Last updated: 2026-09-10 5 min read

A plate containing a circular hole is a canonical example of finite elastic stress concentration caused by a geometric discontinuity. The solution changes rapidly in space while the hole boundary remains smooth, making it well suited to testing how accurately the elements capture a stress gradient and converge under local mesh refinement.

What this case verifies

  • The traction-free condition on a curved free surface
  • Plane-stress constitutive behavior and quarter-model symmetry
  • Stress-component transformation and circumferential post-processing
  • Local stress concentration and monotonic convergence with mesh refinement

Problem definition

Plate with Hole boundary conditions

A circular hole of radius aa is placed in a plate wide enough to approximate an infinite domain, with remote uniaxial tension σ0\sigma_0 . Load and geometric symmetry reduce the model to one quarter, and plane stress is assumed.

Reference solution

At the hole boundary r=ar=a , Kirsch's solution gives zero radial and shear traction:

σrr(a,θ)=0,τrθ(a,θ)=0\sigma_{rr}(a,\theta)=0, \qquad \tau_{r\theta}(a,\theta)=0

The circumferential stress is

σθθ(a,θ)=σ0(12cos2θ)\sigma_{\theta\theta}(a,\theta) = \sigma_0\left(1-2\cos 2\theta\right)

When θ\theta is measured from the loading axis, the maximum at θ=π/2\theta=\pi/2 is 3σ03\sigma_0 . Thus the elastic stress concentration factor is

Kt=σθθ,maxσ0=3K_t = \frac{\sigma_{\theta\theta,max}}{\sigma_0}=3

Unlike a crack-tip singularity, this is a finite concentration around a smooth boundary, so numerical convergence toward an exact value can be judged directly.

Results

Plate with Hole x-normal stress

QuantityTheoryFEMError
Stress concentration factor KtK_t3.002.92 → 2.99−2.7% → −0.3%

The error decreases monotonically from 12.7% to 4.3% to 0.34% under refinement. A coarse mesh initially under-resolves the local maximum, while refinement around the hole drives the result toward the exact value of 3.

Engineering significance

This verification is directly relevant to bolt holes, coolant passages, and housing openings. It also shows why a reported peak stress in a design should be accompanied by a local mesh-sensitivity check.

Reference

Back to the eight-case validation summary