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• Interactive mode allows you to interact “live” with ANSYS, reviewing
each operation as you go.
• Of the three main phases of an analysis — preprocessing, solution,
postprocessing — the preprocessing and postprocessing phases are
best suited for interactive mode.
• We will mainly cover interactive mode in this course.
Interactive Mode
Overview
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Interactive Mode
Starting ANSYS
Launcher –
• Allows you to start ANSYS and other ANSYS utilities by pressing buttons on a menu.
• On Windows systems, press:
Start > Programs > ANSYS 7.0
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• Pressing the Interactive button on the launcher brings up a dialog
box containing start-up options:
Interactive Mode
…Starting ANSYS
Windows systems
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Output
Window
Icon Toolbar Menu
Abbreviation Toolbar Menu
Utility Menu
Graphics Area
Main Menu
Input Line
The GUI
Layout
Raise/Hidden Icon
Current Settings User Prompt Info
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• Tree structure format.
• Contains the main functions required for an
analysis.
• Use scroll bar to gain access to long tree
structures.
The GUI
Main Menu
scroll bar
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The GUI
…Main Menu
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Main Menu
UIDL Behavior
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Main Menu
Filtered Branches
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• Jobname definition when using Open ANSYS File Icon:
– the ANSYS jobname will be changed to the prefix of the database file being resumed.
Open ANSYS File
When opening the “blades.db” database
(using the Open ANSYS File Icon), the
jobname will be changed to “blades”.
The Open ANSYS File Icon can be used to open either ANSYS
Database or ANSYS Command file types
The GUI
….Icon Toolbar Menu
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• The Preferences dialog (Main Menu >
Preferences) allows you to filter out
menu choices that are not applicable to
the current analysis.
• For example, if you are doing a thermal
analysis, you can choose to filter out
other disciplines, thereby reducing the
number of menu items available in the
GUI:
– Only thermal element types will be shown
in the element type selection dialog.
– Only thermal loads will be shown.
– Etc.
The GUI
Preferences
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• The PlotCtrls menu is used to control how
the plot is displayed:
– plot orientation
– zoom
– colors
– symbols
– annotation
– animation
– etc.
• Among these, changing the plot
orientation (/VIEW) and zooming are the
most commonly used functions.
Interactive Mode
…Graphics and Picking
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• The default view for a model is the front view:
looking down the +Z axis of the model.
• To change it, use dynamic mode — a way to
orient the plot dynamically using the Control
key and mouse buttons.
– Ctrl + Left mouse button pans the model.
– Ctrl + Middle mouse button:
zooms the model
spins the model (about screen Z)
– Ctrl + Right mouse button rotates the model:
about screen X
about screen Y
Note, the Shift-Right button on a two-button
mouse is equivalent to the Middle mouse
button on a three-button mouse.
P
Z R
Ctrl
Interactive Mode
…Graphics and Picking
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• If you don’t want to hold down the
Control key, you can use the Dynamic
Mode setting in the Pan-Zoom-Rotate
dialog box.
– The same mouse button assignments
apply.
– On 3-D graphics devices, you can also
dynamically orient the light source.
Useful for different light source shading
effects.
Interactive Mode
…Graphics and Picking
When using 3-D driver
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Picking
• Picking allows you to identify model entities
or locations by clicking in the Graphics
Window.
• A picking operation typically involves the
use of the mouse and a picker menu. It is
indicated by a + sign on the menu.
• For example, you can create keypoints by
picking locations in the Graphics Window
and then pressing OK in the picker.
Interactive Mode
…Graphics and Picking
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• The term ANSYS database refers to the data ANSYS maintains in
memory as you build, solve, and postprocess your model.
• The database stores both your input data and ANSYS results data:
– Input data -- information you must enter, such as model dimensions,
material properties, and load data.
– Results data -- quantities that ANSYS calculates, such as
displacements, stresses, strains, and reaction forces.
Interactive Mode
The Database and Files
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Save and Resume
• Since the database is stored in the computer’s memory (RAM), it
is good practice to save it to disk frequently so that you can
restore the information in the event of a computer crash or power
failure.
• The SAVE operation copies the database from memory to a file
called the database file (or db file for short).
– The easiest way to do a save is to click on Toolbar > SAVE_DB
– Or use:
• Utility Menu > File > Save as Jobname.db
• Utility Menu > File > Save as…
• SAVE command
Chapter 3 - Interactive Mode
…The Database and Files
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• To restore the database from the db file back into memory, use the
RESUME operation.
– Toolbar > RESUME_DB
– Or use:
• Utility Menu > File > Resume Jobname.db
• Utility Menu > File > Resume from…
• RESUME command
• The default file name for SAVE and RESUME is jobname.db, but
you can choose a different name by using the “Save as” or
“Resume from” functions.
Chapter 3 - Interactive Mode
…The Database and Files
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Clearing the Database
• The Clear Database operation allows
you to “zero out” the database and
start fresh. It is similar to exiting and
re-entering ANSYS.
– Utility Menu > File > Clear & Start New
– Or use the /CLEAR command.
Chapter 3 - Interactive Mode
…The Database and Files
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• Typical files:
jobname.log: Log file, ASCII.
• Contains a log of every command issued during the session.
• If you start a second session with the same jobname in the same
working directory, ANSYS will append to the previous log file (with
a time stamp).
jobname.err: Error file, ASCII.
• Contains all errors and warnings encountered during the session.
ANSYS will also append to an existing error file.
jobname.db, .dbb: Database file, binary.
• Compatible across all supported platforms.
jobname.rst, .rth, .rmg, .rfl: Results files, binary.
• Contains results data calculated by ANSYS during solution.
• Compatible across all supported platforms.
Chapter 3 - Interactive Mode
…The Database and Files
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File Management Tips
• Run each analysis project in a separate working directory.
• Use different jobnames to differentiate various analysis runs.
• You should keep the following files after any ANSYS analysis:
– log file ( .log)
– database file ( .db)
– results files (.rst, .rth, …)
– load step files, if any (.s01, .s02, ...)
– physics files (.ph1, .ph2, ...)
• Use /FDELETE or Utility Menu > File > ANSYS File Options to
automatically delete files no longer needed by ANSYS during that
session.
Chapter 3 - Interactive Mode
…The Database and Files
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• Three ways to exit ANSYS:
– Toolbar > QUIT
– Utility Menu > File > Exit
– Use the /EXIT command in the Input Window
Chapter 3 - Interactive Mode
Exiting ANSYS
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Every analysis involves four main steps:
• Preliminary Decisions
– Which analysis type?
– What to model?
– Which element type?
