Q: Definition check: A simply supported beam is one which is supported on more than two supports. Is this statement true?

Introduction / Context: Beam support conditions define statical determinacy and influence internal forces and deflections. Understanding the standard meaning of a simply supported beam avoids confusion with continuous beams and other boundary conditions. Given Data / Assumptions: Classical definitions from structural analysis. Supports are idealized as pin (hinge) and roller providing reactions without moment restraint. Concept / Approach: A simply supported beam is supported at its ends by a pin and a roller (two supports) allowing rotation and, in the case of the roller, horizontal movement. A beam supported at more than two points is a continuous beam and is generally statically indeterminate to a higher degree. Step-by-Step Solution: Define simply supported beam: two end supports, no end fixity.Compare with continuous beams: three or more supports → indeterminacy.Therefore, the statement claiming “more than two supports” is false. Verification / Alternative check: Textbook free-body diagrams and determinacy counts confirm that simply supported beams have two reaction points yielding three static unknowns (two verticals and possibly one horizontal), solvable by equilibrium alone if needed. Why Other Options Are Wrong: “True” contradicts the standard definition. “True only for continuous beams” mislabels a different category. Determinacy depends on constraints, not just number of supports; loading does not change the support definition. Common Pitfalls: Confusing “simply supported” with “continuous”; assuming any beam with no end fixity is simply supported regardless of additional intermediate supports (that makes it continuous, not simply supported). Final Answer: False

Q: Thick cylindrical shell under internal pressure For a thick-walled cylinder subjected to an internal pressure p, how does the circumferential (tangential/hoop) stress vary across the wall thickness?

Introduction / Context: Design of pressure vessels and gun barrels requires understanding the stress distribution in thick cylinders. Unlike thin shells where hoop stress is assumed uniform, thick cylinders exhibit a radial variation governed by Lame’s equations. Given Data / Assumptions: Cylinder subject to internal pressure p only (no external pressure). Axisymmetric, long cylinder; plane strain or generalized plane stress idealization. Linear elastic, homogeneous, isotropic material. Concept / Approach: Lame’s theory states that for a thick cylinder the radial stress σ_r and hoop (tangential) stress σ_θ vary with radius r as σ_r = A − B/r^2 and σ_θ = A + B/r^2. Constants A and B are found from boundary conditions (σ_r = −p at inner surface, σ_r = 0 at outer surface). Step-by-Step Solution: Apply boundary conditions to determine A and B in σ_θ = A + B/r^2.Because of the +B/r^2 term, σ_θ increases as r decreases toward the inner surface.Therefore hoop stress is highest at the inner radius and reduces toward the outer radius. Verification / Alternative check: Plotting σ_θ(r) from typical dimensions confirms a monotonic decrease from inner to outer surface when only internal pressure acts. Why Other Options Are Wrong: Uniform stress is a thin-shell assumption; options implying zero hoop stress at one surface contradict equilibrium and elasticity solutions. Common Pitfalls: Confusing radial stress (which is zero at the outer surface) with hoop stress; applying thin-wall results to thick-wall situations. Final Answer: Maximum at the inner surface and minimum at the outer surface

Q: Riveted joint detailing – Minimum edge distance (margin) To avoid tearing at the plate edge, what should be the minimum distance from the centre of a rivet hole to the nearest edge (margin), in terms of hole diameter d (in mm)?

Introduction / Context: Proper detailing of riveted joints ensures that plates do not tear at the edges under load. The minimum edge distance (margin) is a standard proportion in machine design and fabrication practice. Given Data / Assumptions: Unwelded, riveted lap or butt joint plate. Hole diameter d (mm) after drilling or punching. Need to prevent edge tearing and maintain manufacturability. Concept / Approach: If the rivet hole is placed too close to the edge, the ligament is weak and may tear. Empirical and codal recommendations prescribe a minimum margin to ensure adequate strength and avoid local failures. Step-by-Step Reasoning: Tearing strength along the edge ligament must exceed the force transferred by shear of rivets.A commonly adopted minimum margin for general machine design is 1.5 d, balancing strength and plate economy.Larger margins (2 d or more) may be used for thicker plates or severe service, but 1.5 d is the accepted minimum. Verification / Alternative check: Design handbooks and fabrication guides list 1.5 d as the minimum edge distance to prevent edge tearing and facilitate hole making without distortion. Why Other Options Are Wrong: d is too small and risks tearing; 2 d, 2.5 d, 3 d are conservative but not the minimum standard requirement for typical joints. Common Pitfalls: Confusing pitch/spacing with margin; using bolt diameter instead of hole diameter; not accounting for plate tolerance and hole drift. Final Answer: 1.5 d

Q: Combined stresses – Minimum normal (principal) stress under biaxial normal stresses σx, σy with in-plane shear τxy When a body is subjected to direct stresses σx and σy on mutually perpendicular planes and a shear stress τxy, what is the minimum nor…

Introduction / Context: Determining principal stresses under combined biaxial normal stresses with shear is fundamental for failure analysis using criteria such as maximum normal stress, maximum shear stress, or distortion energy. Given Data / Assumptions: Plane stress state with σx, σy, and τxy defined positive by standard sign convention. Linear elastic behavior; principal planes are orthogonal. Concept / Approach: Principal stresses are the extrema of normal stress on rotated planes where shear becomes zero. They are obtained from Mohr’s circle or the characteristic equation of the 2D stress tensor. Step-by-Step Solution: Principal stresses: σ1,2 = (σx + σy)/2 ± sqrt( ((σx − σy)/2)^2 + τxy^2 ).By definition, the minimum normal stress is σmin = (σx + σy)/2 − sqrt( ((σx − σy)/2)^2 + τxy^2 ).The maximum normal stress is the corresponding + sign. Verification / Alternative check: Construct Mohr’s circle with center at (σx + σy)/2 on the σ-axis and radius R = sqrt( ((σx − σy)/2)^2 + τxy^2 ). The leftmost intersection gives σmin as stated. Why Other Options Are Wrong: Option (b) is σmax; (c) is not a correct general expression; (d) and (e) are not invariant and ignore the quadratic coupling between σx, σy, and τxy. Common Pitfalls: Dropping the square on τxy; mixing up σmax and σmin; using absolute values incorrectly. Final Answer: (σx + σy)/2 − sqrt( ((σx − σy)/2)^2 + τxy^2 )

Q: Type of riveted joint pattern When rivets in adjacent rows are directly opposite each other, how is the riveted joint described?

