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Chapter 5 3D Simulations 1
Chapter 53D Simulations5.1 Step-by-Step: Beam Bracket
5.2 Step-by-Step: Cover of Pressure Cylinder
5.3 More Details
5.4 More Exercise: LCD Display Support
5.5 Review
Chapter 5 3D Simulations Section 5.1 Beam Bracket 2
Section 5.1Beam Bracket
Problem Description
[1] The bracket is made of
structural steel.
[2] The bracket is designed to
withstand a load of 27 kN uniformly distributed over
the seat plate.
[3] Fixed support at the back
face.
Chapter 5 3D Simulations Section 5.1 Beam Bracket 3
Techniques/Concepts
• Engineering Data
• Material Assignment
• Stress Tool>Safety Factor
• Structural Error
• Mesh Control>MultiZone
• 3D Solid Elements
Chapter 5 3D Simulations Section 5.2 Cover of Pressure Cylinder 4
Section 5.2Cover of Pressure Cylinder
Problem Description
[3] Circularity of this internal
surface is what concerns us most.
[1] The cover is made of an engineering
plastic.
[2] The cover is designed to hold
up an internal pressure of 0.5
MPa.
Chapter 5 3D Simulations Section 5.2 Cover of Pressure Cylinder 5
Techniques/Concepts
• Add a new material in
<Engineering Data>
• Isotropic Elasticity
• Material Assignment
• Loads>Pressure
• Create a new coordinate
system
• Cylindrical Coordinate
Systems
Chapter 5 3D Simulations Section 5.3 More Details 6
Global Mesh Controls
• Relevance Center
• Relevance
• Number of nodes/elements
• Mesh Quality Metric
Section 5.3More Details
Chapter 5 3D Simulations Section 5.3 More Details 7
Mesh with MultiZone Method
• Generally, hexahedral elements are more
desirable than tetrahedral.
• A simple idea of creating hexahedra is to
mesh faces (source) of a body with
quadrilaterals and then "sweep" along a path
up to other end faces (target) of the body.
• Not all bodies are sweepable.
• The idea of <MultiZone> method is to
decompose a non-sweepable body into
several sweepable bodies, and then apply
<Sweep> method on each of bodies.
Chapter 5 3D Simulations Section 5.3 More Details 8
Coordinate Systems
• When defining an environment
condition or a solution object by
<Components>, you need to refer
to a coordinate system. By default,
<Global Coordinate System> is
used, which is a Cartesian
coordinate system.
• To define a new coordinate
system, you need to define the
type of the coordinate system, the
origin, and the axes.
[1] Type of the coordinate
system.
[2] Origin.
[3] Axes.
Chapter 5 3D Simulations Section 5.3 More Details 9
[1] Increase/decrease contour
bands.
[4] Number of significant digits.
[3] Double-click to edit value.
[5] Turn on/off the date/time.
[6] Display independent
bands.
[2] The divider can be dragged.
[7] Reset the legend.
Legend Controls
Chapter 5 3D Simulations Section 5.3 More Details 10
Adaptive Meshing
• Workbench provides a tool to
automate the mesh refinement
until a user-specified level of
accuracy is reached.
• This idea is termed adaptive
meshing.
• Internally, Workbench exploits
the structural errors to help
adjust the mesh, that is, it refines
the mesh size in the area of
large structural errors.
Chapter 5 3D Simulations Section 5.4 LCD Display Support 11
Section 5.4LCD Display Support
Problem Description [2] The design load (40 N) applies on
the trough.
[1] The LCD display support is made of an ABS
plastic.
Chapter 5 3D Simulations Section 5.4 LCD Display Support 12
Techniques/Concepts
• Loads>Bearing Load
Chapter 6 Surface Models 1
Chapter 6Surface Models6.1 Step-by-Step: Bellows Joints
6.2 Step-by-Step: Beam Bracket
6.3 More Exercise: Gearbox
6.4 Review
Chapter 6 Surface Models Section 6.1 Bellows Joints 2
Section 6.1Bellows Joints
Problem Description
• With the internal pressure, the
engineers are concerned about the
radial deformation (due to an
engineering tolerance
consideration) and hoop stress
(due to a safety consideration).
Chapter 6 Surface Models Section 6.1 Bellows Joints 3
R315
28
R315 28
20
Unit: mm.
Chapter 6 Surface Models Section 6.1 Bellows Joints 4
Techniques/Concepts
• Create surface bodies
using <Revolve>.
