Kinematic Theorem (Upper bound theorem): This theorem states that the load computed from any assumed kinematically issible mechanism is greater than or equal to the true collapse load. This theorem leads to kinematic or mechanism method of analysis.



This theorem also called the unsafe theorem satisfies equilibrium and mechanism condition. A kinematically issible mechanism (deformation) is one in which the deformation (rotation and deflection) under the load and s satisfies the virtual work equation. (internal work by the plastic moment at plastic hinges = external work by the loads on the structure) Uniqueness Theorem : This theorem states that if the load evaluated by static and kinematic theorems is same, then it is the true collapse load. All the three conditions of plastic analysis are satisfied. According to this theorem, there is only one unique solution for a given structure, while there are innumerable possible solutions with other theorems. All the three theorems are graphically shown in the figure below.

Methods of Plastic Analysis : Equilibrium or Static Method : This method is based on the lower bound theorem and consists of the following steps: i) The redundant forces are chosen. ii) Free BMD (Simply ed) of the structure is drawn. iii) Redundant BMD of the structure is drawn. iv) The two BMDs are combined and the peak moments are determined. The peak moment points are set the corresponding plastic moment, Mp . Also, check the number of plastic hinges formed. v) The collapse load is determined using the equilibrium condition by equating the maximum simply ed BM to the plastic moment at the corresponding point. vi) A check is applied so that plastic moment at any point is not > or = Mp at that point. vii) BMD and SFD are drawn if required.



Kinematic or Mechanism method: This method is based on the upper bound theorem and consists of the following steps: i) The possible points of plastic hinges (N) formation is located. They are invariably formed at points of maximum BM, Continuous s, Fixed s, rigid ts, etc., ii) The number of independent mechanisms and combined mechanisms are determined. In beams, only independent mechanisms are required. No. of independent mechanisms = N - SI , where N = No. of plastic hinges possible and SI = Static indeterminacy iii) Using the principle of virtual work, the equilibrium equation involving the internal work done by plastic moment, Mp and the external work done by loads are equated to determine the plastic collapse load. iv) A check is applied so that plastic moment at any point is not > or = Mp at that point. v) BMD and SFD are drawn if required. In this method , the elastic strain energy is ignored and the internal work done at only plastic hinges is considered. Virtual Work Principle: This principle is used for determining the collapse loads using mechanism method. This principle establishes the equilibrium relation between the work done by external loads and the internal work done by the plastic moment at specified location of plastic hinges. The principle is stated as follows : If a structure is subjected to a set of loads which is in equilibrium, a virtual displacement (deflection or rotation) at specified points will not alter the equilibrium of the structure with total work done being zero. With this, the virtual work equation can be written as External Work done by the loads = Internal Work done by the plastic moment a the location of the plastic hinges. Plastic analysis of beams : Beams can be analyzed by equilibrium or mechanism method. Usually, beams are subjected to transverse loads and only beam mechanisms occur. In continuous beam, each span is converted into a mechanism separately and lowest collapse load or the highest plastic moment is taken as the true value. It will be assumed that if one span collapses, the structure fails. In beams, mechanisms can be relevant or irrelevant. Relevant mechanisms are the correct mechanisms, where plastic hinges are assumed at maximum BM locations such as fixed , continuous , concentrated loads, point of zero shear etc., Irrelevant mechanisms are incorrect mechanisms, where plastic hinges are assumed to be at incorrect locations. In analysis, only relevant mechanisms are considered. No. of relevant mechanisms = N - SI N = No. of plastic hinges possible SI = Static indeterminacy