Introduction / Context: Riveted joints are classified by the relative position of rivets in successive rows. Correct terminology is essential for fabrication drawings and strength calculations. Given Data / Assumptions: Multiple rows of rivets connecting plates. Interest is only in the positional pattern of rivets. Concept / Approach: In chain riveting, rivets in adjacent rows are aligned directly opposite, forming straight transverse lines. In zig-zag riveting, rivets in one row are staggered relative to the next, forming a zig-zag path. Step-by-Step Identification: Observe the rows: if rivets line up across rows, it is chain riveting.If rivets alternate positions between rows, it is zig-zag (staggered). Verification / Alternative check: Handbooks and codes use these standard definitions for layout and pitch computations. Why Other Options Are Wrong: “Zig-zag” implies stagger; “Diamond” is a special pattern; “Staggered lap” is a descriptive phrase, not the standard name; “Cruciform” refers to a type of joint configuration, not this pattern. Common Pitfalls: Confusing chain and zig-zag when pitches are unequal; misreading drawings. Final Answer: Chain riveted

Q: Definition of thin shell in pressure vessel design Evaluate the statement: “A pressure vessel is called a thin shell when it is made of thin sheets.”

Introduction / Context: The classification of pressure vessels as thin or thick shells determines the stress formulas used in design. It is based on geometry, not merely on how the vessel is fabricated. Given Data / Assumptions: Cylindrical shell of diameter d and wall thickness t. Internal pressure p, elastic material. Concept / Approach: A shell is considered thin when the wall thickness is small compared to its radius/diameter, so that stress through the thickness is nearly uniform and radial stress is negligible. A common criterion is t/d ≤ 1/20 (or t/r ≤ 1/10). Step-by-Step Reasoning: Check the geometric ratio t/d.If t/d ≤ about 1/20, thin-shell (use membrane formulas).If thicker, use Lame’s thick-cylinder theory with radial stress variation. Verification / Alternative check: Thin-shell formulas give hoop stress σ_h = p d / (2 t) and longitudinal stress σ_l = p d / (4 t), which assume negligible radial stress compared to σ_h and σ_l. Why Other Options Are Wrong: Fabrication by “thin sheets” is not the deciding factor; operating pressure and diameter alone do not define thinness without t/d. Common Pitfalls: Equating “sheet metal” with thin-shell theory; ignoring diameter’s role in t/d. Final Answer: Disagree

Q: Definition – Principal stress Is the direct normal stress acting across a principal plane known as the principal stress?

Introduction / Context: Principal stresses and planes are fundamental in failure analysis and stress transformation. On a principal plane, the shear stress is zero and the normal stress attains an extremum value. Given Data / Assumptions: Plane stress or 3D stress state in a linear elastic continuum. Principal planes are mutually orthogonal. Concept / Approach: By definition, a principal plane has zero shear stress. The corresponding normal stress on that plane is a principal stress (maximum, middle, or minimum depending on order). Step-by-Step Clarification: Find planes where τ = 0 via Mohr’s circle or eigenvalue problem.The normal stresses on these planes are σ1, σ2 (and σ3 in 3D).Therefore the direct normal stress across a principal plane is indeed the principal stress. Verification / Alternative check: Eigenvectors of the stress tensor give principal directions; eigenvalues are principal stresses—purely normal, no shear. Why Other Options Are Wrong: Presence of shear contradicts the definition; restriction to uniaxial or ductile materials is unnecessary. Common Pitfalls: Confusing maximum principal stress with Von Mises equivalent stress; mixing plane of maximum shear with principal plane. Final Answer: Yes

Q: Beam classification by end fixity A beam that is built-in (encastré) at both ends is referred to as which type?

Introduction / Context: Beam behavior depends strongly on end restraints. Knowing the correct classification is essential for selecting bending moment and deflection formulas. Given Data / Assumptions: Both ends are encastré (fully fixed: zero rotation and zero translation at supports). Linearly elastic, prismatic beam. Concept / Approach: A beam with both ends fixed is a fixed beam. By contrast, a simply supported beam has pin/roller supports allowing rotation; a cantilever is fixed at one end and free at the other; a continuous beam spans over more than two supports. Step-by-Step Reasoning: Identify boundary conditions: rotations at both ends are restrained.Thus, end moments develop even under symmetric loads, characteristic of a fixed beam. Verification / Alternative check: Deflection curves and moment diagrams of fixed beams show end negative moments compared to simply supported counterparts. Why Other Options Are Wrong: They do not match the described end fixity; continuous beams require three or more supports. Common Pitfalls: Confusing propped cantilever (fixed one end, simple support at the other) with a fully fixed beam. Final Answer: Fixed beam

Q: Thin cylinder under internal pressure – Ratio of longitudinal strain to hoop strain A thin cylindrical shell of diameter d, thickness t, and length l is subjected to internal pressure p. If ν is Poisson’s ratio, what is the ratio of longitudinal str…

