{"id":3599,"date":"2023-06-12T11:16:07","date_gmt":"2023-06-12T11:16:07","guid":{"rendered":"https:\/\/plm.systemworkx.de\/docs\/cyclic-symmetry-in-abaqus-fea\/"},"modified":"2023-07-17T10:52:39","modified_gmt":"2023-07-17T10:52:39","password":"","slug":"cyclic-symmetry-in-abaqus-fea","status":"publish","type":"docs","link":"https:\/\/plm.systemworkx.de\/en\/docs\/cyclic-symmetry-in-abaqus-fea\/","title":{"rendered":"Cyclic symmetry in Abaqus FEA"},"content":{"rendered":"

<\/div><\/div><\/span>

Introduction<\/h2><\/h2><\/span>
<\/div><\/div><\/div>

Cyclic symmetry finds application in the linear\/nonlinear analysis of structures that can be divided into n equal substructures when orbiting about a given axis of rotation. For this purpose, it is sufficient to determine the solution for a substructure (so-called sector).
\nThe procedure is simple: a cyclic sector is cut out of the overall structure. Cyclic symmetry is defined at the intersections at the Primary and Secondary surfaces via an interaction in the INITIAL STEP. Instead of a Surface, a Node Region\/Geometry can also be used.<\/p>\n

It is irrelevant whether the crosslinks at the Primary and Secondary Surface are identical, but care must be taken that the finer crosslink is always assigned to the Secondary Surface.<\/p>\n

There are restrictions with regard to the loads, which are explained in more detail in the first example.<\/p>\n

Furthermore, it is possible to transfer the obtained stress and deformation state to a 360\u00b0 overall model in order to then apply non-cyclic symmetric external loads, such as bending (is content of a separate paper, see also *SYMMETRIC MODEL GENERATION, *SYMMETRIC RESULTS TRANSFER).<\/p>\n

The following two examples show how cyclic symmetry is applied and what advantages it has. The examples were created with Abaqus\/CAE. We will be happy to provide you with the CAE file.<\/p>\n<\/div>

<\/div>
<\/div><\/div><\/span>

Example1
\n<\/strong><\/h2><\/h2><\/span>
<\/div><\/div><\/div><\/div><\/div><\/div><\/div>

From a full model of a shaft to be clamped with an outer part, it follows that a 30\u00b0 cutout is cyclically symmetrical. It results in 12 cyclic symmetrical parts. For one partial model and one full model the calculation is built.<\/p>\n

The inner surface of the shaft (a) is coupled to a reference point on the axis of rotation via node coupling of the Kinematic type. This reference point is fixed via a boundary condition.<\/p>\n

By bracing the inner part (b) with the outer part (c) with a bolt force and the taper of the outer part in the area of the shaft, the inner part, outer part and shaft are pressed together. The step is defined as a Static, General with non-linear geometry.<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

Full model<\/p>\n<\/div>

<\/a><\/span><\/div><\/div>

30\u00b0 segment<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div><\/div><\/div><\/div><\/div>
<\/a><\/span><\/div><\/div><\/div><\/div>

Definition of the axis of symmetry
\nThese points must be defined as Reference Points beforehand.<\/p>\n

In case they are not part of a coupling, they appear in the DAT file with a warning that can be ignored (unused node).<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div><\/div><\/div><\/div><\/div>

While practically all loads (centrifugal force, temperature…) can be applied to the sector, this does NOT apply to non-symmetrical forces, moments and displacements.
\nIt basically applies:<\/strong>
\nThe deformation of the Secondary Surface follows the deformation of the Primary Surface with respect to the symmetry axis<\/strong>
\nValid forces, moments, displacements, torsions:
\nCF1, CM1,U1,UR1 : No
\nCF2,CM2,U2,UR2 : No
\nCF3,CM3,U3,UR3 : Yes<\/p>\n

The applied bolt force acts in the 3-direction.<\/p>\n

Forces and\/or torques must be divided in relation to the solid model<\/strong>
\nby the number of sectors ! <\/strong><\/p>\n

To determine the stiffnesses, the reaction forces\/moment of reaction must be<\/strong>
\nmultiplied by the number of sectors !<\/strong><\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div><\/div><\/div><\/div><\/div>
<\/div><\/div><\/div><\/div><\/div>

In post-processing, the sector can be expanded to a full 3D model in the ODB display options<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div><\/div><\/div><\/div><\/div>
<\/div>

The calculations of the model with cyclic symmetry and a full model are to be compared.<\/p>\n

C3D8I elements were predominantly used for the meshing (except for the screw). There is not quite a factor of 12 in the number of elements due to slight differences in meshing<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

1\/12 model \/ cyclic symmetry<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

Full model<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div><\/div><\/div><\/div><\/div>

The von Mises stresses differ only minimally.<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

1\/12 model \/ cyclic symmetry<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

Full model<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div>

The calculations were performed on a laptop (HP Z- Book, 4 cores, 32 Gb RAM with GPU support). There are differences in computing time and memory (CPU RAM) requirements with a factor of > 12. However, both models scale similarly.<\/p>\n<\/div>

<\/div><\/div><\/div><\/div><\/div>
<\/a><\/span><\/div><\/div>

1\/12 model \/ cyclic symmetry<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

Full model<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div>
<\/div><\/div><\/span>

Example 2: Modal analysis<\/h2><\/h2><\/span>
<\/div><\/div><\/div>
<\/div><\/div><\/div><\/div><\/div>
<\/a><\/span><\/div><\/div>

1\/12 model \/ cyclic symmetry<\/p>\n<\/div><\/div><\/div>

<\/a><\/span><\/div><\/div>

Full model<\/p>\n<\/div><\/div><\/div><\/div><\/div>

<\/div><\/div><\/div><\/div><\/div>

For the display of the eigenmodes, this setting must be selected in the ODB display options<\/p>\n<\/div>

<\/a><\/span><\/div><\/div>
<\/div><\/div><\/div><\/div><\/div>
<\/a><\/span><\/div><\/div>

1\/12 Model \/ Cyclic Symmetry (Left) and Full Model (Right)<\/p>\n<\/div>

<\/div><\/div><\/div><\/div><\/div>
<\/div><\/div><\/span>

Worth knowing<\/h2><\/h2><\/span>
<\/div><\/div><\/div>

If boundary conditions<\/strong> are on the secondary surface of the cyclic symmetry, a warning message is displayed. The boundary conditions are automatically disabled by Abaqus\/CAE, but they can also be deselected by the user.<\/p>\n

However, in the Example 1, Secondary Surface nodes are used in a node coupling, see figure below.<\/p>\n<\/div>

<\/a><\/span><\/div><\/div>
<\/div><\/div><\/div><\/div><\/div>
<\/div><\/div><\/div><\/div>

If nodes of a node coupling<\/strong> are located on the secondary surface of the cyclic symmetry, a warning message is issued. These nodes are automatically removed from the coupling by Abaqus\/CAE, but they can also be deselected by the user.<\/p>\n

Here: Boundary conditions on inner surface of shaft overlap with Secondary surface.<\/p>\n<\/div>

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