• Preprocessing
– Define Material
– Create or import the model geometry
– Mesh the geometry
• Solution
– Apply loads
– Solve
• Postprocessing
– Review results
– Check the validity of the solution
Preprocessing
Solution
Postprocessing
Preliminary
Decisions
Chapter 4 - General Analysis Procedure
…Overview
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Chapter 4 - A. Preliminary Decisions
Which analysis type?
• The analysis type usually belongs to one of the following
disciplines:
Structural Motion of solid bodies, pressure on solid bodies, or
contact of solid bodies
Thermal Applied heat, high temperatures, or changes in
temperature
Electromagnetic Devices subjected to electric currents (AC or DC),
electromagnetic waves, and voltage or charge
excitation
Fluid Motion of gases/fluids, or contained gases/fluids
Coupled-Field Combinations of any of the above
•The appropriate analysis type for this model is a structural analysis!
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Chapter 4 - A. Preliminary Decisions
…What to model?
• What should be used to model the geometry of the spherical tank?
– Axisymmetry since the loading, material, and the boundary
conditions are symmetric. This type of model would provide the
most simplified model.
– Rotational symmetry since the loading, material, and the
boundary conditions are symmetric. Advantage over
axisymmetry: offers some results away from applied boundary
conditions.
– Full 3D model is an option, but would not be an efficient choice
compared to the axisymmetric and quarter symmetry models. If
model results are significantly influenced by symmetric
boundary conditions, this may be the only option.
An axisymmetric and a one-quarter symmetry (i.e. rotational
symmetry) model will be analyzed for this model!
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Chapter 4 - A. Preliminary Decisions
…Which Element Type?
• What element type should be used for the model of the spherical
tank?
– Axisymmetric model:
• Axisymmetric since 2-D section can be revolved to created 3D
geometry.
• Linear due to small displacement assumption.
– PLANE42 with KEYOPT(3) = 1
– Rotational symmetry model:
• Shell since radius/thickness ratio > 10
• Linear due to small displacement assumption.
• membrane stiffness only option since “membrane stresses” are
required.
– SHELL63 with KEYOPT(1) = 1
• Since the meshing of this geometry will create SHELL63 elements
with shape warnings, a mid-side noded equation of the SHELL63 was
used:
– SHELL93 with KEYOPT(1) = 1
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• A typical solid model is defined by volumes, areas, lines, and
keypoints.
– Volumes are bounded by areas. They represent solid objects.
– Areas are bounded by lines. They represent faces of solid objects, or
planar or shell objects.
– Lines are bounded by keypoints. They represent edges of objects.
– Keypoints are locations in 3-D space. They represent vertices of
objects.
Volumes Areas Lines & Keypoints
Chapter 4 - B. Preprocessing
…Create the Solid Model
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• Meshing is the process used to “fill” the solid model with nodes
and elements, i.e, to create the FEA model.
– Remember, you need nodes and elements for the finite element
solution, not just the solid model. The solid model does NOT
participate in the finite element solution.
Solid model FEA model
meshing
Chapter 4 - B. Preprocessing
Create the FEA Model
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Chapter 4 - B. Preprocessing
Define Material
Material Properties
• Every analysis requires some material property input: Young’s
modulus EX for structural elements, thermal conductivity KXX for
thermal elements, etc.
• There are two ways to define material properties:
– Material library
– Individual properties
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• There are five categories of loads:
DOF Constraints Specified DOF values, such as displacements
in a stress analysis or temperatures in a
thermal analysis.
Concentrated Loads Point loads, such as forces or heat flow rates.
Surface Loads Loads distributed over a surface, such as
pressures or convections.
Body Loads Volumetric or field loads, such as temperatures
(causing thermal expansion) or internal heat
generation.
Inertia Loads Loads due to structural mass or inertia, such
as gravity and rotational velocity.
Chapter 4 – C. Solution
Define Loads
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• Postprocessing is the final step in the finite element analysis
process.
• It is imperative that you interpret your results relative to the
assumptions made during model creation and solution.
• You may be required to make design decisions based on the
results, so it is a good idea not only to review the results carefully,
but also to check the validity of the solution.
• ANSYS has two postprocessors:
– POST1, the General Postprocessor, to review a single set of results
over the entire model.
– POST26, the Time-History Postprocessor, to review results at selected
points in the model over time. Mainly used for transient and nonlinear
analyses. (Not discussed in this course.)
Chapter 4 - D. Postprocessing
Review Results
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Details
• Small details that are unimportant to the analysis should not be
included in the analysis model. You can suppress such features
before sending a model to ANSYS from a CAD system.
• For some structures, however, "small" details such as fillets or
holes can be locations of maximum stress and might be quite
important, depending on your analysis objectives.
Chapter 5 – A. What to Model
…What to model?
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Symmetry
• Many structures are symmetric in some form and allow only a
representative portion or cross-section to be modeled.
• The main advantages of using a symmetric model are:
– It is generally easier to create the model.
– It allows you to make a finer, more detailed model and thereby obtain
better results than would have been possible with the full model.
Chapter 5 – A. What to Model
…What to model?
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• To take advantage of symmetry, all of the following must be
symmetric:
– Geometry
– Material properties
– Loading conditions
• There are different types of symmetry:
– Axisymmetry
– Rotational
– Planar or reflective
– Repetitive or translational
Chapter 5 – A. What to Model
…What to model?
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Axisymmetry
• Symmetry about a central axis, such as in light bulbs, straight
pipes, cones, circular plates, and domes.
• Plane of symmetry is the cross-section anywhere around the
structure. Thus you are using a single 2-D “slice” to represent
360° — a real savings in model size!
• Loading is also assumed to be
axisymmetric in most cases. However,
if it is not, and if the analysis is linear,
the loads can be separated into
harmonic components for independent
solutions that can be superimposed.
Chapter 5 – A. What to Model
…What to model?
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Rotational symmetry
• Repeated segments arranged about a central axis, such as in
turbine rotors.
• Only one segment of the structure needs to be modeled.
• Loading is also assumed to be symmetric about the axis.
Chapter 5 – A. What to Model
…What to model?
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This model illustrates
both reflective and
rotational symmetry
Planar or reflective symmetry
• One half of the structure is a mirror image of the other half. The
mirror is the plane of symmetry.
• Loading may be symmetric or anti-symmetric about the plane of
symmetry.
Chapter 5 – A. What to Model
…What to model?
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This model illustrates both repetitive and reflective symmetry.
Repetitive or translational symmetry
• Repeated segments arranged along a straight line, such as a long
pipe with evenly spaced cooling fins.
• Loading is also assumed to be “repeated” along the length of the
model.
Chapter 5 – A. What to Model
…What to model?
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• In some cases, only a few minor details will disrupt a structure's
symmetry. You may be able to ignore such details (or treat them
as being symmetric) in order to gain the benefits of using a
smaller model. How much accuracy is lost as the result of such a
compromise might be difficult to estimate.