Introduction / Context: Thin-cylinder membrane theory gives closed-form expressions for stresses and strains under internal pressure. The ratio of longitudinal to hoop strain is important for estimating changes in length and diameter. Given Data / Assumptions: Thin shell: t/d ≤ about 1/20, radial stress negligible compared to membrane stresses. Hoop stress σ_h = p d / (2 t); longitudinal stress σ_l = p d / (4 t). Linear elastic isotropic material with Young’s modulus E and Poisson’s ratio ν. Concept / Approach: Strains considering Poisson coupling are ε_h = (σ_h/E) − ν (σ_l/E) and ε_l = (σ_l/E) − ν (σ_h/E). Form the ratio ε_l / ε_h. Step-by-Step Solution: Let σ_l = 0.5 σ_h (from thin-cylinder stresses).ε_l = (σ_l − ν σ_h)/E = (0.5 σ_h − ν σ_h)/E = σ_h (0.5 − ν)/E.ε_h = (σ_h − ν σ_l)/E = (σ_h − ν * 0.5 σ_h)/E = σ_h (1 − 0.5 ν)/E.Therefore, ε_l / ε_h = (0.5 − ν) / (1 − 0.5 ν). Verification / Alternative check: For ν = 0.3, ε_l / ε_h = (0.2) / (0.85) ≈ 0.235, consistent with the fact that hoop strain exceeds longitudinal strain. Why Other Options Are Wrong: Inversions or ν-independent values contradict the derived dependence; expressions with (1 ± ν) are for other relationships (e.g., plane stress/plane strain conversions). Common Pitfalls: Ignoring Poisson’s effect and assuming ε_l/ε_h = σ_l/σ_h = 0.5; mixing thin and thick cylinder assumptions. Final Answer: (0.5 − ν) / (1 − 0.5 ν)

Question 1

Buckling versus crushing: For long (slender) columns, how does the Euler buckling load compare with the material's crushing (compressive) load?

Accepted Answer

Introduction / Context: Long columns fail by elastic instability at stresses far below the compressive strength of the material. Recognizing this distinction prevents unsafe designs that rely solely on compressive strength without checking Euler stability limits. Given Data / Assumptions: Slender column, length and end conditions such that Euler theory applies. Elastic behavior up to buckling. Crushing load refers to A * σ_c (material strength), far higher than elastic buckling load for slender members. Concept / Approach: Euler buckling load is P_cr = (π^2 * E * I) / (Le^2). As slenderness increases (Le large), P_cr drops rapidly. For sufficiently slender members, P_cr is much less than A * σ_c; thus buckling precedes material crushing. Step-by-Step Solution: Express P_cr and P_crushing = A * σ_c.Note P_cr ∝ 1 / (Le^2) → small for large Le.Hence for long columns, P_cr < P_crushing. Verification / Alternative check: Numerical example: For a steel strut with large slenderness, Euler critical stress may be a fraction (say 10–20%) of σ_y, confirming that buckling governs well before crushing. Why Other Options Are Wrong: “Equal to” applies only to a special transition slenderness, not generally for long columns. “More than” contradicts the inverse square dependence on Le. “Cannot be compared” ignores established formulas. Common Pitfalls: Using material compressive strength alone; neglecting effective length factor; overlooking imperfections that further reduce actual buckling load. Final Answer: less than

Question 2

Definition check: A simply supported beam is one which is supported on more than two supports. Is this statement true?

Accepted Answer

Introduction / Context: Beam support conditions define statical determinacy and influence internal forces and deflections. Understanding the standard meaning of a simply supported beam avoids confusion with continuous beams and other boundary conditions. Given Data / Assumptions: Classical definitions from structural analysis. Supports are idealized as pin (hinge) and roller providing reactions without moment restraint. Concept / Approach: A simply supported beam is supported at its ends by a pin and a roller (two supports) allowing rotation and, in the case of the roller, horizontal movement. A beam supported at more than two points is a continuous beam and is generally statically indeterminate to a higher degree. Step-by-Step Solution: Define simply supported beam: two end supports, no end fixity.Compare with continuous beams: three or more supports → indeterminacy.Therefore, the statement claiming “more than two supports” is false. Verification / Alternative check: Textbook free-body diagrams and determinacy counts confirm that simply supported beams have two reaction points yielding three static unknowns (two verticals and possibly one horizontal), solvable by equilibrium alone if needed. Why Other Options Are Wrong: “True” contradicts the standard definition. “True only for continuous beams” mislabels a different category. Determinacy depends on constraints, not just number of supports; loading does not change the support definition. Common Pitfalls: Confusing “simply supported” with “continuous”; assuming any beam with no end fixity is simply supported regardless of additional intermediate supports (that makes it continuous, not simply supported). Final Answer: False

Question 3

Thick cylindrical shell under internal pressure For a thick-walled cylinder subjected to an internal pressure p, how does the circumferential (tangential/hoop) stress vary across the wall thickness?