Problem 1 Simply ed beam with central concentrated load -

Equilibrium method Maximum free BM = WU * L / 4 Plastic moment of the section = MP Equating, WU * L / 4 = MP WU = 4 * M P / L Mechanism method Internal work done = 2 * MP * θ External work done = WU * δ From geometry, δ = (L / 2) * θ Equating, 2 * MP * θ = WU * (L / 2) * θ WU = 4 * M P / L Problem 2 Propped Cantilever with Central concentrated load Equilibrium method Maximum free BM = WU * L / 4 Plastic moment of the section = MP + MP / 2 = 1.5 MP Equating, WU * L / 4 = 1 5 MP WU = 6 * M P / L Mechanism method Internal work done = 3 * MP * θ External work done = WU * δ



From geometry, δ = (L / 2) * θ Equating, 3 * MP * θ = WU * (L / 2) * θ WU = 6 * M P / L

Problem 3 Propped Cantilever with UDL throughout



The location of the plastic hinge at C is carried out by segment equilibrium method. Let the hinge at C be at distance x from B. BC = x and AC = ( L- x) At C, SF = 0 Consider the segment BC, ΣMB = 0, MP - wu x2 / 2 = 0 wu = 2 MP / x2 ------------------------------ (1) Consider the segment AC, ΣMA = 0, wu (L-x)2 / 2 - 2 Mp = 0 wu = 4 Mp / (L-x)2 --------------------------- (2) Equating (1) and (2), 2 MP / x2 = 4 Mp / (L-x)2 Simplifying, we get x2 + 2Lx - L2 = 0 x=-L+√2*L x = 0.414 L (BC) and L - x = 0.586 L (AC) wu = 11.66 Mp / L2 Equilibrium method Simply ed BM at 0.414 L from B = wu L / 2 * 0.414L - wu * ( 0.414L)2 / 2 = 0.1213 wu L2 Plastic moment of the section = MP + 0.414 MP = 1.414 MP Equating, 1.414 MP = = 0.1213 wu L2 wu = 11.66 Mp / L2 Mechanism method Internal work done = 2 Mp θ + Mp θ1 External work done = 0.5 * L * δ * wu ( Area under the mechanism * intensity of loading) From geometry, δ = 0.586L θ = 0.414L θ1 Equating, 2 Mp θ + Mp θ1 = 0.5 * L * δ * wu 2 Mp θ + Mp * 1.415 θ = 0.5 * L * 0.586L θ * wu 3.415 Mp = 0.293 wu L2 wu = 11.66 Mp / L2 SFD if required can be drawn either in of Mp or wu



Problem 4 Propped Cantilever with two concentrated loads at collapse. Find Mp

Two plastic hinges can be formed at collapse. No. of possible plastic hinges = 3 (A, C and D) Two Relevant mechanisms are possible. Equilibrium method Plastic hinges at A and C Maximum free BM = 10 * 2.5 = 25 kNM Plastic moment of the section = MP + 0.5 MP = 1.5 MP Equating, 25 = 1.5 MP MP = 16.67 kNm Plastic hinges at A and D Maximum free BM = 20 * 1.25 = 25 kNM Plastic moment of the section = MP + 0.25 MP = 1.25 MP Equating, 25 = 1.25 MP MP = 20 kNm Adopt the largest value of MP = 20 kNm for design. Mechanism method Internal work done = 2 * MP * θ + MP * θ1 External work done = 20 * δ + 10 * δ1 From geometry, δ = 3.75 θ , δ = 1.25 θ1, θ1 = 3 θ and δ1 = 2.5 θ Equating, 2 * MP * θ + MP * θ1 = 20 * δ + 10 * δ1 2 * MP * θ + MP * 3 θ = 20 * 3.75 θ + 10 * 2.5 θ MP = 20 kNm