Chapter 5 – A. What to Model
…What to model?
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• Solid Modeling can be defined as the process of
creating solid models.
• Definitions:
– A solid model is defined by volumes, areas, lines,
and keypoints.
– Volumes are bounded by areas, areas by lines, and
lines by keypoints.
– Hierarchy of entities from low to high:
keypoints < lines < areas < volumes
– You cannot delete an entity if a higher-order entity
is attached to it.
• Also, a model with just areas and below, such as
a shell or 2-D plane model, is still considered a
solid model in ANSYS terminology.
Volumes
Areas
Lines &
Keypoints
Keypoints
Lines
Areas
Volumes
Chapter 5 – C. ANSYS Native Commands
Definitions
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Chapter 6 – Creating the Finite Element Model
Overview
• The purpose of this chapter is to discuss the meshing element
attributes, various means to create a mesh in ANSYS, and finally
how to import one’s finite element model directly into ANSYS.
Recall, ANSYS does not use the solid model in the solution of the
model, rather it needs to use finite elements.
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• Meshing is the process used to “fill” the solid model with nodes
and elements, i.e, to create the FEA model.
– Remember, you need nodes and elements for the finite element
solution, not just the solid model. The solid model does NOT
participate in the finite element solution.
Solid model FEA model
meshing
Chapter 6 – Creating the Finite Element Model
…Overview
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• There are three steps to meshing:
– Define element attributes
– Specify mesh controls
– Generate the mesh
• Element attributes are characteristics of the finite element model
that you must establish prior to meshing. They include:
– Element types
– Real constants
– Material properties
Chapter 6 – Creating the Finite Element Model
Element Attributes
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Element Type
• The element type is an important choice that determines the
following element characteristics:
– Degree of Freedom (DOF) set. A thermal element type, for example,
has one dof: TEMP, whereas a structural element type may have up to
six dof: UX, UY, UZ, ROTX, ROTY, ROTZ.
– Element shape -- brick, tetrahedron, quadrilateral, triangle, etc.
– Dimensionality -- 2-D (X-Y plane only), or 3-D.
– Assumed displacement shape -- linear vs. quadratic.
• ANSYS has a “library” of over 150 element types from which you
can choose. Details on how to choose the “correct” element type
will be presented later. For now, let’s see how to define an
element type.
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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Element category
• ANSYS offers many different categories of elements. Some of the
commonly used ones are:
– Line elements
– Shells
– 2-D solids
– 3-D solids
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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• Line elements:
– Beam elements are used to model bolts, tubular members, C-sections,
angle irons, or any long, slender members where only membrane and
bending stresses are needed.
– Spar elements are used to model springs, bolts, preloaded bolts, and
truss members.
– Spring elements are used to model springs, bolts, or long slender
parts, or to replace complex parts by an equivalent stiffness.
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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• Shell elements:
– Used to model thin panels or curved surfaces.
– The definition of “thin” depends on the application, but as a general
guideline, the major dimensions of the shell structure (panel) should
be at least 10 times its thickness.
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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• 2-D Solid elements:
– Used to model a cross-section of solid objects.
– Must be modeled in the global Cartesian X-Y plane.
– All loads are in the X-Y plane, and the response (displacements) are
also in the X-Y plane.
– Element behavior may be one of the following:
• plane stress
• plane strain
• generalized plain strain
• axisymmetric
• axisymmetric harmonic
Y
X Z
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• Plane stress assumes zero stress in
the Z direction.
– Valid for components in which the Z
dimension is smaller than the X and Y
dimensions.
– Z-strain is non-zero.
– Optional thickness (Z direction)
allowed.
– Used for structures such as flat plates
subjected to in-plane loading, or thin
disks under pressure or centrifugal
loading.
Y
X Z
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• Plane strain assumes zero strain in the Z
direction.
– Valid for components in which the Z dimension is
much larger than the X and Y dimensions.
– Z-stress is non-zero.
– Used for long, constant cross-section structures
such as structural beams.
Y X
Z
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Chapter 6 – Creating the Finite Element Model
…Element Attributes
• Generalized Plane Strain assumes a finite deformation domain
length in the Z direction, as opposed to the infinite value assumed
for standard plane strain.
– Gives more practical results for deformation problems where the Z-
direction dimension is not long enough.
– Gives users a more efficient way to simulate certain 3-D deformations
using 2-D element options.
– Option is a feature developed for PLANE182 and PLANE183.
– The deformation domain or structure
is formed by extruding a plane area
along a curve with a constant curvature.
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• Axisymmetry assumes that the 3-D model and its
loading can be generated by revolving a 2-D
section 360° about the Y axis.
– Axis of symmetry must coincide with the global Y
axis.
– Negative X coordinates are not permitted.
– Y direction is axial, X direction is radial, and Z
direction is circumferential (hoop) direction.
– Hoop displacement is zero; hoop strains and
stresses are usually very significant.
– Used for pressure vessels, straight pipes, shafts,
etc.
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…Element Attributes
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• Axisymmetric harmonic is a special case of axisymmetry where
the loads can be non-axisymmetric.
– The non-axisymmetric loading is decomposed into Fourier series
components, applied and solved separately, and then combined later.
No approximation is introduced by this simplification!
– Used for non-axisymmetric loads such as torque on a shaft.
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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• 3-D Solid elements:
– Used for structures which, because of geometry, materials, loading, or
detail of required results, cannot be modeled with simpler elements.
– Also used when the model geometry is transferred from a 3-D CAD
system, and a large amount of time and effort is required to convert it
to a 2-D or shell form.
Chapter 6 – Creating the Finite Element Model
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• To define an element type:
– Main Menu > Preprocessor >
Element Type > Add/Edit/Delete
• [Add] to add new element type
• Choose the desired type
(such as SOLID92) and press
OK
• [Options] to specify additional
element options
– Or use the ET command:
• et,1,solid92
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• Notes:
– Setting preferences to the desired discipline (Main Menu > Preferences)
will show only the element types valid for that discipline.
– You should define the element type early in the preprocessing phase
because many of the menu choices in the GUI are filtered out based
on the current DOF set. For example, if you choose a structural
element type, thermal load choices will not be not shown at all.
Chapter 6 – Creating the Finite Element Model
…Element Attributes
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Real Constants
• Real constants are used for geometric properties that cannot be
completely defined by the element’s geometry. For example:
– A beam element is defined by a line joining two nodes. This defines
only the length of the beam. To specify the beam’s cross-sectional
properties, such as the area and moment of inertia, you need to use
real constants.
– A shell element is defined by a quadrilateral or triangular area. This
defines only the surface area of the shell. To specify the shell
thickness, you need to use real constants.
– Most 3-D solid elements do not require a real constant since the
element geometry is fully defined by its nodes.