• Top/Bottom of a surface
body
• Shell Elements
Chapter 6 Surface Models Section 6.2 Beam Bracket 5
Section 6.2Beam Bracket
Techniques/Concepts
• Create surface bodies
using <Mid-Surface>
Chapter 6 Surface Models Section 6.3 Gearbox 6
Section 6.3Gearbox
Problem Description
[3] The housing is made of
stainless sheet steel of 3 mm
thickness.
[1] The flanged bearing is made of gray cast iron.
[2] The base is also made of cast
iron.
Chapter 6 Surface Models Section 6.3 Gearbox 7
Unit: mm.
540
520
240
180
100
355
15 3
0
170 R30
R50 R20
R40
170 200 70
(R170)
(R70)
Chapter 6 Surface Models Section 6.3 Gearbox 8
Techniques/Concepts
• Create surface bodies by
<Thin/Surface>
• Loads>Bearing Loads
• Set up <Bonded>
connections.
Chapter 7 Line Models 1
Chapter 7Line Models7.1 Step-by-Step: Flexible Gripper
7.2 Step-by-Step: 3D Truss
7.3 More Exercise: Two-Story Building
7.4 Review
Chapter 7 Line Models Section 7.1 Flexible Gripper 2
Section 7.1Flexible Gripper
Problem Description
[3] Actuation direction (input).
[2] The ends are connected to a rigid ground (preventing
translations and rotations).
[4] Gripping direction (output).
[1] The gripper is made of POM.
P1(−70,0)
P2(−90,40)
P3(−69,120)
P4(−35,160)
P5(−34,100)
P6(−24,60)
P7(0,50)
X
Y
Chapter 7 Line Models Section 7.1 Flexible Gripper 3
Techniques/Concepts
• Line bodies
• Cross Sections
• Cross Section Alignments
• Cross Section Solids
• Beam Elements
• Symmetry Conditions
• Geometric Advantage
0
10
20
30
40
50
60
0 5 10 15 20 25 30 35 40 45 50
Hor
izon
tal D
ispl
acem
ent
(mm
)
Input Displacement (mm)
Chapter 7 Line Models Section 7.1 Flexible Gripper 4
52.24
52.26
52.28
52.30
52.32
0 125 250 375 500 625
Out
put
Dis
plac
emen
t (m
m)
Number of Elements
Convergence Study of Beam Elements
[1] In this exercise, we meshed with 34
elements, resulting 52.335 mm of displacement.
[2] The displacement converges to 52.381 mm.
Chapter 7 Line Models Section 7.2 3D Truss 5
200"
200"
75"
P1 P2
P3
P4
P5 P6
P7 P8
P9 P10
1
2
3 4
5 6 7 8 9
10 11
12 13
14 15
16
17
18 19
20
21
22 23
24
25
100
" 10
0"
X Y
Z
75"
Section 7.23D Truss
Problem Description
Design Loads for the Transmission Tower
Joint FX (lb) FY (lb) FZ (lb)
P1 1,000 -10,000 -10,000
P2 0 -10,000 -10,000
P3 500 0 0
P6 600 0 0
Chapter 7 Line Models Section 7.2 3D Truss 6
Techniques/Concepts
• Create points
• Concepts>Lines From Points
• Convergence of straight beam
elements
Chapter 7 Line Models Section 7.3 Two-Story Building 7
Section 7.3Two-Story Building
Problem Description
[1] All beams and columns are made of structural steel,
with a cross section of W16x50. [2] The floor slabs
are made of reinforced concrete, with a thickness of 5".
[3] Each floor-to-floor height is 10'.
20
'
20 ' 20 ' 20 '
Chapter 7 Line Models Section 7.3 Two-Story Building 8
Techniques/Concepts
• Adjust Cross Section
Alignments
• Concepts>Surface From
Edges
• Use of Selection Panes
• Flip Surface Normal
• Form New Part
• Import Engineering Data
• Inertial>Standard Earth
Gravity
• Inertial>Acceleration
Chapter 8 Optimization� � 1
Chapter 8Optimization8.1� Step-by-Step: Flexible Gripper
8.2� More Exercise: Triangular Plate
8.3� Review
Chapter 8 Optimization� Section 8.1 Flexible Gripper� 2
Section 8.1Flexible Gripper
Problem Description
P1(�70,0)
P2(�90,40)
P3(�69,120)
P4(�35,160)
P5(�34,100)
P6(�24,60)
P7(0,50)
X
Y
• Positions of the P2, P3, and P6 are free to be changed.
• The idea is to fix the X-coordinates of these points and
adjust their Y-coordinates to achieve a better GA value.
• Allowable adjustment ranges are 10 mm for P2, 20 mm
for P3, and 5 mm for P6.
