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Altair Confidential
Optimization and Lifing of
Aircraft Structures and Engines
Dr. J. S. Rao
Chief Science Officer
January 8 2011
GITAM University
Visakhapatnam
Altair Confidential
Design a column such that
Stress induced is < yield and buckling
Mean diameter d to be in the range 2 to 14 cm
Thickness t to be in the range 0.2 to 0.8 cm
Cost to be lowest, given by 5 times weight + 2
times the mean diameter.
E = 0.85×106 kg/cm2
Density = 0.0025 kg/cm2
Length l = 250 cm
P = 2500 kg
Yield stress = 500 kg/cm2
Optimization – Mathematical Programming
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Design Vector
Formulation
t
d
x
xX
2
1
Objective Function 121 282.92525 xxxddtldWXf
Behavioral Constraints
5002500
21
xxdt
P
stressyieldstressinduced
2
2
2
2
1
62
21 2508
1085.02500 xx
xx
stressbucklingstressinduced
Side Constraints
8.02.0
0.140.2
t
d
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Given the Design Vector
Statement of Problem
2
1
x
xX
Minimize the Objective Function 121 282.9 xxxXf
Subject to Constraints 05002500
21
1 xx
Xg
0
2508
1085.025002
2
2
2
1
62
21
2
xx
xxXg
08.0
02.0
00.14
00.2
26
25
14
13
xXg
xXg
xXg
xXg
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Problem with Two Design Variables
Constraint 1
593.1
05002500
21
21
1
xx
xxXg
3.47
02508
1085.02500
2
2
2
121
2
2
2
2
1
62
21
2
xxxx
xx
xxXg
8.0;2.0;0.14;0.2 2211 xxxx
Plot P1 Q1 593.121 xx
Plot P2 Q2
Constraint 2
3.472
2
2
121 xxxx
Plot all side constraints 3 to 6
Choose different values of C
and plot; C = 50, 40, 31.8, 26.53
CxxxXf 121 282.9
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Graphical Solution – Design Space – Optimum Point
Graphical Optimization
0.0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0 1 2 3 4 5 6 7 8 9 10 11 12 13 14
d(X1)
f(X
2)
X1*X2 = 1.593X1*X2*(X1**2 + X2**2) = 47.3
C = 50C = 40
C = 31.8C = 26.53
Optimum Point
(5.44, 0.293)
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Iterations X1 X2
1 2 0.2
2 2.44 0.2
3 2 0.244
4 2.4 0.238
5 2.30879 0.2856
6 2.36005 0.321197
7 2.80846 0.385437
8 3.37015 0.45867
9 4.01048 0.550404
10 4.36014 0.445827
11 4.66099 0.356662
12 5.23217 0.386645
13 5.27673 0.309316
14 5.31056 0.313182
15 5.33557 0.309316
16 5.45705 0.292034
Objective_1 Constraint_1 Constraint_2
7.928 -1.193 -45.684
9.67216 -1.105 -44.3751
8.79216 -1.105 -45.3189
10.4092 -1.0218 -43.9775
11.0928 -0.93361 -43.7313
12.1641 -0.83496 -42.9996
16.2469 -0.51052 -38.6011
21.9199 -0.04721 -29.4179
29.6975 0.614384 -11.1278
27.8091 0.350868 -9.95916
25.6467 0.069398 -10.9731
30.3301 0.429989 8.38288
26.5814 0.039176 -1.69776
26.9535 0.070174 -0.23196
26.8778 0.057375 -0.15874
26.5637 6.44E-04 0.293614
Response Surface Analysis
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Classification of Optimization Problems
Constraints Design Variables Physical Structure
Constrained
Equality and
Inequality
Unconstrained
No constraints
Parameter or
Static –
Minimum weight of a
Prismatic Beam
Dynamic –
Minimum weight of a
Beam with variable
Cross-section –
Design Variables
continuous function
through space
Optimal Control
Two types of variables
Control (design) and
State variables
Non-optimal
Nature of Equations
Nonlinear
Programming
Geometric
Programming
Quadratic
Programming
Linear
Programming
Stochastic Programming Multi-objective Programming
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Static Optimization –
Prismatic Beam
Static/Dynamic Optimization Problems
d
b
x
xX
2
1 lbdXf
0
0
max
d
b
Xtip
Dynamic Optimization –
Variable Cross-section Beam
Depends not only on the
variables but also on the
trajectories through some sort
of space.
td
tbtX dttdtbtXf
l
0
lttd
lttb
lttXtip
0,0
0,0
0,max
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Optimal Control Problem
l
i
iii yxfXf1
,
Control (design) variables x thrust and
state variables y velocity of a rocket;
Control variables govern the evolution of
the system from one stage i to the next i+1
and the state variables describe the system
in any stage; q may represent the thrust
velocity relationship in each stage, g may
be the maximum thrust available in a
given stage ….