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• To define real constants:
– Main Menu > Preprocessor > Real
Constants
• [Add] to add a new real constant
set.
• If multiple element types have
been defined, choose the element
type for which you are specifying
real constants.
• Then enter the real constant
values.
– Or use the R family of commands.
• Different element types require
different real constants. Check the
Elements Manual, available on-line,
for details.
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Material Properties
• Every analysis requires some material property input: Young’s
modulus EX for structural elements, thermal conductivity KXX for
thermal elements, etc.
• Refer to Chapter 7 for details on the two ways to define material
properties.
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• Most FEA models have multiple attributes. For example, the silo shown
here has two element types, three real constant sets, and two materials.
MAT 1 = concrete
MAT 2 = steel
REAL 1 = 3/8” thickness
REAL 2 = beam properties
REAL 3 = 1/8” thickness
TYPE 1 = shell
TYPE 2 = beam
Chapter 6 – Creating the Finite Element Model
Multiple Element Attributes
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• Whenever you have multiple TYPEs, REALs and MATs, you need
to make sure that each element is assigned the proper attributes.
There are three ways to do this:
– Assign attributes to the solid model entities before meshing
– Activate a “global” setting of MAT, TYPE, and REAL before meshing
– Modify element attributes after meshing
• If no assignments are made, ANSYS uses default settings of
MAT=1, TYPE=1, and REAL=1 for all elements in the model. Note,
the current active TYPE, REAL, and MAT dictates mesh operation.
Chapter 6 – Creating the Finite Element Model
…Multiple Element Attributes
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Modifying Element Attributes
1. Define all necessary element types, materials, and real constant sets.
2. Activate the desired combination of TYPE, REAL, and MAT settings:
– Main Menu > Preprocessor > Meshing > Mesh Attributes > Default Attribs
– Or use the TYPE, REAL, and MAT commands
3. Modify the attributes of only those elements to which the above settings apply:
– Issue EMODIF,PICK or choose Main Menu > Preprocessor > Modeling > Move/Modify > Elements > Modify Attrib
– Then pick the desired elements
4. In the subsequent dialog box, set attributes to “All to current.”
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• Examples of different SmartSize
levels are shown here for a
tetrahedron mesh.
• Advanced SmartSize controls, such
as mesh expansion and transition
factors, are available on the SMRT
command or:
Main Menu > Preprocessor > Meshing >
Size Cntrls > SmartSize > Adv Opts
• You can turn off SmartSizing using
the MeshTool or by issuing smrt,off.
Chapter 6 – Creating the Finite Element Model
…Controlling Mesh Density
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• There are two main meshing methods: free and
mapped.
• Free Mesh
– Has no element shape restrictions.
– The mesh does not follow any pattern.
– Suitable for complex shaped areas and volumes.
• Mapped Mesh
– Restricts element shapes to quadrilaterals for areas
and hexahedra (bricks) for volumes.
– Typically has a regular pattern with obvious rows of
elements.
– Suitable only for “regular” areas and volumes such as
rectangles and bricks.
Chapter 6 – Creating the Finite Element Model
Mapped Meshing
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• For volume meshing, we have only seen two
options so far:
– Free meshing, which creates an all-tet mesh. This
is easy to achieve but may not be desirable in
some cases because of the large number of
elements and total DOF created.
– Mapped meshing, which creates an all-hex mesh.
This is desirable but usually very difficult to
achieve.
• Hex-to-tet meshing provides a third option that
is the “best of both worlds.” It allows you to
have a combination of hex and tet meshes
without compromising the integrity of the mesh.
Chapter 6 – Creating the Finite Element Model
Hex-to-Tet Meshing
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• This option works by creating pyramid-shaped elements in the transition
region between hex and tet regions.
– Requires the hex mesh to be available (or at least a quad mesh at the shared
area).
– The mesher first creates all tets, then combines and rearranges the tet elements
in the transition region to form pyramids.
– Available only for element types that support both pyramid and tet shapes, e.g:
• Structural SOLID95, 186, VISCO89
• Thermal SOLID90
• Multiphysics SOLID62, 117, 122
SOLID95
– Results are good even in the transition
region. Element faces are compatible even
when transitioning from a linear hex
element to a quadratic tet element.
Chapter 6 – Creating the Finite Element Model
…Hex-to-Tet Meshing
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– Hex-to-tet meshing is valid for both quadratic-to-quadratic and linear-to-
quadratic transitions. Element type must support a 9-node pyramid for the latter.
8-Node Hex 9-Node Pyramid 10-Node Tet
Hex Mesh Transition Layer Tet Mesh
Quadratic
to
Quadratic
Linear
to
Quadratic
10-Node Tet 13-Node Pyramid 20-Node Hex
Chapter 6 – Creating the Finite Element Model
…Hex-to-Tet Meshing
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Specifying Individual Material Properties
• Instead of choosing a material name, this method involves directly
specifying the required properties through the Material Model GUI.
• To specify individual
properties:
– Main Menu > Preprocessor >
Material Props > Material Models
• Double-click on the
appropriate property to be
defined.
Chapter 7 – Defining the Material
Material Model GUI
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• Work through the tree
structure to the material
type to be defined.
• Then enter the individual
property values.
• Or use the MP command. – mp,ex,1,30e6
– mp,prxy,1,.3
Chapter 7 – Defining the Material
…Material Model GUI
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• Add temperature dependent
properties
• Graph properties vs. temperature
Chapter 7 – Defining the Material
…Material Model GUI
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• The solution step is where we apply loads on the object and let
the solver calculate the finite element solution.
• Loads are available both in the Solution and Preprocessor menus.
Chapter 8 - Loading
Overview
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• There are five categories of loads:
DOF Constraints Specified DOF values, such as displacements
in a stress analysis or temperatures in a
thermal analysis.
Concentrated Loads Point loads, such as forces or heat flow rates.
Surface Loads Loads distributed over a surface, such as
pressures or convections.
Body Loads Volumetric or field loads, such as temperatures
(causing thermal expansion) or internal heat
generation.
Inertia Loads Loads due to structural mass or inertia, such
as gravity and rotational velocity.
Chapter 8 - Loading
Define Loads
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• You can apply loads either on the solid model or directly on the
FEA model (nodes and elements).
– Solid model loads are easier to apply because there are fewer entities
to pick.
– Moreover, solid model loads are independent of the mesh. You don’t
need to reapply the loads if you change the mesh.
Constraints
at nodes
FEA model
Pressures on element faces
Force at node
Constraint
on line
Solid model
Pressure on line
Force at keypoint
Chapter 8 - Loading
…Define Loads
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Chapter 8 - Loading
Nodal Coordinate System
• All forces, displacements, and other direction-dependent nodal
quantities are interpreted in the nodal coordinate system.