Accepted Answer

Introduction / Context: Design of pressure vessels and gun barrels requires understanding the stress distribution in thick cylinders. Unlike thin shells where hoop stress is assumed uniform, thick cylinders exhibit a radial variation governed by Lame’s equations. Given Data / Assumptions: Cylinder subject to internal pressure p only (no external pressure). Axisymmetric, long cylinder; plane strain or generalized plane stress idealization. Linear elastic, homogeneous, isotropic material. Concept / Approach: Lame’s theory states that for a thick cylinder the radial stress σ_r and hoop (tangential) stress σ_θ vary with radius r as σ_r = A − B/r^2 and σ_θ = A + B/r^2. Constants A and B are found from boundary conditions (σ_r = −p at inner surface, σ_r = 0 at outer surface). Step-by-Step Solution: Apply boundary conditions to determine A and B in σ_θ = A + B/r^2.Because of the +B/r^2 term, σ_θ increases as r decreases toward the inner surface.Therefore hoop stress is highest at the inner radius and reduces toward the outer radius. Verification / Alternative check: Plotting σ_θ(r) from typical dimensions confirms a monotonic decrease from inner to outer surface when only internal pressure acts. Why Other Options Are Wrong: Uniform stress is a thin-shell assumption; options implying zero hoop stress at one surface contradict equilibrium and elasticity solutions. Common Pitfalls: Confusing radial stress (which is zero at the outer surface) with hoop stress; applying thin-wall results to thick-wall situations. Final Answer: Maximum at the inner surface and minimum at the outer surface

Question 4

Riveted joint detailing – Minimum edge distance (margin) To avoid tearing at the plate edge, what should be the minimum distance from the centre of a rivet hole to the nearest edge (margin), in terms of hole diameter d (in mm)?

Accepted Answer

Introduction / Context: Proper detailing of riveted joints ensures that plates do not tear at the edges under load. The minimum edge distance (margin) is a standard proportion in machine design and fabrication practice. Given Data / Assumptions: Unwelded, riveted lap or butt joint plate. Hole diameter d (mm) after drilling or punching. Need to prevent edge tearing and maintain manufacturability. Concept / Approach: If the rivet hole is placed too close to the edge, the ligament is weak and may tear. Empirical and codal recommendations prescribe a minimum margin to ensure adequate strength and avoid local failures. Step-by-Step Reasoning: Tearing strength along the edge ligament must exceed the force transferred by shear of rivets.A commonly adopted minimum margin for general machine design is 1.5 d, balancing strength and plate economy.Larger margins (2 d or more) may be used for thicker plates or severe service, but 1.5 d is the accepted minimum. Verification / Alternative check: Design handbooks and fabrication guides list 1.5 d as the minimum edge distance to prevent edge tearing and facilitate hole making without distortion. Why Other Options Are Wrong: d is too small and risks tearing; 2 d, 2.5 d, 3 d are conservative but not the minimum standard requirement for typical joints. Common Pitfalls: Confusing pitch/spacing with margin; using bolt diameter instead of hole diameter; not accounting for plate tolerance and hole drift. Final Answer: 1.5 d

Question 5

Combined stresses – Minimum normal (principal) stress under biaxial normal stresses σx, σy with in-plane shear τxy When a body is subjected to direct stresses σx and σy on mutually perpendicular planes and a shear stress τxy, what is the minimum nor…

Accepted Answer

Introduction / Context: Determining principal stresses under combined biaxial normal stresses with shear is fundamental for failure analysis using criteria such as maximum normal stress, maximum shear stress, or distortion energy. Given Data / Assumptions: Plane stress state with σx, σy, and τxy defined positive by standard sign convention. Linear elastic behavior; principal planes are orthogonal. Concept / Approach: Principal stresses are the extrema of normal stress on rotated planes where shear becomes zero. They are obtained from Mohr’s circle or the characteristic equation of the 2D stress tensor. Step-by-Step Solution: Principal stresses: σ1,2 = (σx + σy)/2 ± sqrt( ((σx − σy)/2)^2 + τxy^2 ).By definition, the minimum normal stress is σmin = (σx + σy)/2 − sqrt( ((σx − σy)/2)^2 + τxy^2 ).The maximum normal stress is the corresponding + sign. Verification / Alternative check: Construct Mohr’s circle with center at (σx + σy)/2 on the σ-axis and radius R = sqrt( ((σx − σy)/2)^2 + τxy^2 ). The leftmost intersection gives σmin as stated. Why Other Options Are Wrong: Option (b) is σmax; (c) is not a correct general expression; (d) and (e) are not invariant and ignore the quadratic coupling between σx, σy, and τxy. Common Pitfalls: Dropping the square on τxy; mixing up σmax and σmin; using absolute values incorrectly. Final Answer: (σx + σy)/2 − sqrt( ((σx − σy)/2)^2 + τxy^2 )

Question 6

Type of riveted joint pattern When rivets in adjacent rows are directly opposite each other, how is the riveted joint described?

Accepted Answer

Introduction / Context: Riveted joints are classified by the relative position of rivets in successive rows. Correct terminology is essential for fabrication drawings and strength calculations. Given Data / Assumptions: Multiple rows of rivets connecting plates. Interest is only in the positional pattern of rivets. Concept / Approach: In chain riveting, rivets in adjacent rows are aligned directly opposite, forming straight transverse lines. In zig-zag riveting, rivets in one row are staggered relative to the next, forming a zig-zag path. Step-by-Step Identification: Observe the rows: if rivets line up across rows, it is chain riveting.If rivets alternate positions between rows, it is zig-zag (staggered). Verification / Alternative check: Handbooks and codes use these standard definitions for layout and pitch computations. Why Other Options Are Wrong: “Zig-zag” implies stagger; “Diamond” is a special pattern; “Staggered lap” is a descriptive phrase, not the standard name; “Cruciform” refers to a type of joint configuration, not this pattern. Common Pitfalls: Confusing chain and zig-zag when pitches are unequal; misreading drawings. Final Answer: Chain riveted

Question 7

Definition of thin shell in pressure vessel design Evaluate the statement: “A pressure vessel is called a thin shell when it is made of thin sheets.”

