File: PVE-9729 Last Updated: Oct 14 / 2016, Cameron Moore, Ben Vanderloo, Laurence Brundrett

Here are some of our results using the 2016 release of SolidWorks Simulation: Simply Supported Rectangular Plate
A simply supported plate is first center point loaded and then uniformly loaded.
The plate is 1″ thick and 40″ on a side. Modulus of elasticity = 3 X 10^7 psi, Poisson’s ratio = 0.3.
Using symmetry restraints, only 1/4 of the plate is required. The outside edges are simply supported.
A mesh size of 1/2″ with thin plate elements produces a close match between theory and our FEA results. The image shows displacement.
Center Deflection
Center point load = 400 lbs
Center Deflection
Uniform Pressure = 1 psi
Theory 0.0027023 0.00378327
PVEng 0.0027046 0.0037855
%Error -0.0851% -0.0589%
Timoshenko, S. P. and Woinowsky-Krieger, “Theory of Plates and Shells,” McGraw-Hill Book Co., 2nd edition. pp. 120, 143, 1962.
Center point load: UY = (0.0116 * F * b2) / D
D = (E * h3) / (12* (1 – v2))
Uniform Pressure: UY = ( 0.00406 * q * b4) / D Deflection of a Cantilever Beam
A cantilever beam is subjected to a concentrated load (F = 1 lb) at the free end. Determine the deflections at the free end and the average shear stress. Dimensions of the cantilever are: L = 10″, h = 1″, t = 0.1″.
Deflection at free edge, inch Average Shear Stress, psi
Theory 0.001333 10
PVEng 0.001341 9.9407
%Error -0.6002% 0.5930%
UY = (F*L3 ) / (3 * E * I )
Average shear stress: τxy ave = V / ( t * h)
L = Beam length
E = Modulus of Elasticity
I = Area moment of inertia
V = Shear force
t = Beam thickness
h = Beam height Tip Displacements of a Circular Beam
A circular beam fixed at one end and free at the other end is subjected to a 200 lb force. Determine the deflections in the X, Y direction. Radius of curvature of the beam = 10″. The beam width and thickness are 4″ and 1″ respectively. This problem is solved using thin shell elements.
X Deflection at free edge, inch Y Deflection at free edge, inch
Theory 0.00712 0.01
PVEng 0.007137 0.009992
%Error -0.2388% 0.0800%
Warren C. Young, “Roark’s Formulas for Stress and Strain,” Sixth Edition, McGraw Hill Book Company, New York, 1989.
DX = ( 3/4 * π-2)* H R3 / (E *I) , DY = (1/2*H*R3 ) / ( E* I ), Modulus of elasticity = 3 X 107 psi

We documented our complete run of the 2010 SolidWorks Simulation static analysis validation set. Our results can be Downloaded.  In all cases, our results matched those obtained by SolidWorks, and also matched the theoretical results.