– Input quantities:
• Forces and moments FX, FY, FZ, MX, MY, MZ
• Displacement constraints UX, UY, UZ, ROTX, ROTY, ROTZ
• Coupling and constraint equations
• Etc.
– Output quantities:
• Calculated displacements UX, UY, UZ, ROTX, ROTY, ROTZ
• Reaction forces FX, FY, FZ, MX, MY, MZ
• Etc.
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• If necessary, you can rotate
the nodal CS to a different
orientation.
For example:
– To simulate an inclined roller
support.
– To apply radial forces.
– To apply radial constraints
(perhaps to simulate a rigid,
press-fitted pin).
Chapter 8 - Loading
...Nodal Coordinate System
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• To “rotate nodes,” use this four-step procedure:
1. Select the desired nodes.
2. Activate the coordinate system (or create a local CS)
into which you want to rotate the nodes, e.g, CSYS,1.
3. Choose Main Menu > Preprocessor > Modeling >
Move/Modify > Rotate Node CS > To Active CS, then press
[Pick All] in the picker.
Or issue NROTAT,ALL.
4. Reactivate all nodes.
• Note: When you apply symmetry on anti-symmetry
boundary conditions, ANSYS automatically rotates all
nodes on that boundary.
Chapter 8 - Loading
...Nodal Coordinate System
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• Displacement constraints are also used to enforce symmetry or
antisymmetry boundary conditions.
– Symmetry BC: Out-of-plane displacements and in-plane rotations are
fixed.
– Antisymmetry BC: In-plane displacements and out-of-plane rotations
are fixed.
Antisymmetry Boundary
UY=UZ=0
ROTX=0
Symmetry Boundary
UX=0
ROTY=ROTZ=0
Y
X
Loading & Solution
…Displacement Constraints
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• A force is a concentrated load (or “point
load”) that you can apply at a node or
keypoint.
• Point loads such as forces are
appropriate for line element models
such as beams, spars, and springs.
In solid and shell models, point loads
usually cause a stress singularity, but
are acceptable if you ignore stresses in
the vicinity. Remember, you can use
select logic to “ignore” the elements in
the vicinity of the point load.
Loading & Solution
Concentrated Forces
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• In the 2-D solid model shown at bottom left, notice that maximum
stress SMAX (24,652) is reported at the location of the force.
When the nodes and elements in the vicinity of the force are
unselected, SMAX (12,279) moves to the bottom corner, which is
another singularity due to the displacement constraint at the
corner.
Loading & Solution
Concentrated Forces
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By unselecting nodes and elements near the bottom corner, you
get the expected stress distribution with SMAX (7,895) near the
top hole.
Loading & Solution
…Concentrated Forces
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Note that for axisymmetric models:
• Input values of forces are based on the full 360°.
• Output values (reaction forces) are also based on the full 360°.
• For example, suppose a cylindrical shell of radius r has an edge load of P
lb/in. To apply this load on a 2-D axisymmetric shell model (SHELL51
elements, for example), you would specify a force of 2prP.
r
P lb/in 2prP lb
Loading & Solution
…Concentrated Forces
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Verifying applied loads
• Plot them by activating load symbols:
– Utility Menu > PlotCtrls > Symbols
– Commands -- /PBC, /PSF, /PBF
• Or list them:
– Utility Menu > List > Loads >
Loading & Solution
Verifying Loads
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• Element type
• The table below shows commonly used structural element types.
• The nodal DOF’s may include: UX, UY, UZ, ROTX, ROTY, and ROTZ.
2-D Solid 3-D Solid 3-D Shell Line Elements
Linear PLANE42 SOLID45 SOLID185
SHELL63 SHELL181
BEAM3
BEAM4
BEAM188
Quadratic PLANE82 PLANE2
SOLID95 SOLID92 SOLID186
SHELL93 BEAM189
Commonly used structural element types
Chapter 10 – A. Preprocessing
Meshing
• Material properties
– Minimum requirement is Young’s Modulus, EX. If Poisson’s Ratio is
not entered a default of 0.3 will be assumed.
– Setting preferences to “Structural” limits the Material Model GUI to
display only structural properties.
• Real constants and Section properties
– Primarily needed for shell and line elements.
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• Structural loading conditions can be:
DOF Constraints Regions of the model where displacements are known.
Concentrated Forces External forces that can be simplified as a point load.
Pressures Surfaces where forces on an area are known.
Uniform Temperature Temperatures applied as a body force used with a reference
temperature to predict thermal strains.
Gravity Accelerations applied as inertia boundary conditions
Chapter 10 – B. Solution
Define Loads
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Displacement Constraints
• Used to specify where the model is fixed (zero displacement locations).
• Can also be non-zero, to simulate a known deflection.
• To apply displacement constraints :
– Main Menu > Solution > Define Loads > Apply > Structural > Displacement
• Choose where you want to apply the constraint.
• Pick the desired entities in the graphics window.
• Then choose the constraint direction. Value defaults to zero.
– Or use the D family of commands: DK, DL, DA, D.
• Question: In which coordinate system are UX, UY, and UZ interpreted?
Chapter 10 – B. Solution
Displacement Constraints
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• To apply a force, the following information is needed:
– node or keypoint number (which you can identify by picking)
– force magnitude (which should be consistent with the system of units
you are using)
– direction of the force — FX, FY, or FZ
Use:
– Main Menu > Solution > Define Loads > Apply > Structural > Force/Moment
– Or the commands FK or F
• Question: In which coordinate system are FX, FY, and FZ
interpreted?
Chapter 10 – B. Solution
Concentrated Forces
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Pressures
• To apply a pressure:
– Main Menu > Solution > Define Loads > Apply
Structural > Pressure
• Choose where you want to apply the
pressure -- usually on lines for 2-D
models, on areas for 3-D models.
• Pick the desired entities in the graphics
window.
• Then enter the pressure value.
A positive value indicates a
compressive pressure (acting towards
the centroid of the element).
– Or use the SF family of commands: SFL,
SFA, SFE, SF.
Chapter 10 – B. Solution
Pressure
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• For a 2-D model, where pressures
are usually applied on a line, you
can specify a tapered pressure
by entering a value for both the I
and J ends of the line.
• I and J are determined by the line
direction. If you see the taper
going in the wrong direction,
simply reapply the pressure with
the values reversed.
VALI = 500
500
L3
500
VALI = 500
VALJ = 1000
L3
1000
500
VALI = 1000
VALJ = 500
L3
1000 500
Chapter 10 – B. Solution
…Pressure
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Uniform Temperature
• To uniform temperature
– Main Menu > Solution > Define Loads > Apply >
Structural > Temperature > Uniform Temp
– Or use the TUNIF command.