Accepted Answer

Introduction / Context: The classification of pressure vessels as thin or thick shells determines the stress formulas used in design. It is based on geometry, not merely on how the vessel is fabricated. Given Data / Assumptions: Cylindrical shell of diameter d and wall thickness t. Internal pressure p, elastic material. Concept / Approach: A shell is considered thin when the wall thickness is small compared to its radius/diameter, so that stress through the thickness is nearly uniform and radial stress is negligible. A common criterion is t/d ≤ 1/20 (or t/r ≤ 1/10). Step-by-Step Reasoning: Check the geometric ratio t/d.If t/d ≤ about 1/20, thin-shell (use membrane formulas).If thicker, use Lame’s thick-cylinder theory with radial stress variation. Verification / Alternative check: Thin-shell formulas give hoop stress σ_h = p d / (2 t) and longitudinal stress σ_l = p d / (4 t), which assume negligible radial stress compared to σ_h and σ_l. Why Other Options Are Wrong: Fabrication by “thin sheets” is not the deciding factor; operating pressure and diameter alone do not define thinness without t/d. Common Pitfalls: Equating “sheet metal” with thin-shell theory; ignoring diameter’s role in t/d. Final Answer: Disagree

Question 8

Definition – Principal stress Is the direct normal stress acting across a principal plane known as the principal stress?

Accepted Answer

Introduction / Context: Principal stresses and planes are fundamental in failure analysis and stress transformation. On a principal plane, the shear stress is zero and the normal stress attains an extremum value. Given Data / Assumptions: Plane stress or 3D stress state in a linear elastic continuum. Principal planes are mutually orthogonal. Concept / Approach: By definition, a principal plane has zero shear stress. The corresponding normal stress on that plane is a principal stress (maximum, middle, or minimum depending on order). Step-by-Step Clarification: Find planes where τ = 0 via Mohr’s circle or eigenvalue problem.The normal stresses on these planes are σ1, σ2 (and σ3 in 3D).Therefore the direct normal stress across a principal plane is indeed the principal stress. Verification / Alternative check: Eigenvectors of the stress tensor give principal directions; eigenvalues are principal stresses—purely normal, no shear. Why Other Options Are Wrong: Presence of shear contradicts the definition; restriction to uniaxial or ductile materials is unnecessary. Common Pitfalls: Confusing maximum principal stress with Von Mises equivalent stress; mixing plane of maximum shear with principal plane. Final Answer: Yes

Question 9

Beam classification by end fixity A beam that is built-in (encastré) at both ends is referred to as which type?

Accepted Answer

Introduction / Context: Beam behavior depends strongly on end restraints. Knowing the correct classification is essential for selecting bending moment and deflection formulas. Given Data / Assumptions: Both ends are encastré (fully fixed: zero rotation and zero translation at supports). Linearly elastic, prismatic beam. Concept / Approach: A beam with both ends fixed is a fixed beam. By contrast, a simply supported beam has pin/roller supports allowing rotation; a cantilever is fixed at one end and free at the other; a continuous beam spans over more than two supports. Step-by-Step Reasoning: Identify boundary conditions: rotations at both ends are restrained.Thus, end moments develop even under symmetric loads, characteristic of a fixed beam. Verification / Alternative check: Deflection curves and moment diagrams of fixed beams show end negative moments compared to simply supported counterparts. Why Other Options Are Wrong: They do not match the described end fixity; continuous beams require three or more supports. Common Pitfalls: Confusing propped cantilever (fixed one end, simple support at the other) with a fully fixed beam. Final Answer: Fixed beam

Question 10

Thin cylinder under internal pressure – Ratio of longitudinal strain to hoop strain A thin cylindrical shell of diameter d, thickness t, and length l is subjected to internal pressure p. If ν is Poisson’s ratio, what is the ratio of longitudinal str…

Accepted Answer

Introduction / Context: Thin-cylinder membrane theory gives closed-form expressions for stresses and strains under internal pressure. The ratio of longitudinal to hoop strain is important for estimating changes in length and diameter. Given Data / Assumptions: Thin shell: t/d ≤ about 1/20, radial stress negligible compared to membrane stresses. Hoop stress σ_h = p d / (2 t); longitudinal stress σ_l = p d / (4 t). Linear elastic isotropic material with Young’s modulus E and Poisson’s ratio ν. Concept / Approach: Strains considering Poisson coupling are ε_h = (σ_h/E) − ν (σ_l/E) and ε_l = (σ_l/E) − ν (σ_h/E). Form the ratio ε_l / ε_h. Step-by-Step Solution: Let σ_l = 0.5 σ_h (from thin-cylinder stresses).ε_l = (σ_l − ν σ_h)/E = (0.5 σ_h − ν σ_h)/E = σ_h (0.5 − ν)/E.ε_h = (σ_h − ν σ_l)/E = (σ_h − ν * 0.5 σ_h)/E = σ_h (1 − 0.5 ν)/E.Therefore, ε_l / ε_h = (0.5 − ν) / (1 − 0.5 ν). Verification / Alternative check: For ν = 0.3, ε_l / ε_h = (0.2) / (0.85) ≈ 0.235, consistent with the fact that hoop strain exceeds longitudinal strain. Why Other Options Are Wrong: Inversions or ν-independent values contradict the derived dependence; expressions with (1 ± ν) are for other relationships (e.g., plane stress/plane strain conversions). Common Pitfalls: Ignoring Poisson’s effect and assuming ε_l/ε_h = σ_l/σ_h = 0.5; mixing thin and thick cylinder assumptions. Final Answer: (0.5 − ν) / (1 − 0.5 ν)

Question 11

Euler’s column theory – Critical load for a pin-ended (hinged-hinged) column According to Euler, what is the crippling (critical) load for a column of length l with both ends hinged?