Problem 5 Calculate the collapse load for the fixed beam shown with Mp = 100 kNm

By inspection, we note that collapse occurs when plastic hinges are formed at A, C and D. Equilibrium method Plastic hinges at A, B and C Maximum free BM at C = (10 / 6) WU * 2 = (10 / 3) WU Plastic moment of the section = MP + MP = 2 MP Equating, (10 / 3) WU = 2 MP = 200 kNm WU = 60 kN Mechanism method Internal work done = 2 * MP * θ + 2 * MP * θ1 External work done = 2 WU * δ + WU * δ1 From geometry, δ = 2 θ , δ = 4 θ1, θ1 = 0.5 θ and δ1 = 2 θ1 = θ Equating internal and external work done, 2 * MP * θ + 2 * MP * θ1 = 2 WU * δ + WU * δ1 2 * MP * θ + 2 * MP * 0.5 θ = 2 WU * 2 θ + WU * θ 3MP = 5 WU WU = 0.6 MP = 60 kN The vertical reactions will be as in the case of simply ed beam. Problem 6 Calculate the collapse load for the fixed beam shown. The plastic hinges are formed at A , B and C based on crossing of shear force at C



The Simply ed reactions at A and B are 1.25WU and 0.75WU respectively. Equilibrium method Plastic hinges at A, B and C Maximum free BM at C = 0.75 WU * L Plastic moment of the section = MP + MP = 2 MP Equating, 0.75 WU * L = 2 MP WU = (8 / 3) MP / L Mechanism method Internal work done = 4 * MP * θ External work done = WU * δ + 0.5 * L * δ * WU / L From geometry, δ = L θ Equating internal and external work done, 4 * MP * θ = WU * δ + 0.5 * L * L θ * WU / L 4 * M P * θ = W U * L θ + WU * L θ / 2 4MP = 1.5 WU L WU = (8 / 3) MP / L Problem 7 Fixed beam with different plastic moments. The beam is shown in the figure. The Simply ed reactions at A and B are 1.25WU and 1.75WU respectively.



Equilibrium method Plastic hinges at A, B and D Maximum free BM at C = 1.25 WU * 2 = 2.50 WU Plastic moment of the section = MP + 1.25 MP = 2.25 MP Equating, 2.50 WU = 2.25 MP WU = 0.9 MP Plastic hinges at A, B and C Maximum free BM at C = 1.25 WU * 5 - WU * 3 = 3.25 WU Plastic moment of the section = MP + 1.625 MP = 2.625 MP Equating, 3.25 WU = 2.625 MP WU = 0.8077 MP Plastic hinges at A, B and E Maximum free BM at C = 1.75 WU * 2 = 3.5 WU Plastic moment of the section = 2 MP + 1.75 MP = 3.75 MP Equating, 3.5 WU = 3.75 MP WU = 1.0714 MP The lowest load of WU = 0.8077 MP is the true collapse load. Mechanism method Internal work done = 2 * MP * θ + 3 * MP * θ1 External work done = WU * δ2 + 2WU * δ1 From geometry, δ = 5 θ = 3 θ1, δ1 =2 θ1, δ2 =2 θ, θ1 = (5 / 3) θ Equating internal and external work done,



2 * MP * θ + 3 * MP * θ1 = WU * δ2 + 2WU * δ1 2 * MP * θ + 3 * MP * (5 / 3) θ = WU * 2 θ + 2WU * 2 * (5 / 3) θ 7MP = (26 / 3)WU WU = 0.8077 MP The reactions in the fixed beam can be obtained as follows : 2WU * 6 + WU * 2 + 2 MP - MP - VB * 8 = 0 VB = 1.538 MP VA = 0.885 MP SFD can be drawn. Problem 8 A two span continuous beam is shown below. All the loads are service loads.