Chapter 10 – B. Solution
Uniform temperature
• To define reference temperature
– Main Menu > Solution > Load Step Opts > Other > Reference Temp
– Or use the TREF command or as MP,REFT
LTT refth )( • Recall,
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Gravity
• To apply gravitational acceleration:
– Main Menu > Solution > Define Loads >
Apply > Structural > Gravity
– Or use the ACEL command.
• Notes:
– A positive acceleration value causes deflection in the negative
direction. If Y is pointing upwards, for example, a positive ACELY
value will cause the structure to move downwards.
– Density (or mass in some form) must be defined for gravity and other
inertia loads.
Chapter 10 – B. Solution
Gravity
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Modifying and Deleting Loads
• To modify a load value, simply reapply the load
with the new value.
• To delete loads:
– Main Menu > Solution > Define Loads > Delete
– When you delete solid model loads, ANSYS also
automatically deletes all corresponding finite element
loads.
Chapter 10 – B. Solution
Modifying and Deleting Loads
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Static vs. Dynamic Analysis
• A static analysis assumes that only the stiffness forces are
significant.
• A dynamic analysis takes into account all three types of forces.
• For example, consider the analysis of a diving board.
– If the diver is standing still, it might be sufficient to do
a static analysis.
– But if the diver is jumping up and down, you will need
to do a dynamic analysis.
Chapter 10 – B. Solution
Solutions Options
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• Inertia and damping forces are usually significant if the applied
loads vary rapidly with time.
• Therefore you can use time-dependency of loads as a way to
choose between static and dynamic analysis.
– If the loading is constant over a relatively long period of time, choose
a static analysis.
– Otherwise, choose a dynamic analysis.
• In general, if the excitation frequency is less than 1/3 of the
structure’s lowest natural frequency, a static analysis may be
acceptable.
Chapter 10 – B. Solution
Solutions Options
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Linear vs. Nonlinear Analysis
• A linear analysis assumes that the loading causes negligible
changes to the stiffness of the structure. Typical characteristics
are:
– Small deflections
– Strains and stresses within the elastic limit
– No abrupt changes in stiffness such as two bodies coming into and
out of contact
Strain
Stress
Elastic modulus
(EX)
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Solutions Options
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• A nonlinear analysis is needed if the loading causes significant
changes in the structure’s stiffness. Typical reasons for stiffness
to change significantly are:
– Strains beyond the elastic limit (plasticity)
– Large deflections, such as with a loaded fishing rod
– Contact between two bodies
Strain
Stress
Chapter 10 – B. Solution
Solutions Options
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• Reviewing results of a stress analysis generally involves:
– Deformed shape
– Stresses
– Reaction forces
Deformed Shape
• Gives a quick indication of whether the loads were applied in the
correct direction.
• Legend column shows the maximum displacement, DMX.
• You can also animate the deformation.
Chapter 10 – C. Postprocessing
Review Results
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• To plot the deformed shape:
– General Postproc > Plot
Results > Deformed Shape
– Or use the PLDISP command.
• For animation:
– Utility Menu > PlotCtrls >
Animate > Deformed Shape
– Or use the ANDISP
command.
Chapter 10 – C. Postprocessing
…Review Results
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Stresses
• The following stresses are typically available for a 3-D solid
model:
– Component stresses — SX, SY, SZ, SXY, SYZ, SXZ (global Cartesian
directions by default)
– Principal stresses — S1, S2, S3, SEQV (von Mises), SINT (stress
intensity)
• Best viewed as contour plots, which allow you to quickly locate
“hot spots” or trouble regions.
– Nodal solution: Stresses are averaged at the nodes, showing smooth,
continuous contours.
– Element solution: No averaging, resulting in discontinuous contours.
Chapter 10 – C. Postprocessing
…Review Results
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• To plot stress contours:
– General Postproc > Plot Results > Contour Plot > Nodal Solu or PLNSOL command
– General Postproc > Plot Results > Contour Plot > Element Solu or PLESOL command
• You can also animate stress contours:
– Utility Menu > PlotCtrls > Animate > Deformed Results... or ANCNTR command
Chapter 10 – C. Postprocessing
…Review Results
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• There are many ways to review results in the general
postprocessor (POST1), some of which have already been
covered.
• In this chapter, we will explore two additional methods — query
picking and path operations — and also introduce you to the
concepts of results transformation, error estimation, and load
case combination.
Chapter 13 - Postprocessing
Overview
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• Query picking allows you to “probe” the model for stresses,
displacements, or other results quantities at any picked location.
• You can also quickly locate the maximum and minimum values of
the item being queried.
• Available only through the GUI (no commands):
– General Postproc > Query Results > Nodal or Element or Subgrid Solu
– Choose a results quantity and press OK
PowerGraphics
OFF
PowerGraphics
ON
Chapter 13 - Postprocessing
Query Picking
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– Then pick any point in the model to see the results value at that point.
• Min and Max will show the value at the minimum and maximum
points.
• Use Reset to clear all values and start over.
• Notice that the entity number, its location, and the results value are
also shown in the Picker.
Automatically
generate text
annotation
Chapter 13 - Postprocessing
…Query Picking
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• Demo: – Continue from the last multi-load-step solution of rib.db
– Plot SEQV for load step 1
– Query “Nodal Solu” SEQV at several locations, including MIN & MAX. (Switch to
full graphics if needed.)
– Switch to PowerGraphics and query “Subgrid Solu.”
Chapter 13 - Postprocessing
…Query Picking
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• All direction-dependent quantities that you view in POST1, such
as component stresses, displacements, and reaction forces, are
reported in the results coordinate system (RSYS).
• RSYS defaults to 0 (global Cartesian). That is, POST1 transforms
all results to global Cartesian by default, including results at
“rotated” nodes.
• But there are many situations — such as pressure vessels and
spherical structures — where you need to check the results in a
cylindrical, spherical, or other local coordinate system.
Chapter 13 - Postprocessing
Results Coordinate System
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• To change the results CS to a different
system, use:
– General Postproc > Options for Outp…
– or the RSYS command
All subsequent contour plots, listings, query picks, etc. will report
the values in that system.
Default orientation
RSYS,0
Local cylindrical
system RSYS,11
Global cylindrical
system RSYS,1
Chapter 13 - Postprocessing
…Results Coordinate System
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• RSYS,SOLU
– Sets the results CS to “As calculated.”
– All subsequent contour plots, listings, query picks, etc. will report the
values in the nodal and element coordinate systems.
• DOF results and reaction forces will be in the nodal CS.
• Stresses, strains, etc. will be in the element CS. (The orientation of
the element CS depends on the element type and the ESYS
attribute of the element. Most solid elements, for example, default
to global Cartesian.)
– Not supported by PowerGraphics.