Accepted Answer

Introduction / Context: Euler’s buckling formula gives the elastic critical load for long, slender columns. The effective length depends on end conditions. Given Data / Assumptions: Slender prismatic column, linear elastic material. Both ends hinged (pin–pin), no end moment restraint. Initial imperfections small; loading concentric. Concept / Approach: The Euler load is P_cr = π^2 * E * I / (L_e^2), where L_e is the effective length. For hinged–hinged ends, L_e = l. Step-by-Step Solution: Identify end condition factor K = 1.0 for hinged–hinged.Compute L_e = K * l = l.Therefore P_cr = π^2 * E * I / l^2. Verification / Alternative check: Comparing with other end conditions: fixed–fixed has L_e = l/2 (four times higher P_cr), fixed–free has L_e = 2l (one-quarter P_cr). Why Other Options Are Wrong: They use incorrect multipliers or dimensions; the only correct expression for pin–pin is π^2 E I / l^2. Common Pitfalls: Confusing effective length factors; mixing units of E, I, and length. Final Answer: P_cr = π^2 * E * I / l^2

Question 12

Elastic constants – quick evaluation: For an isotropic material with Poisson’s ratio v = 0.25, what is the ratio of bulk modulus to Young’s modulus (K / E)?

Accepted Answer

Introduction / Context: Bulk modulus K and Young’s modulus E are two fundamental elastic constants for isotropic materials. Knowing how they relate through Poisson’s ratio v allows quick conversions between laboratory test data and design parameters. This question checks your fluency with the standard isotropic elasticity relations. Given Data / Assumptions: Material is homogeneous and isotropic. Poisson’s ratio v = 0.25 (dimensionless). Small-strain linear elasticity applies. Concept / Approach: The well-known relation between E, K, and v in isotropy is K = E / (3 * (1 − 2v)). Rearranging gives K / E = 1 / (3 * (1 − 2v)). Substituting v immediately yields the numerical ratio without unit conversions, because both K and E have identical dimensions (stress). Step-by-Step Solution: Start with K = E / (3 * (1 − 2v)).Form the ratio: K / E = 1 / (3 * (1 − 2v)).Plug in v = 0.25 → 1 − 2v = 1 − 0.5 = 0.5.Therefore K / E = 1 / (3 * 0.5) = 1 / 1.5 = 2 / 3. Verification / Alternative check: Use the companion identity E = 3 * K * (1 − 2v). Solving for K / E provides the same expression. For v in the common metallic range (0.25 to 0.35), K is typically of the same order as E, which is consistent with 2/3 for v = 0.25. Why Other Options Are Wrong: 1/3 or 1/2: arise from omitting the factor (1 − 2v) or misapplying the 3. 1: would require v = 0, which is not the case. 3/2: inverted relationship; not physically consistent. Common Pitfalls: Confusing the E–K relation with E–G (E = 2 * G * (1 + v)). Always check which modulus is in the formula and keep track of the 3 and (1 − 2v) factors. Final Answer: 2/3

Question 13

Eccentrically loaded columns – nature of stress: When a column carries an eccentric load, what kinds of stresses are induced in the cross-section?

Accepted Answer

Introduction / Context: Columns are often loaded away from the centroidal axis due to construction tolerances or intentional eccentricity (e.g., brackets). Such eccentricity changes the internal stress state from pure compression to a combination that designers must assess for safety against crushing and buckling. Given Data / Assumptions: Eccentric axial load P acting at an eccentricity e from the centroidal axis. Prismatic, homogeneous column section. Small deflection and linear elastic behavior for section stress evaluation. Concept / Approach: An eccentric axial load is statically equivalent to a concentric load P (causing uniform direct compressive stress) plus a bending moment M = P * e (causing a linear compressive–tensile stress distribution). The resulting stress at a fibre is the algebraic sum of direct and bending components. Step-by-Step Solution: Direct stress: sigma_d = P / A.Bending moment: M = P * e.Bending stress at a fibre: sigma_b = M * y / I.Resultant stress: sigma = sigma_d ± sigma_b = (P / A) ± (P * e * y / I). Verification / Alternative check: At the neutral axis y = 0, only direct stress remains. At extreme fibres, bending may reduce or add to direct compression, potentially producing tension if (P * e * y / I) > (P / A). Why Other Options Are Wrong: Direct only / bending only: omit half of the statically equivalent effects. Shear only: eccentric axial loading does not create a primary shear resultant in uniform prismatic members. Direct and torsional: torsion requires a moment about the longitudinal axis, which is not produced by simple planar eccentricity. Common Pitfalls: Ignoring tension possibility on one side, or using net section area after cracking without justification. Always check maximum and minimum fibre stresses. Final Answer: Direct and bending stress both

Question 14

Riveted joints – shear condition: In a double-strap butt joint with equal cover straps on both sides, the rivets are in which shear condition?

