When you create a new view by copying an existing view, the list of active layers for that view is now properly dupli-cated. Previously, the layer list was missed, requiring you to recreate it in the new view.
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Documentation (Version 4.41)
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6.3.12 Create Material - Hyperelastic
When entering Hyperelastic material constants Di, be careful. They are translated directly for NASTRAN, but for ABAQUS the values written are 1 / Di.
6.10.11 View Select . . .
Two new postprocessing styles have been added to the View Select command. The new deformed style called Trace Plotting allows you to display "streamline" style lines as nodes deform. The new Vector Contour Style provides the display of contour-colored vectors at the centers of elements.
Deformed Trace Style
You can now produce a Trace Plot from a output contained in multiple Output Sets. This capability is especially valu-able for visualization of deformation in transient analyses which produce time dependent results. This new capability works much like MultiSet Animation, except that as the animation proceeds, a line or trace is left behind showing the location of one or more nodes. Through the Trace Locations option in the Deformed and Contour Data dialog box, you can choose to select all the nodes, a group of nodes, or a single node to use for the trace. A new Trace Style option has also been added to the View Options command. Here you can choose whether to display or label each location along the trace lines, and whether to display full length trace lines or to animate them with the model. When used in combination with the Skip Deformation option in View Select, you can independently control whether the model and/or the trace lines are animated.
Contour Vector Style
Elemental and Nodal Results can now be displayed as vectors in contour colors based on their magnitude. If you choose elemental output, the vectors will be shown at the centroids of the associated elements. Choosing nodal results causes vectors to be displayed at the nodes.
You choose the output to be displayed via the Contour Vectors option in the Deformed and Contour Data dialog box.
You can define the output in any of four different methods - Standard Vectors, Single Value, 2-D Components, or 3-D Components. Typically you will want to select a Standard Vector since these Output Vectors contain data which was already calculated based upon their components. Examples of these type of vectors include Total Translation or Rotation for Nodal Data, Plate Top Major Stress for 2-D Plate Elements, and Solid Major Principal Stress for 3-D Solid Elements. The direction and magnitude of these vectors are automatically calculated by FEMAP to generate the Vector Contour Plot.
If you want to display vectors other than standard, you can simply select the number of components of the vector (Single, 2-D, or 3-D). If you decide to display a single vector, you must also define the vector direction under the Dis-play Direction button. The standard FEMAP Vector Definition Dialog Box is disDis-played to enable you to define the direction of this 1-D plot. If you select 2-D components, and the two associated vectors for the X and Y components, the data will be displayed in the coordinate directions defined by the "Output Relative To" portion of the dialog box (discussed below). 3-D components works just like 2-D except that you must now choose three vectors. In either of these cases, the components must be chosen in a top-down fashion. That is, the first vector represents the x compo-nent, the second is the y compocompo-nent, and the third (if necessary) is the z component. By allowing you to select a Standard Vector, or any combination of 1-D, 2-D, or 3-D vectors, FEMAP can produce Elemental Centroidal plots for a wide variety of conditions and vectors.
FEMAP does not know nor keep track of the coordinate system where your output is defined. Therefore it is up to you to provide this information prior to making a vector plot. You can choose any one of five different methods, depending on how your results were defined by your analysis program. THIS IS EXTREMELY IMPORTANT ! IF YOU CHOOSE THE WRONG, OR INAPPROPRIATE METHOD, THE DISPLAY WILL BE WRONG. YOU MUST KNOW HOW THE DATA WAS DEFINED BY YOUR ANALYSIS PROGRAM BEFORE PROCEEDING.
Element Edge / Solid CSys or Nodal Output CSys
This method is used for output from planar elements if the X output direction is defined relative to the first element edge (the line connecting the first two nodes). It is used for Solid elements if output is defined in the solid property coordinate system. Use it for nodal output, if the results are in the Nodal output coordinate system. Be aware how-ever that for most standard three dimensional nodal output vectors (Displacements, Constraint Forces, Applied Loads, Velocities and Accelerations) FEMAP transforms output into global coordinates and this option is not appro-priate.
Element Midside Locations
This option is used for output from planar elements when the X output direction is defined as the vector that joins the midsides of the second and final (4th for a quad, 3rd for a triangle) edge.
Element Diagonal Bisector
This option is used for output from planar elements when the X output direction is defined as the vector that bisects the angle formed by the two element diagonals, in the quadrant that generally points along the first edge.
Element Material Direction
This option is used for elemental output that is defined in the material direction. For example along the rotated plies of a laminate.
CSys
This final method is available if your output is defined in some known coordinate system. You must also choose the appropriate coordinate system along with this option.
View Options - Contour Vector Style
A new Contour Vector Style option has been added to the View Options command as well. Here you can choose whether the length and/or color of the vectors will be adjusted based on their magnitude. You can also choose how the vectors are located and whether or not they have arrowheads. If you choose to center the vectors, they will either be centered at the node or element centroid, as appropriate. Otherwise, the start of the vector will be placed at that location. If you choose a Single Arrow style, the direction of the vector (toward the arrowhead) will imply whether the value is positive or negative. For Dual Arrow styles, outward pointing arrowheads are used for positive values, inward pointing arrowheads are used for negative values.
