Re: ANSYS V13 Windows 32 Bit MAGNiTUDE
Elliott Davis
"An internal solution magnitude limit was exceeded. (Node Number 26789822, Body Unknown, DOF UX). Please check your environment for innaproriate loads of supports. You may select the offending object and/or geometry via RMB on this warning in the messages window. Please see the troubleshooting section of the Help System for more information."
I have looked at the Newton-Raphson residual forces and one washer has most of the residual forces but I am not sure whether this is a red herring and the internal magnitude limit is being exceeded elsewhere.
The upper panel shows a representative WSS Map from an aorta with a coarctation. (A) There is low magnitude oscillatory WSS in the downstream region and high unidirectional WSS in the upstream region. The lower images show representative confocal images (63x) from en face mounted aortas stained for either VCAM-1 (B and C) or superoxide (D and E). The images on the left (B and D) were taken from the upstream region while the images on the right (C and E) were taken from the downstream region. (To see this illustration in color the reader is referred to the web version of this article at www.liebertonline.com/ars).
Click Loads > Pressure to specify a traction. Select the right edge of the geometry and apply it in the details view window. The pressure's magnitude from the problem specification is -1e6 psi (pressure in ANSYS defaults to compression, and we need tension, hence the negative sign). Now that the forces have been set, we need to set up the solution before we solve.
Problem Description
# Material : The plate is made of steel with Modulus of elasticity E = 200 GPa, and Poisson's ratio = 0.25
# Unit : SI Units ONLY. It is important to convert pressure to "Pa" and all dimensions to "meters".
# Boundary Conditions : We will use symmetry conditions to solve this problem, by considering only the top right quarter of the plate. Therefore, the boundary conditions for the plate are symmetry conditions on the left and bottom parts of the plate.
# Loading : Uniform tensile Load with magnitude 1 MPa acting on both left and right sides of the plate (Since we're using symmetry, we will apply pressure to only the right side of the top right quarter of the plate) Because we are performing a linear analysis, a uniform load/area of 1 MPa is appropriate. Stresses, strains and displacements for any other magnitude of loading can be determined by simply re-scaling the results from this model.(eg. To obtain results for a 100MPa load, simply multiply results from this model by 100)
# Objectives :
1. To use symmetry conditions to determine magnitudes of maximum stress, minimum stress and their locations on the plate after the load is applied.
2. To model the plate using a default mesh (coarse mesh) and using mesh size control to increase element resolution (fine mesh). You will then determine how element resolution affects the maximum and minimum stresses.# Things to hand in :
1. Contour plot
2. Query of maximum stress
3. Query of minimum stress
4. Plot of stress xx and stress yy VS y along y=0
# Figure and Dimensions:
1. Specify Geometry
There are several ways to create the model geometry in ANSYS. For this problem, we will use two ways to create the specified object. The first method is to define keypoints then create area rectangles through these keypoints. The second method is to define key points and create lines. After we have the boarder of the object, we will then create an area.
However, in order to see their numbers when creating keypoints, we will need to turn on the keypoint numbers.
ANSYS UTILITY MENU -> PlotCtrls -> Numbering...
Temporal resolution in a spectrogram is fundamentally determined by the window size, equal to the FFT-length. In a simple plot of the spectrogram of a short signal, one pixel on the screen equals one window. If a high frequency resolution is wanted, which requires long windows, the spectrogram appears pixelated on the time axis. This can be smoothed by making windows overlap. 50% overlap gives twice the display resolution, 90% overlap 10 times the display resolution, which creates visually more appealing displays. When interpreting the spectrogram, this "smoothing" must be kept in mind, as the fundamental time resolution is still given by the FFT-size/window length and cannot be improved by overlapping. Windows are correlated, as explained in @WMXZ's answer.
If a Hann window is used, one can argue that 50% overlap is well justified, because no part of the signal contributes more to the spectrogram than others. In the individual Hann-window, the middle part is weighted with 100%, but the beginning and end are weighted 0%. However, the sum of a series of 50% overlapping Hann-windows equals 1 except for the first half and last half window, meaning that every part of the signal contributes equally. If larger overlap is used, the overlapping segments contribute with more than 100%, and less than 100% for smaller overlaps.Same argument can be used for overlapping windows in power spectrum estimates.
This symmetry a particularly useful feature of Hann windows, generally not true for other windows (Bartlett/triangular window is one exception), making Hann-windows a very good first choice for analysis.
Equally distributed time points are often used to animate linear static or transient analysis and in modal analysis. In nonlinear static or transient analysis, equally distributed time points might be used, with the warning that time points between results sets in the RST results file will be linearly interpolated, are not in equilibrium, and contain some error. In nonlinear work, users may prefer to generate animation frames at results sets only, particularly if a reasonable number of results sets were saved at substeps during the solution. Prior to generating animations, users may want to adjust displacement magnitude, with choices made from the drop-down list or entered manually. In nonlinear analysis, True Scale magnitude of 1.0 is often preferred, while in linear analysis, Auto-Scale is common.
User experience is that with larger models and requests for large numbers of animation frames, Workbench Mechanical does not always successfully generate a complete AVI animation file. Model size, large graphics windows, and many frames in the animation can affect this.
Hi - In addition to what Jim says - was it really the intention that the height of that edge is 2.05 units?
It is recommended that features are at least one order of magnitude larger than the file tolerance. With your file tolerance of 0.01, you are only half an order of magnitude away (as the remaining edge is only 0.05).
image738426 71.1 KB
-wim
What cache sizes of this magnitude have an opportunity to do is noticeably improve (1) effective memory bandwidth and (2) effective memory latency. Many HPC applications increase their performance partially or fully in-line with improvements to memory bandwidth and/or memory latency, so the potential impact to HPC customers of Milan-X processors is large. Examples of workloads that fall into these categories include:
In 1979 a new version of DYNA3D was released which was programmed for optimal performance on the CRAY-1 supercomputers. This new release contained improved sliding interface treatment which was an order of magnitude faster than the previous contact treatment. This version also eliminated structural and higher order solid elements of the first version, while including element-wise integration of the integral difference method developed in 1974.[4]
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