• The maximum stress should not exceed 15 MPa.
Chapter 8 Optimization� Section 8.1 Flexible Gripper� 3
Techniques/Concepts
• Input Parameters
• Output Parameters
• Design Points
• Goal Driven Optimization
• Design of Experiments
• DOE Tables
• Response Surfaces
• Optimization
• Objectives and Constraints
• Optimization algorithms
• Current Design
Chapter 8 Optimization� Section 8.2 Triangular Plate� 4
Section 8.2Triangular Plate
Problem Description
W
R
[2] The initial value of the width of the
bridge is 30 mm and its allowable range is
20-30 mm.
[3] The initial value of the radius of the fillet is 10 mm and its allowable range is
5-15 mm.
[1] we want to change the values
of W and R to reduce the amount
of material.
Chapter 8 Optimization� Section 8.2 Triangular Plate� 5
Techniques/Concepts
• No additional techniques/concepts are introduced.
Chapter 9 Meshing 1
Chapter 9Meshing9.1 Step-by-Step: Pneumatic Fingers
9.2 More Exercise: Cover of Pressure Cylinder
9.3 More Exercise: Convergence Study of 3D Solid Elements
9.4 Review
Chapter 9 Meshing Section 9.1 Pneumatic Fingers 2
Section 9.1Pneumatic Fingers
Problem Description
Unit: mm.
80
5
1 2
5.1 4
3 3.2 1 (19.2)
Plane of symmetry.
Chapter 9 Meshing Section 9.1 Pneumatic Fingers 3
Techniques/Concepts
• Mesh Metric: Skewness
• Hex Dominant Method
• Sweep Method
• MultiZone Method
• Section View
• Nonlinear Simulations
• Line Search
• Displacement Convergence
Chapter 9 Meshing Section 9.2 Cover of Pressure Cylinder 4
Section 9.2Cover of Pressure Cylinder
Techniques/Concepts
• Patch Conforming Method
• Patch Independent Method
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 5
Section 9.3Convergence Study of 3D Solid Elements
Problem Description
100 mm
10 mm
[1] The beam is made of steel.
[2] The width of the beam is 10 mm. A uniform load of 1 MPa applies on the upper face of the beam.
[3] We will record the vertical tip deflection.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 6
Element Shapes
[1] hexahedron. [2] Tetrahedron.
[4] Perpendicular prism.
[3] Parallel prism.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 7
0.60
0.64
0.68
0.72
0.76
0 3000 6000 9000 12000 15000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Lower-Order Elements
[1] Lower-order tetrahedron.
[2] Lower-order perpendicular
prism.
[3] Lower-order parallel prism.
[4] Lower-order hexahedron.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 8
0.746
0.747
0.748
0.749
0.750
0.751
0.752
0 2000 4000 6000 8000 10000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Higher-Order Elements
[1] Higher-order tetrahedron.
[2] Higher-order perpendicular prism.
[3] Higher-order parallel prism.
[4] Higher-order hexahedron.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 9
0.746
0.747
0.748
0.749
0.750
0.751
0.752
0 2000 4000 6000 8000 10000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Hexahedra
[2] Higher-order hexahedron.
[1] Lower-order hexahedron.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 10
0.600
0.640
0.680
0.720
0.760
0 2000 4000 6000 8000 10000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Tetrahedra
[1] Lower-order tetrahedron.
[2] Higher-order tetrahedron.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 11
0.66
0.68
0.70
0.72
0.74
0.76
0 2000 4000 6000 8000 10000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Parallel Prisms
[2] Higher-order parallel prism.
[1] Lower-order parallel prism.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 12
0.66
0.68
0.70
0.72
0.74
0.76
0 2000 4000 6000 8000 10000
Tip
Def
lect
ion
(mm
)
Number of Nodes
Perpendicular Prisms
[2] Higher-order perpendicular prism.
[1] Lower-order perpendicular prism.
Chapter 9 Meshing Section 9.3 Convergence Study of 3D Solid Elements 13
Guidelines
• Never use lower-order tetrahedra/triangles.
• Higher-order tetrahedra/triangles can be as good as other elements as long as the
mesh is fine enough. In cases of coarse mesh, however, they perform poorly and
are not recommended.
• Lower-order prisms are not recommended.
• Lower-order hexahedra/quadrilaterals can be used, but they are not as efficient as
their higher-order counterparts.
• Higher-order hexahedra, prisms, and quadrilaterals are among the most efficient
elements so far we have discussed. Mesh your models with these elements
whenever possible. If that is not possible, then at least try to achieve a higher-
order hexahedra-dominant or quadrilateral-dominant mesh.