Accepted Answer

Introduction / Context: Riveted butt joints use cover plates (straps) to connect the main plates. The number and placement of straps control the load path through rivets and thus whether the rivets experience single shear or double shear. Recognizing this is essential for calculating joint efficiency and rivet strength. Given Data / Assumptions: Butt joint with two equal cover straps, one on each side of the main plates. Load is axial, transmitted symmetrically through straps. Neglect secondary bending due to eccentricity of load path. Concept / Approach: With two cover straps, load from one main plate to the other splits into two parallel shear planes across each rivet shank. The rivet is thus cut by two shear planes (one to each strap), placing it in double shear. This doubles the nominal shear area compared to single-strap configurations, increasing rivet shear capacity. Step-by-Step Solution: Identify load path: plate → upper strap via rivets, and plate → lower strap via rivets.Each rivet has two shear planes: one between the first plate and near strap, another between the second plate and far strap.Conclusively, the rivet experiences double shear under symmetric loading. Verification / Alternative check: Compare to a single-strap butt joint: there is only one strap and one shear plane through each rivet, resulting in single shear. Adding the second strap creates the second shear plane. Why Other Options Are Wrong: Single shear / either-or: contradict the symmetric two-strap configuration. Never in shear / torsion: rivets primarily carry shear in these joints; torsion is not a basic design action here. Common Pitfalls: Forgetting eccentric load distribution if straps are unequal; with equal straps and proper fit, double shear is the governing idealization. Final Answer: Always in double shear

Question 15

Material idealization of RCC members: A reinforced cement concrete (RCC) beam is best considered as which kind of material system for analysis and design?

Accepted Answer

Introduction / Context: Reinforced cement concrete (RCC) members combine two distinct materials—concrete and steel—to exploit their complementary strengths. Understanding the correct idealization informs how we distribute stresses and calculate capacities for bending, shear, and serviceability. Given Data / Assumptions: RCC beam with steel reinforcement embedded in concrete. Perfect bond assumed between steel and concrete within the elastic range. Modular ratio or transformed section concept used in elastic analysis. Concept / Approach: Concrete is strong in compression but weak in tension, whereas steel excels in tension and has ductility. Together they form a composite system where different constituents share load. Analysis often transforms steel area into an equivalent concrete area using the modular ratio n = E_s / E_c, explicitly acknowledging composite behavior. Step-by-Step Solution: Recognize constituents: concrete (matrix) + steel (reinforcement).Assume strain compatibility due to bond: epsilon_concrete = epsilon_steel at a given level.Use transformed section method: A_s(eq) = n * A_s to compute neutral axis and stresses.Conclude that RCC behaves as a composite section, not as a single homogeneous or purely isotropic material. Verification / Alternative check: Experimental strain profiles in RCC beams show consistent strain compatibility and distinct stress sharing, validating the composite model. Design codes (e.g., working stress or limit state methods) are built on this notion. Why Other Options Are Wrong: Homogeneous / isotropic: would imply identical material properties throughout, which is not true. “Hetrogeneous” alone: although constituents differ, the engineering idealization that drives analysis is specifically a composite section with bonded interaction. Viscoelastic: time-dependent effects exist, but the primary classification for structural analysis is composite. Common Pitfalls: Ignoring bond slip or cracking effects; at ultimate states, cracked section analysis and tension stiffening concepts refine the composite model. Final Answer: Composite material

Question 16

Mohr’s circle – scope of application: Mohr’s circle can be used to find stresses on an oblique plane of a body subjected to which of the following loading combinations?

Accepted Answer

Introduction / Context: Mohr’s circle is a powerful graphical tool for 2D stress transformation. It provides principal stresses, maximum shear stress, and normal and shear stresses on any oblique plane from a single diagram, unifying different combined-stress scenarios. Given Data / Assumptions: Plane stress condition (sigma_x, sigma_y, tau_xy) acting on a differential element. Linear elastic continuum; sign conventions consistent. Interest is in stresses on a plane at angle theta from the reference axis. Concept / Approach: Mohr’s circle plots normal stress on the abscissa and shear stress on the ordinate. For any given 2D state, the center C is at ( (sigma_x + sigma_y)/2, 0 ) and the radius R = sqrt( ((sigma_x − sigma_y)/2)^2 + tau_xy^2 ). Rotating 2 * theta around the circle yields the transformed stresses on a plane at angle theta. Step-by-Step Solution: Construct circle with center and radius from the given sigma_x, sigma_y, tau_xy.A pure uniaxial case with shear (option a) maps to a circle offset from zero with nonzero tau.Two perpendicular direct stresses without shear (option b) map to a circle with tau_xy = 0.The most general 2D case (option c) is directly represented and solved. Verification / Alternative check: The analytical transformation equations sigma_theta = (sigma_x + sigma_y)/2 + ((sigma_x − sigma_y)/2) * cos(2theta) + tau_xy * sin(2theta) and tau_theta = −((sigma_x − sigma_y)/2) * sin(2theta) + tau_xy * cos(2theta) yield identical results to the circle construction, confirming its universality in plane stress. Why Other Options Are Wrong: Each individual option (a), (b), or (c) is a subset; the comprehensive answer is that Mohr’s circle handles all of them. “None” contradicts standard strength-of-materials practice. Common Pitfalls: Misinterpreting the 2*theta rotation rule; forgetting sign conventions for shear; or applying plane-stress Mohr’s circle to 3D states without modification. Final Answer: All of the above

Question 17

Neutral axis and centroid in symmetric beams: State whether the following is true or false: “For a symmetrical, homogeneous beam section under pure bending, the neutral axis does not pass through the centroid.”