Chapter 13 - Postprocessing
…Results Coordinate System
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• Another way to review results is via path operations, which allow
you to:
– map results data onto an arbitrary “path” through the model
– perform mathematical operations along the path, including integration
and differentiation
– display a “path plot” — see how a result item varies along the path
• Available only for models containing 2-D or 3-D solid elements or
shell elements.
Chapter 13 - Postprocessing
Path Operations
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• Three steps to produce a path plot:
– Define a path
– Map data onto the path
– Plot the data
1. Define a Path
– Requires the following information:
• Points defining the path (2 to 1000). You can use existing nodes or
locations on the working plane.
• Path curvature, determined by the active coordinate system
(CSYS).
• A name for the path.
Chapter 13 - Postprocessing
…Path Operations
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1. Define a Path (cont’d)
– First activate the desired coordinate system (CSYS).
– General Postproc > Path Operations > Define Path > By Nodes or On
Working Plane
• Pick the nodes or WP locations that form the desired path, and
press OK
• Choose a path name. The nSets and nDiv fields are best left to
default in most cases.
Chapter 13 - Postprocessing
…Path Operations
From
To
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2. Map Data onto Path
– General Postproc > Path Operations > Map onto Path (or PDEF
command)
• Choose desired quantity, such as SEQV.
• Enter a label for the quantity, to be used on plots and listings.
– You can now display the path if needed.
• General Postproc > Path Operations > Plot Paths
• (or issue /PBC,PATH,1 followed by NPLOT or EPLOT)
Chapter 13 - Postprocessing
…Path Operations
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3. Plot the Data
– You can plot path items either on a graph:
• PLPATH or General Postproc > Path Operations > Plot Path Item >
On Graph
– or along path geometry:
• PLPAGM or General Postproc > Path Operations > Plot Path Item >
On Geometry
Chapter 13 - Postprocessing
…Path Operations
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• ANSYS allows you to define multiple paths, each
with a unique name that you assign. Only one
path can be active at a time.
• Besides plots and listings, there are many other
path capabilities, including:
– Stress linearization — used in the pressure vessel
industry to decompose stress along a path into its
membrane and bending components.
– Calculus functions — used in fracture mechanics to
calculate J-integrals and stress concentration
factors. Also useful in thermal analyses to
calculate the heat lost or gained across a path.
– Dot products and cross products — used widely in
electromagnetics analyses to operate on vector
quantities.
Chapter 13 - Postprocessing
…Path Operations
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• Demo: – Continue with rib postprocessing…
– Plot nodes, then switch to CSYS,1 if desired
– Define a path using nodes
– Map SX or SEQV or other data onto path
– Plot the path itself
– Plot the path item on graph and on geometry
– Define a second path elsewhere in the model and show how to toggle between
the two.
Chapter 13 - Postprocessing
…Path Operations
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• The finite element solution calculates stresses on a per-element
basis, i.e, stresses are individually calculated in each element.
• When you plot nodal stress contours in POST1, however, you will
see smooth contours because the stresses are averaged at the
nodes.
If you plot the element solution, you will see unaveraged data,
which shows the discontinuity between elements.
Elem 1 Elem 2
savg = 1100
s = 1200 s = 1000
savg = 1200
s = 1300 s = 1100
• The difference between averaged and
unaveraged stresses gives an indication
of how “good” or how “bad” the mesh is.
This is the basis for error estimation.
Chapter 13 – Postprocessing
Error Estimation
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• Error estimation is available only in POST1 and is valid only for:
– linear static structural and linear steady-state thermal analyses
– solid elements (2-D and 3-D) and shell elements
– Full Graphics (not PowerGraphics)
If these conditions are not met, ANSYS automatically turns off
error estimation calculations.
• To manually activate or deactivate error estimation, use
– ERNORM,ON/OFF
– or General Postproc > Options for Outp
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…Error Estimation
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• POST1 calculates the following error measures.
– Stress analysis:
• percentage error in energy norm (SEPC)
• element stress deviations (SDSG)
• element energy error (SERR)
• maximum and minimum stress bounds (SMXB, SMNB)
– Thermal analysis:
• percentage error in energy norm (TEPC)
• element thermal gradient deviations (TDSG)
• element energy error (TERR)
Chapter 13 - Postprocessing
…Error Estimation
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Percentage error in energy norm (SEPC)
• SEPC is a rough estimate of the stress error (or displacement,
temperature, or thermal flux) over the entire set of selected
elements.
• Can be used to compare similar models of similar structures
subjected to similar loadings.
• SEPC is shown in the legend column of deformed shape displays.
You can list it manually using PRERR or General Postproc > List
Results > Percent Error.
Chapter 13 - Postprocessing
…Error Estimation
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• As a general rule of thumb,
look for SEPC to be 10% or
less. If it is higher, then:
– Check for point loads or
other stress singularities and
unselect elements in the
vicinity.
– If it is still higher, plot the
element energy error. The
elements with high values of
energy error are candidates
for mesh refinement.
SEPC = 35.149
SEPC = 3.484
Chapter 13 - Postprocessing
…Error Estimation
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Element stress deviations (SDSG)
• SDSG is a measure of the amount by
which an element’s stress disagrees with
the stress averages at its nodes.
• You can plot SDSG contours using
PLESOL,SDSG or General Postproc > Plot
Results > Contour Plot > Element Solu...
• A high value of SDSG is not necessarily
bad, especially if it is a small percentage
of the nominal stresses in the structure.
For example, this plate-with-a-hole model
shows only a 1.5% stress deviation in the
region of interest.
SDSG at location of interest
= ~450 psi, which is ~1.5% of
~30,000 psi nominal stress
Chapter 13 - Postprocessing
…Error Estimation
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Element energy error (SERR)
• SERR is the energy associated with the stress mismatches at the
nodes of the element. This is the basic error measure from which
the other error quantities are derived. SERR has units of energy.
• To plot SERR contours, issue PLESOL,SERR or General Postproc >
Plot Results > Contour Plot > Element Solu
• Generally, the elements with the highest SERR are candidates for
mesh refinement. However, since SERR will always be highest at
stress singularities, be sure to unselect those elements first.
Chapter 13 - Postprocessing
…Error Estimation
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Stress bounds (SMXB and SMNB)
• The stress bounds can help you determine the potential effect of
mesh discretization error on the maximum stress.
• They are displayed on stress contour plots in the legend column
as SMXB (upper bound) and SMNB (lower bound).
• The bounds are not estimates of the actual maximum and
minimum, but they do define a “confidence band.” Without other
supporting verification, you have no basis for believing that the
true maximum stress is below SMXB.
Chapter 13 - Postprocessing
…Error Estimation
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• Caution: If you don’t unselect elements near stress singularities,
the stress bounds are meaningless, as shown below.