Mathematical programming involving a
number of stages, where each stage
evolves from the previous stage.
Determine the control variables x such that
the total objective function over l number
of stages, time, is minimized.
lkyh
ljxg
liyyyxq
kk
jj
iiiii
,...,2,1,0
,...,2,1,0
,...,2,1,, 1
ix
x
x
X 2
1
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Nonlinear Programming
w
d
d
d
X3
2
1Three stepped cone pulley drive, dias di all
having same width w and shaft center
distance a to be designed for minimum
weight to transmit a minimum power from
a constant speed input N and desired
output speeds and tension ratio of the belt.
3
1
2
2 14 N
NdwXf i
i
Same length c of all belts
Equality constraints 0
0
31
21
cc
cca
a
dN
N
N
Ndc
ii
iii 2
4
1
12
2
2
Constraint on ratio of tensions
- Inequality constraint2
21sin2exp 1
a
d
N
N ii
Constraint on Power -
Inequality constraint min
1
17600
'
21sin2exp1 HP
Nd
a
d
N
NT iiii
3,2,1,0;0 idw i
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Geometric Programming
Polynomial Function
N
i
a
j
n
ji
a
n
aa
N
a
n
aa
ij
NnNNn
xc
xxxcxxxcXh
11
1211211 ......... 2111211
o
ij
N
i
ji
p
j
n
ji xcxcXf
11
0,0,Objective Function
Constraints mjaxaXgj
ik
N
i
ij
q
k
n
kijj ,...2,1,0,0
11
Cost minimization of a shell and tube type heat
exchanger with a constraint on thermal energy
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Linear Programming
XCxcxcxcxcXfT
n
j
jjnn 1
2211 ...Objective Function
Constraints
mnmnmm
nn
nn
bxaxaxa
bxaxaxa
bxaxaxa
...
...
...
...
2211
22222121
11212111
0,..1,0
,..1,
1
Xnjx
BXA
mibxa
j
n
j
ijij
Statement of the Problem
n variables, m constraint equations
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Linear Programming – Dantzig’s Simplex Method - 1947
54321 32103 xxxxxXf
10040102015080
300060010060030002500
54321
54321
xxxxx
xxxxx0ix
n = 5, m = 2 No. of Basic Solutions
10!!
!
mmn
n
• The optimum feasible basic solution out of the 10 basic solutions is given here.
Choose basic variables x1, x5
1048
30625
51
51
xx
xx
26
5,
13
21 51 xx
26
14f
Let
• To obtain a basic solution set
n-m variables (non-basic) = 0
• Choose m out of n variables
as basic and the rest n-m as non
basic variables.
• Feasible solution is one which
satisfies the inequality constraints
• If the solution obtain is not optimal, find a neighboring basic feasible solution which has
a lower value of f and repeat the process until an optimum is found.
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Associated with every linear programming problem, called the primal, there
is another linear programming problem called its dual. These two problems
possess very interesting and closely related properties. If the optimal solution
to any one is known, the optimal solution to the other can readily be obtained.
In fact, it is immaterial which problem is designated the primal since the dual of a
dual is the primal. Because of these properties, the solution of a linear
programming problem can be obtained by solving either the primal or the dual,
whichever is easier.
Primal and Dual Problems
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Primal Problem
mnmnmm
nn
nn
bxaxaxa
bxaxaxa
bxaxaxa
...
...
...
...
2211
22222121
11212111
nixxcxcxcf inn ,..1,0 ...2211
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Dual Problem
nmmnnn
mm
mm
cyayaya
cyayaya
cyayaya
...
...
...
...
2211
22222112
11221111
maximized be tois and ,..1,0
...2211
vmiy
ybybybv
i
mm
Dual problem is formulated by transposing the rows and columns of Primal including
the right-hand side and the objective function, reversing the inequalities and
maximizing instead of minimizing. Denoting the dual variables as y1, y2 … ym,
symmetric primal-dual pairs
The dual of the dual is the primal
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Topology Optimization
• Topology optimization generates optimal shape of a structure.
• The shape is generated within a pre-defined design space.
• In addition, the user provides structural supports and loads.
• Without any further decisions and guidance, the method will form the
structural shape providing a first idea of an efficient geometry.
• Therefore, topology optimization is a much more flexible design tool
than classical structural shape optimization, where only a selected
part of the boundary is varied without any chance to generate a
lightness hole, for example.