8.4 ANSYS Interfaces
Many new capabilities have been added to the ANSYS Interfaces for this release including support for Transient, Frequency Response, Buckling, Nonlinear Static and Nonlinear Transient Response analyses. The following docu-mentation is meant to supplement the information that is already in the FEMAP manual.
Revision
It is very important that you set this option correctly for the version of ANSYS that you will be using. There are signif-icant changes in commands and conventions between ANSYS Revision 4.4 and Revision 5.0. If you choose the incorrect version, your model will almost certainly fail to run. Revision 5 is now the default option. Furthermore, only Static and Modal Analysis are available for ANSYS Revision 4.4.
Commands for Automatic Solve
If you check this option, FEMAP will write additional commands to the end of your ANSYS file. These commands automatically perform the analysis when you load the file into ANSYS, or run the model in batch mode. This com-mand is automatically selected for Transient, Frequency, Buckling, and Nonlinear Transient analyses. Do not select this option if you are running a Static, Modal, or Nonlinear Static analysis and want to load the model into ANSYS,
and then review it in PREP7 before beginning your analysis.
Large Deformation Effects
For Nonlinear Analysis (both Static and Transient), you also have the option to choose Large Deformation Effects.
Simply click on this dialog box if you would like to include these effects. This selection will not appear if you did not select a Nonlinear Analysis Type.
Preparing for Static Analysis - Additional Information
You may also define multiple load and constraint sets for Nonlinear Static analysis, however, the first load set chosen must have active Nonlinear Analysis options. If Nonlinear Analysis options are not defined, an error will occur and FEMAP will not translate the load sets. If Nonlinear Analysis options are defined for the first load set, these options will be used for all following load sets since ANSYS does not allow modification of these options after entering the solution process.
Preparing for Transient and Nonlinear Transient Response Analyses
Preparing for these types of analyses is very similar to preparing for Static and Modal Analysis except only one load set and one constraint set may be chosen. A dialog box will appear to enable you to select the load case.
The load case selected must have the correct Dynamic Analysis Solution Option chosen to prevent translation errors.
If Dynamic Analysis options are turned Off, or a mismatch occurs between solution and analysis type (i.e. you chose Transient Analysis but the Dynamic Analysis Solution Option for the chosen load set is Direct or Modal Frequency), an error message will appear and the load set will not be written.
If the Analysis Type and the Dynamic Analysis option match, FEMAP will automatically determine whether to use a FULL (direct) or MODAL analysis method based upon the Dynamic Analysis Solution Option. If a direct method is active in the Dynamic Analysis Solution option, the Constraint Set dialog box appears and you can select the appro-priate constraint set, after which the translation is completed. If a modal method is active, FEMAP will first write com-mands for the Modal solution and then the transient solution. The ANSYS Dynamic Analysis Options (see Preparing for Modal Analysis) dialog box appears to allow you to select information related to the initial Modal Analysis.
Translating for Nonlinear Transient analysis is identical to Transient analysis except that Modal Transient is not avail-able, Nonlinear Analysis options must be active, and you can choose to activate Large Deformation Effects. If a Modal Transient Solution Method is selected, or Nonlinear Analysis options are not active, an error message appears and the load set is not written.
Preparing for Frequency/Harmonic Response Analysis
Preparing for Frequency analysis is identical to transient except for an additional dialog box which appears at the end of translation. This dialog box is identical to the ANSYS Dynamic Analysis Options dialog box and is used to select the number of frequencies and the frequency range to be analyzed. If a Modal Frequency Solution Method is cho-sen, this dialog box will appear twice. The first time you must choose the options for the initial Modal Analysis, while the second time it appears you must choose the frequency range of interest. As shown below, only Number of quencues, MIN Frequency, Max Frequency, and whther to calculate Element results will be available for the Fre-quency protion of this analsyis. All other options are grayed.
Preparing for Buckling Analysis
Buckling analysis simply requires the writing of a Static Solution followed by a Buckling Solution. Only one load set and one constraint set may be chosen for Buckling Analysis. The only other inputs required are the number of modes to be extracted and whether Elemental Results should be calculated. These are input in the standard ANSYS Dynamic Analysis Options dialog box.
Notes on Dynamic Analyses
It is important to review limitations on Transient and Frequency Response loading conditions in ANSYS. Loads on the same node or elemental face must have the same time history (Transient) or same phase (Frequency). If they do not, FEMAP will write the loading conditions assuming the last time history/phase, and you will most likely get results for a different loading condition than desired.
Also, with regard to damping, you can define alpha and beta damping for frequency analysis by defining the Overall Structural Damping Coefficient (G). FEMAP will automatically compute alpha and beta. If only one frequency is defined for the analysis, FEMAP assumes alpha is 0 and computes beta from 2*G/wi where wi is the frequency. If a range of frequencies are specified, FEMAP will compute alpha and beta based on the equation
G = alpha/(2*wi) + beta*wi/2
by assuming G is constant over the frequency range. Two simultaneous equations are produced at the two frequen-cies which define the range.
For damping in transient analysis, alpha is assumed to be zero and beta is set equal to the G divided by the Fre-quency for System Damping (W3). Alpha and Beta damping are not available for Nonlinear Transient Analysis. For more information concerning damping in ANSYS, please review the ANSYS Procedures Manual.