SMXB = 6,401 SMXB = 15,750
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…Error Estimation
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• Whenever you solve multiple load steps, the results of each load
step are stored as separate sets on the results file (identified by load
step number).
• A load case combination is an operation between two sets of
results, which are called load cases.
– The operation occurs between one load case in the database and the
second load case on the results file.
– The result of the operation — the combined load case — is stored back
in the database.
Load case in database
(computer memory)
Load case
on results file Combined load case in database
overwrites previous contents
Chapter 13 - Postprocessing
Load Case Combinations
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Typical procedure:
1. Create the load cases
2. Read one load case into the database
3. Perform the desired operation
Chapter 13 - Postprocessing
…Load Case Combinations
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Create Load Cases
• A load case simply acts as a pointer to a set
of results. It requires two pieces of
information:
– a unique ID number
– the results set it represents (load step and
substep number)
• Use the LCDEF command or General
Postproc > Load Case > Create Load Case
Chapter 13 - Postprocessing
…Load Case Combinations
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Read One Load Case into the Database (memory)
• Simply identify the results set by its load case
number using LCASE or General Postproc > Load
Case > Read Load Case.
• Or use one of the standard “Read Results” choices
in the postprocessor (SET command).
Chapter 13 - Postprocessing
…Load Case Combinations
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Perform the Desired Operation
• Many operations are available as shown in
the menu here.
• Use the LCOPER command or General
Postproc > Load Case > Add, Subtract, etc.
• Remember that the results of the operation
are stored in the database (memory). The
combined load case is identified on plots
and listings as number 9999.
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…Load Case Combinations
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• There are two useful options to
save the combined load case:
– Write a load case file
– Append the load case to the results
file
• Writing a load case file (LCWRITE
or General Postproc > Write Results)
creates a file that is similar to, but
much smaller than the results file.
• The Append option (RAPPND or
General Postproc > Load Case >
Write Load Case) allows you to add
the combined load case to the
results file and identify it with a
given load step number and time
value.
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…Load Case Combinations
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• Refer to your Workshop Supplement for instructions:
W13A. Connecting Rod
W13B. Spherical Shell
W13C. Axisymmetric Fin with Multiple Load Steps
Chapter 13 - Postprocessing
Workshops
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• The Results Viewer is a specialized postprocessing menu and graphic
system.
– Fast graphics for large models or models that have many time steps
– Easy to use menu system for quick results viewing
Chapter 13 - Postprocessing
Results Viewer
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• Can be created two different ways …
– Use the POUTRES command before solving
to write a jobname.pgr file during solution.
– Main Menu > Solution > Load Step Opts >
Output Cntrls > PGR File
Hold CTRL key for
multiple selection
Chapter 13 - Postprocessing
…Results Viewer
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– Use the PGWRITE command after solution
to write a jobname.pgr file.
– General Postproc > Write PGR File
Chapter 13 - Postprocessing
…Results Viewer
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• Open the Results Viewer from the General Post Processor.
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…Results Viewer
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Element Plot
Nodal/element/vector/trace
results plots
Query Results
Animate using
PNG files
List
Results
Image Capture
Results Set
Locator
Chapter 13 - Postprocessing
…Results Viewer
Time History
Variable Viewer
Report Generation
Mode
Report
Image
Capture
Time
Load Step
Substep
Raise
Hidden
Report
Animation
Capture
Report
Listing
Capture
Report
Table
Capture
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• The graphics window becomes “Context Sensitive”.
Right Click on Model
Chapter 13 - Postprocessing
…Results Viewer
Context-sensitive graphics window
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Right Click on Contour Legend
Context-sensitive graphics window
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…Results Viewer
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Context-sensitive graphics window
Right Click on Contour Bar
Chapter 13 - Postprocessing
…Results Viewer
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Chapter 13 – Postprocessing
Variable Viewer
• The Variable Viewer is a specialized tool allowing one to postprocess results
with respect to time.
• The Variable Viewer can be started by:
– Main Menu > TimeHist Postproc > Variable Viewer
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12
17
Add variable button 1
Delete variable button 2
Graph variable button 3
List variable button 4
Properties button 5
Import data button 6
Export data button 7
Export data type 8
Clear Time History Data 9
Refresh Time History Data 10
Variable name input area
11
Expression input area 14
Defined APDL variables 15
Defined Post26 variables 16
17 Calculator
Chapter 13 - Postprocessing
…Variable Viewer
16
Real/Imaginary Components
Variable list
14
12
13
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15
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100kg
25kg
k = 36kN/m
F
0,0
0,4000
t
tNF
k = 36kN/m
x
y
Chapter 13 - Postprocessing
…Variable Viewer
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• A time consuming part of any
analysis is documenting the
model and results. This
procedure has been partially
automated through the
implementation of the ANSYS
Report Generator.
• The Report Generator allows
the user to quickly capture
pictures, listings, tables, and
other pertinent information.
• It also facilitates the creation of
an HTML formatted file ready to
be distributed to colleagues or
posted to a web site.
Chapter 13 - Postprocessing
Report Generator
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• Launching the Report Generator will
shrink the graphics window and set the
background to white.
• The “Capture Tool” will be opened
allowing the user to grab plots, listings,
and tables. – Utility Menu> File> Report Generator…
or
– ~eui,’euidl::report::toolbar::create’ or
– Select on the Icon Toolbar.
Capture Tool
Chapter 13 - Postprocessing
…Report Generator
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Image Capture
(single PNG file)
Animation Capture
(multiple PNG files)
Table
Capture
Settings
HTML Report
Assembler
Listing
Capture
The Log File records
all captures!
• Capture Tool
Chapter 13 - Postprocessing
…Report Generator
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HTML Assembler . . .
• A tool that allows quick
organization of ANSYS graphics,
tables, listings .
• Log file can be used as an HTML
template.
– utilize parameter substitution
• The generated HTML file can be
used with Netscape Composer,
Microsoft FrontPage, or any other
HTML editor to finalize the report.
Chapter 13 - Postprocessing
…Report Generator
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• Insert TEXT
• Insert any HTML FILE
– possibly created outside ANSYS
• Insert an IMAGE
– possibly one from an external
source like a digital photo
• Insert DYNAMIC DATA
– information specific to your current
ANSYS run like version, run time,
etc.
• Insert a Report Heading
– Including your name, analysis title,
date, and company name
Chapter 13 - Postprocessing
…Report Generator
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• Insert information grabbed using
the Capture Tool
• Report Images
– Contour plots, element plots,
volume plots, graphs
• Report Tables
– Material properties, reaction forces,
etc.
• Report Lists
– Stress along a path, constraints,
etc.
Chapter 13 - Postprocessing
…Report Generator
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• Preview the report
• Delete sections of the report
• Move sections of the report up or
down
Chapter 13 - Postprocessing
…Report Generator
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