beam bending

I have a cantilever beam, 8 in long, rectangular cross section W=0.75 in, H=1.5 in, E=29 msi, Poisson's=0.3, under uniform line load qy = -50 lbf/in (y direction) entire length, bending around strong axis (zz). Beam theory solution M*c/I gives max. stress = 5687 psi.

I model with ANSYS Workbench, uniform mesh Ex-3-6-3D-Normal-Stress.PNG attached.

If I refine the mesh I only get more and more stress concentration. Expected but how to avoid? I just want to get the same result as M*c/I to show how FEA can predict the same as beam theory. 

Hello All,

I am trying to build a homogenized model of beam elements and 2D solid elements in abaqus 6.12. I tried connecting beam elements with plane stress elements through sharing (common) nodes with basic interaction module. The node of beam element (lower end) and node of solid element (upper) are connected through a wire offered in interaction module. This wire have been assigned connector properties. I tried to connect with axial (translation) + rotation connector, so the bending of beam can be transferred to solid elements. But I did not get expected behavior.

Main Page

http://helper.orlovsoft.com/Default.aspx

Bean Bending Online on Microsoft Silverlight

http://helper.orlovsoft.com/Timik.aspx

Beam Mounting Help

http://helper.orlovsoft.com/Start.aspx

It seems that it will be useful for college students training:

http://www.orlovsoft.com/mmsamples/mmpage02.htm

Dear iMechanica,





suppose you have a beam with a square cross-section, manufactured from an elastic-ideally plastic material.



Now apply a load that rises linearly in time, but is locally constant along the beam length. Upon sagging, the beam will develop a plastic zone beginning in the top and surface regions at mid-length.

This is the "straight" problem solved in Prager, Hodge: Theory of perfectly plastic solids, publisher: Springer