No. of possible plastic hinges = 4 (B, Between A and B, under each concentrated load. No. of relevant mechanisms = 4 - 1 = 3 Each mechanism is similar to a propped cantilever. Mechanism 1 Plastic hinges will be at B and in between A and B. The distance x where the SF is zero is worked as in propped cantilever using segment equilibrium method. However, the value of plastic moment at B shall be chosen lesser of the two values ie MP. The plastic moment in between A and B is 2MP. The location of the plastic hinge at F is carried out by segment equilibrium method. Let the hinge at F be at distance x from A. AF = x and BF = (12 - x) At F, SF = 0 Consider the segment AF, ΣMA = 0, 2MP - 60 x2 / 2 = 0 MP = 15 x2 ------------------------------ (1)



Consider the segment BF, ΣMB = 0, 60 (12 - x)2 / 2 - 3 Mp = 0 MP = 10 (12 - x)2 --------------------------- (2) Equating (1) and (2), 15 x2 = 10 (12 - x)2 1.5 x2 = (12 - x)2 Simplifying, we get x = 5.394 m MP = 436.43 kNm Equilibrium Method Simply ed BM at 5.394 m from A – SS BM = 360 * 5.394 - 60 * 5.3942 / 2 = 1068.98 kNm Total Plastic Moment at the section = (2.0 + 0.45) MP = 2.45 MP Equating SS BM to the total plastic moment, 1068.98 = 2.45 MP MP = 436.32 kNm



Mechanism method Internal work done = 2 Mp θ2 + 3Mp θ1 External work done = 0.5 * 12 * δ * 60 = 360 δ From geometry, δ = 5.394 θ2 = 6.606 θ1 Equating, 2 Mp θ2 + 3Mp θ1 = 360 δ 2 Mp θ2 + 3Mp * (5.394 / 6.606) * θ2 = 360 * 5.394 θ2 4.45 Mp = 1941.84 Mp = 436.37 kNm Note : All methods give the same answer. The student shall check the question and accordingly answer. If no method is specified, then the student can have his /her choice. Mechanism 2 Plastic hinges will be formed at B and D ( under 150 kN load near B).

Equilibrium Method Simply ed BM at 3.0 m from B SS BM = 225 * 3.0 = 675 kNm Total Plastic Moment at the section = (1.0 + 2/3) MP = 5/3 MP Equating SS BM to the total plastic moment, 675 = 5/3 MP MP = 405 kNm



Mechanism method Internal work done = 2 Mp θ + Mp θ1 External work done = 225 * δ + 225 * δ1 From geometry, δ = 3 θ = 6 θ1 ; θ1 = 0.5 θ and δ1 = 3 θ1 = 1.5 θ Equating, 2 Mp θ + Mp θ1 = 225 * δ + 225 * δ1 2 Mp θ + Mp * 0.5 θ = 225 * 3 θ + 225 * 1.5 θ 2.5 Mp = 1012.5 Mp = 405 kNm Mechanism 3 Plastic hinges will be at B and E (under 150 kN load near C)

Equilibrium Method Simply ed BM at 3.0 m from C SS BM = 225 * 3.0 = 675 kNm Total Plastic Moment at the section = (1.0 + 1/3) MP = 4/3 MP Equating SS BM to the total plastic moment, 675 = 4/3 MP MP = 506.25 kNm



Mechanism method Internal work done = 2 Mp θ + Mp θ1 External work done = 225 * δ + 225 * δ1 From geometry, δ = 6 θ = 3 θ1 ; θ1 = 2 θ and δ1 = 3 θ Equating, 2 Mp θ + Mp θ1 = 225 * δ + 225 * δ1 2 Mp θ + Mp * 2 θ = 225 * 6 θ + 225 * 3 θ 4 Mp = 2025 Mp = 506.25 kNm The largest value of MP shall be chosen. For the given problem, MP = 506.25 kNm The reactions for the beams are calculated as in elastic analysis by taking moments about any and using the vertical equilibrium equation. The reactions are shown are below. BMD and SFD are also indicated. The BM has not exceeded the relevant plastic moment of the beam.



Note The student shall work similar problems for practice with two and three span continuous beams with different and loadings. If required BMD and SFD can be drawn. If end s are fixed, plastic hinges are formed and the span behaves as fixed beam. Sometimes, the value of MP will be given for each span and the collapse load will be required to be calculated. In such problems, the collapse load is worked for each span and the lowest load is chosen as the true collapse load.


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