Pure flexure

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Bilinear quadrilateral elements are used to solve the infinitesimal pure bending problem.

Bilinear quadrilateral elements are used to solve the pure bending problem. For our simulations we’ll consider a beam of depth $d=1$ and length $L=5$ . The left end has the horizontal displacements restrained to zero for all nodes, and the vertical displacement is fixed to zero at the center node only. The right end is to be loaded by a pure bending moment of value 1. Use full quadrature $(2 \times 2)$ .

Let $E=100$ and consider values for $\nu$ of $0,0.3,0.45$ , and $0.499$ . For each of these values, perform a convergence analysis with meshes consisting of $2 \times 4,4 \times 8,8 \times 16$ and $16 \times 32$ elements. Plot the relative error of the tip vertical deflection (middle node of the right end), when compared with the exact solution of the thin-beam theory (note that we consider plane strain conditions), versus the number of elements along the length for each Poisson ratio. You should note the tendency to lock for the higher Poisson ratios.

The exact 3D solution is given by:

\begin{aligned} u_2 &= -xy/R \\ u_y &= yz/R \\ u_z &= (\nu x^2 + y^2 - z^2)/R \end{aligned}

with $R = \tfrac{1}{12} Ed^3$ .

Deformed cross section from 3D solution of pure flexure.

Note:

For this case, both the Euler and Timoshenko theories are equivalent.
The classical Euler solution to this problem is an exact solution to the continuum mechanics problem, provided transverse strains are not constrained in the plane. This was first shown by Saint Venant in his treatise on Torsion [@timoshenko1983history].

3D Bricks

Plane Strain

Plane Stress

Plane Tapered Cantilever

Rigid Offsets