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22-Mec-A7 Advanced Strength of Materials · Undated paper

Question 8 of 8: Thick cylinder: Tresca vs Von Mises

Nivaar worked solution (AI-drafted; not reviewed by a licensed engineer)

Notes on this paper

Paper format: National Exam — 16-Mec-A7 Advanced Strength of Materials (May 2019). Open-book; eight problems of equal value; any five constitute a complete paper. Every problem is solved as a study resource.

Reference texts: Boresi & Schmidt, Advanced Mechanics of Materials (6th ed.); Ugural & Fenster, Advanced Strength and Applied Elasticity; Timoshenko & Goodier, Theory of Elasticity; Hibbeler, Mechanics of Materials.

Question 8: Thick cylinder: Tresca vs Von Mises (20 marks)

Question text not reproduced: the examination questions are © Engineers and Geoscientists BC. Open the official past paper (linked at the top of this page) to read the question, then follow the worked solution below.

Given. A thick-walled cylinder under internal pressure eight times the external pressure.

Given data
Internal diameter0.11 m (ri = 55 mm)
External diameter0.175 m (ro = 87.5 mm)
Yield strength$\sigma_Y=289$ MPa
Poisson's ratio$\nu=0.29$
Pressure ratio$p_i=8p_e$

Find. the allowable internal pressure by (a) the maximum-shear (Tresca) and (b) the Von Mises yield criteria.

rᵢrₒpₕpₑ
Thick cylinder cross-section; internal pressure pₕ = 8 pₑ.

Approach. Evaluate the Lamé stresses at the inner wall (the critical radius), take the closed-end axial stress as the mean of radial and hoop, then apply each yield criterion at first yield.

  1. Lamé stresses at the bore. With $r_i=55$, $r_o=87.5$ mm and $p_e=p_i/8$, $$\sigma_\theta=1.893\,p_i,\qquad \sigma_r=-p_i,\qquad \sigma_z=\tfrac12(\sigma_\theta+\sigma_r)=0.447\,p_i\ \text{(closed end)}.$$
  2. Maximum-shear (Tresca). The extreme principals are $\sigma_\theta$ and $\sigma_r$, so $\sigma_\theta-\sigma_r=\sigma_Y$ gives $$2.893\,p_i=289\ \Rightarrow\ \boxed{p_i=99.9\ \text{MPa}}.$$
  3. Von Mises. For $\sigma_z$ equal to the mean, $\sigma_{vM}=\tfrac{\sqrt3}{2}(\sigma_\theta-\sigma_r)=\sigma_Y$, hence $$p_i=\frac{289}{2.505}=\boxed{115.4\ \text{MPa}}.$$
Check: The source states neither a factor of safety nor the end condition. The closed-end assumption (σz = mean) is adopted, and "allowable" is taken as the first-yield pressure. If a factor of safety N is required, divide both results by N; an open-end vessel (σz = 0) would instead give pi,Tresca unchanged and a slightly higher Von Mises value.

Von Mises permits about 15% more pressure than Tresca — the fixed factor 2/√3 that always separates the two criteria when the axial stress is the intermediate principal. Tresca is the conservative choice for a code-compliant design.

Final results
p_i by Tresca99.9 MPa
p_i by Von Mises115.4 MPa
Ratio$2/\sqrt3=1.155$
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