However, this presumes that the small-sliding assumption remains valid. In general, small-sliding contacts achieve results that are very similar to those of finite-sliding. Like the nodal connectivity, ditching this step leads to significant performance improvements and better scalability. This avoids a costly sequential step that orders equations at every iteration. Similarly, the sparse solver can also reuse the same matrix structure throughout the simulation. Not having to perform this calculation at each iteration will certainly save on your computational costs. The value then remains unchanged for each iteration of the solution. Another advantage is that the nodal connectivity of the contact element is formed only once at the beginning of the analysis. This is especially true in models that have a low-quality geometry, mesh and non-smooth contact interfaces. Additionally, the logic behind the small sliding contact can solve complex contact models that the finite-sliding logic has difficulty with. These interactions are determined from the initial conditions. For large deflection analysis, this option still permits an arbitrary large rotation. The small-sliding contact assumes the contact interface between two parts will experience minimal motion during the entire analysis. It was found to be an accurate and computationally light option - if your simulation has an absence of large sliding. It also maintains sufficient accuracy while boasting a lower computational cost.ĪNSYS has performed extensive tests using small-sliding contacts to represent bonded contact pairs in small deflection models. Small-sliding contact can solve problems that finite-sliding contact may have difficulty solving. Forced Frictional Sliding should be used instead.However, I can say that ANSYS Mechanical made small-sliding contact the default contact type in small-deflection models or any bonded contact pairs. The coefficient of friction can be any nonnegative value. Once the shear stress is exceeded, the two geometries will slide relative to each other. In this setting, the two contacting geometries can carry shear stresses up to a certain magnitude across their interface before they start sliding relative to each other. This case corresponds to an infinite friction coefficient between the contacting bodies. Contact Types and Behaviours in Ansysīy default, no automatic closing of gaps is performed. Similar to the frictionless setting, these setting models perfectly rough frictional contact where there is no sliding. Weak springs are added to the assembly to help stabilize the model in order to achieve a reasonable solution. The model should be well constrained when using this contact setting.
#Ansys contact types free
A zero coefficient of friction is assumed, thus allowing free sliding. This solution is nonlinear because the area of contact may change as the load is applied. Thus gaps can form in the model between bodies depending on the loading. This setting models standard unilateral contact that is, normal pressure equals zero if separation occurs. Separation of the geometries in contact is not allowed. It only applies to regions of faces for 3D solids or edges for 2D plates.
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This contact setting is similar to the Bonded case. If contact is determined on the mathematical model, any gaps will be closed and any initial penetration will be ignored. If contact regions are bonded, then no sliding or separation between faces or edges is allowed. This is the default configuration and applies to all contact regions surfaces, solids, lines, faces, edges. Most of the types apply to Contact Regions made up of faces only. The available contact types are listed below. If convergence problems arise or if determining the exact area of contact is critical, consider using a finer mesh on the contact faces or edges. However, using these contact types usually results in longer solution times and can have possible convergence problems due to the contact nonlinearity. Choosing the appropriate contact type depends on the type of problem you are trying to solve.