Accepted Answer

Introduction / Context: The neutral axis (NA) is the locus of zero normal stress in bending. For many common engineering sections, quickly locating the NA is essential for stress calculation using the flexure formula. This item checks conceptual understanding of where the NA lies relative to the centroid for symmetric, homogeneous sections. Given Data / Assumptions: Homogeneous, isotropic material. Symmetric prismatic cross-section. Pure bending without shear. Concept / Approach: Under Euler–Bernoulli assumptions, plane sections remain plane and strain varies linearly with distance y from the NA: epsilon = y / rho. Enforcing zero resultant normal force over the cross-section in pure bending makes the NA pass through the centroid for homogeneous sections. Hence, for symmetric homogeneous beams, the NA coincides with the centroidal axis. Step-by-Step Solution: Flexure formula: sigma = M * y / I.Zero net normal force requires integral of sigma over area to be zero.That condition is satisfied when the NA passes through the centroid (first moment about NA equals zero).Therefore, the quoted statement is false for symmetrical homogeneous beams. Verification / Alternative check: Standard shapes (rectangular, circular, I-section with symmetric flanges/web) have NA through centroid in homogeneous materials. Composite or transformed sections are the cases where NA shifts away from geometric centroid. Why Other Options Are Wrong: Agree: contradicts beam theory fundamentals for homogeneous, symmetric sections. Conditional options apply to unsymmetrical or composite sections, not to the stated case. Common Pitfalls: Confusing centroidal axis with NA in cracked or composite sections, where transformed area methods are needed. Final Answer: Disagree

Question 18

Shear in UDL case: For a simply supported beam carrying a uniformly distributed load of intensity w per unit length over the full span, what is the shear force at the midspan (centre) of the beam?

Accepted Answer

Introduction / Context: Shear force and bending moment distributions under simple load cases are staple knowledge in structural analysis. For a uniformly distributed load (UDL), recognizing the symmetry of shear lets you answer midspan values instantly—useful for quick checks in design and exams. Given Data / Assumptions: Simply supported beam with span l. UDL of intensity w acts along the entire span. Static, linear elastic behavior; supports provide vertical reactions only. Concept / Approach: For a symmetric UDL, reactions at supports are equal: R_A = R_B = w l / 2. Shear force V(x) at a distance x from the left support equals R_A − w x, a straight line decreasing from +w l / 2 to −w l / 2. The point where V = 0 is the midspan. Step-by-Step Solution: Compute reactions: R_A = R_B = w l / 2.Write V(x) = R_A − w x.At midspan x = l / 2: V(l/2) = (w l / 2) − w (l / 2) = 0.Hence the shear force at the centre is zero. Verification / Alternative check: The shear diagram is a straight line crossing zero at midspan. The maximum bending moment occurs where shear is zero, i.e., at the midspan, confirming internal consistency (M_max = w l^2 / 8). Why Other Options Are Wrong: w l^2 / 2, w l^2 / 4, w l^2 / 8 are bending-moment-like terms (units of force*length), not shear. w l / 2 is the end shear (support reaction), not the midspan shear. Common Pitfalls: Mixing up shear and moment formulas; always check dimensional consistency to avoid such errors. Final Answer: Zero

Question 19

Flexure formula insight: When a beam is subjected to bending moment, the normal stress at any point varies how with the distance of that point from the neutral axis?

Accepted Answer

Introduction / Context: The classic flexure formula sigma = M * y / I underpins most beam stress calculations. It tells us exactly how normal stress varies from the neutral axis to the extreme fibres and is key to sizing sections efficiently. Given Data / Assumptions: Euler–Bernoulli beam theory (plane sections remain plane). Homogeneous, isotropic material; linear elasticity. Pure bending or regions where shear is negligible. Concept / Approach: The strain distribution is linear: epsilon = y / rho. Using Hooke’s law, sigma = E * epsilon = E * y / rho. Combining with the curvature relation M / I = E / rho yields sigma = (M / I) * y, explicitly showing direct proportionality between stress magnitude and distance from the neutral axis. Step-by-Step Solution: Start: epsilon = y / rho.Apply Hooke’s law: sigma = E * y / rho.Use M / I = E / rho → sigma = (M / I) * y.Therefore, sigma increases linearly with |y| and changes sign across the neutral axis. Verification / Alternative check: Maximum stress occurs at extreme fibres where |y| is largest; zero stress at y = 0 (neutral axis). This matches both theoretical derivation and experimental strain gauge data. Why Other Options Are Wrong: Equal to / independent of distance: contradict linear variation. Inverse or quadratic dependence: not supported by the flexure formula under standard assumptions. Common Pitfalls: For composite or cracked sections, the neutral axis location changes; still, within each transformed section, the variation remains linear with local y. Final Answer: Directly proportional to the distance

Question 20

Types of strain – basic definition: When a change in length occurs in a member under load, what is the appropriate name of the strain developed?

Accepted Answer

Introduction / Context: Strain describes deformation normalized by original dimensions. Correctly naming the type of strain is important for applying the right constitutive relations and for interpreting test data such as tensile tests on bars or coupons. Given Data / Assumptions: A prismatic bar changes its length under axial loading. Small deformations so engineering strain definitions apply. Isotropic homogeneous material (not essential for naming). Concept / Approach: Linear (or longitudinal) strain is the ratio of change in length to original length along the direction of the applied load. If the bar elongates by delta L from an original length L, linear strain epsilon = delta L / L. Lateral strain refers to the concurrent contraction/expansion perpendicular to the load due to Poisson’s effect. Volumetric strain sums the three principal linear strains. Step-by-Step Solution: Identify deformation mode: change in length along the load direction.Use definition: epsilon_linear = delta L / L.Recognize accompanying lateral strain may exist, but the question asks specifically about strain due to change in length.Therefore, the correct term is linear strain. Verification / Alternative check: Tensile test stress–strain curves plot axial stress against axial (linear) strain; this is the primary measure reported for material properties such as Young’s modulus E. Why Other Options Are Wrong: Lateral strain: transverse response, not the axial change described. Volumetric strain: sum of principal linear strains; more general measure. Shear strain: associated with angular distortion, not axial change. Thermal strain: cause-based descriptor; the question is geometric, not causal. Common Pitfalls: Confusing cause and effect (thermal vs mechanical). Regardless of cause, if the measured deformation is axial length change, the strain type is linear. Final Answer: Linear strain

Strength of Materials Questions