<p class=”MsoNormal”>I am developing an ANSYS Mechanical model of a thin flexible plate (SHELL181 elements) with free boundary conditions. Gravity is applied over the entire plate. To simulate handling, I apply equal and opposite distributed pressure over four symmetrically placed patches so that the total force balances gravity and induces bending deformation.<\/p><p class=”MsoNormal”>The goal is to use this ANSYS model as a reference (ground truth) to validate a Kirchhoff–Love plate PDE model implemented in MATLAB. The geometric discretization and parameters are kept consistent between base model and ANSYS.<\/p><p class=”MsoNormal”>In the base model:<\/p><ul style=”margin-top: 0cm;” type=”disc”><li class=”MsoNormal”>Linear Kirchhoff plate formulation (no geometric nonlinearity)<\/li>\n
<li class=”MsoNormal”>Viscous damping proportional to velocity, normalized as:C\/D=5 and constant on all nodes<\/li>\n<\/ul>\n
<p>to match steady-state deformation and damping behavior with ANSYS,<\/p><p class=”MsoNormal”>1. How can I select Rayleigh damping (specifically stiffness-proportional coefficient (β) in ANSYS transient analysis to match the base model damping term C\/D=5 which is normalized by plate stiffness?<\/p><p class=”MsoNormal”>2. Should I use Static Structural or Transient analysis? Which is more appropriate for validating a linear plate model?<br data-start=”2251″ data-end=”2254″>3. The structure is unconstrained, so I use weak springs: Without weak springs –> solution fails & with large deflection ON –> solution does not converge<\/p><p data-start=”2410″ data-end=”2431″>Is it appropriate to:<\/p><ul data-start=”2432″ data-end=”2527″><li data-section-id=”1kgz494″ data-start=”2432″ data-end=”2456″>keep weak springs ON<\/li>\n
<li data-section-id=”7hzfyj” data-start=”2457″ data-end=”2527″>keep large deflection OFF (to remain consistent with linear theory)?<\/li>\n<\/ul>\n
<p>4. Upward prressure: <\/p><ul data-start=”2432″ data-end=”2527″><li data-section-id=”18380a0″ data-start=”2564″ data-end=”2643″>Distributed pressure on patches introduces a small imbalance (~1e−3 N in Z)<\/li>\n
<li data-section-id=”3itu2c” data-start=”2644″ data-end=”2720″>Remote displacement (Z=0, rotations free) produces different deformation<\/li>\n<\/ul>\n
<p data-start=”2722″ data-end=”2813″>Which approach is physically more appropriate for representing gripper action in this case?<\/p><p data-start=”2820″ data-end=”2869″><strong data-start=”2820″ data-end=”2850″>5. <\/strong>Current results:<\/p><ul data-start=”2870″ data-end=”2956″><li data-section-id=”tixw3g” data-start=”2870″ data-end=”2956″>Max deflection ≈ 0.198 m (consistent in static and transient analysis with β = 0.75)<\/li>\n<\/ul>\n
<p data-start=”2958″ data-end=”3013″>What are recommended criteria or checks to ensure that:<\/p><ul data-start=”3014″ data-end=”3187″><li data-section-id=”1fcmo69″ data-start=”3014″ data-end=”3065″>the force balance is correctly represented<\/li>\n
<li data-section-id=”bmfb6w” data-start=”3066″ data-end=”3187″>the deformation result is physically consistent and suitable as a reference for validating a reduced-order plate model?<\/li>\n<\/ul>\n
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