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• Finite element discretization of the design space
• Strain Energy Density in each element can be used as a measure to identify the
material necessary to carry the given load
Strain Energy Density Approach
Key to Topology Optimization
► Find how the load is transmitted in the structure before optimization
► Identify the material taking the load vis a vis idle material
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Load Path with Strain Energy Density
Manual Topology optimization based on strain energy
Iteration IT0 Iteration IT1
Iteration IT2 Iteration IT3
Iteration IT4 Iteration IT5
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Solid Isotropic Material with Penalization - SIMP
Function between “relative density“ and
Elasticity using penalty factor p
E/E0
/0
/0)p
1
1
Step 1: Finite element discretization of the design space - Arbitrarily assign for each element volume
fraction (relative density)
Step 2: Convert for each element /0 into E/E0 and find Young’s modulus E in accordance to the value of
penalty parameter p. Start with using penalty = 1
Step 3: Set up each element stiffness matrix and assemble them to form global stiffness matrix
Step 4: Set up [K]{x}={F} and solve for {x}. This will be the response for the structure to begin with.
This of course is not what we want.
Step 5: For each element set up different values of /0 with chosen step size say 0.5 above and below the
starting values. Set up DOE and find responses.
Step 6: Minimize the response vector {x} with E/E0 (i.e., /0) as design variables and obtain the new set
of /0.
Step 7: Go back to step 1 and repeat the iterations until /0 have converged.
p = 4
13 iterations
p = 1
6 iterations
FxK
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Simple Topology Example - Model details
1 2 3 4 5 6
7 8 9 10 11 12
13 14 15 16 17 18
Element IDs
Element ID
Node ID
50 N each
18 Elements and 56 Nodes
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Baseline Analysis
E = 210000 MPa
= E0
Node ID v/s Displacement
-2.00E-03
-1.50E-03
-1.00E-03
-5.00E-04
0.00E+00
5.00E-04
0 10 20 30 40 50 60
Node ID
Dis
pla
cem
en
t
E/E0
/0
/0)p
1
1
p = 1
0.001826 Elements 7-8
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Iteration 1
= 0.5E0
Node ID v/s Displacement
-0.004
-0.0035
-0.003
-0.0025
-0.002
-0.0015
-0.001
-0.0005
0
0.0005
0 10 20 30 40 50 60
Node ID
Dis
pla
ce
me
nt
Reduce density by half
For p = 1, E is reduced by half
Find displacements
Max displ doubles to 0.003652
Keep same displacement as baseline
and reduce weight or find where
material is necessary, i.e find the load
path by iterations
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= 0.2E0
= 0.8E0
= 0.5E0
Node ID v/s Dispalcement
-3.00E-03
-2.50E-03
-2.00E-03
-1.50E-03
-1.00E-03
-5.00E-04
0.00E+00
5.00E-04
0 10 20 30 40 50 60
Node ID
Dis
palc
em
en
t
Iteration 2
Reduce density where deflections are
small, i.e., E, for example as above.
Find displacements
Max displ reduced to 0.002524
Find the improved load path
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Iteration 3
= 0.1E0
= E0
= 0.8E0
Node ID v/s Diplacement
-2.50E-03
-2.00E-03
-1.50E-03
-1.00E-03
-5.00E-04
0.00E+00
5.00E-04
0 10 20 30 40 50 60
Node ID
Dip
lacem
en
t
The above E (or ) distribution
Gives the same displacement as
baseline
We need a truss like structure with
red elements above and the other
elements can be removed.
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Function between density and
elasticity using penalty factor p
Density = 1
Density = 0
E/E0
/0
/0)p
1
1
Problem solution using finite elements and
iterative optimization procedure
Topology Optimization
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…Engineer defines Requirements… …Altair OptiStruct Creates
Optimal Design Concepts
Building a Bridge…
Design Conceptualization
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Fundamental Procedure of Topology Optimization
“old” design
design proposal
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Optimization Methods in OptiStruct
• Automatic selection of best optimization algorithm (all local approximation methods)
- Optimality criteria method (a primal method)
- Convex approximation method (a dual method)
- Method of feasible directions (a primal method)
- Sequential quadratic programming (a primal method)
• The design sensitivity analysis of the structural responses (with respect to the design
variables) is one of the most important ingredients to take the step from a simple
design variation to a computational optimization.
• The design update is computed using the solution of an approximate optimization
problem, which is established using the sensitivity information.
• Among the four optimization methods listed above, the last three are based on a
convex linearization of the design space.
• The dual or primal methods are used depending upon the number of constraints and
design variables. The dual method is of advantage if the number of design variables
exceeds the number of constraints (common in topology and topography
optimization). The primal method is used in the opposite case, which is more
common in size and shape optimizations. However, the choice is made automatically
by OptiStruct.
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Optimization Methods in HyperStudy
• Method of feasible directions – Local Approximation Method
• Sequential quadratic programming – Local Approximation Method
• Adaptive Response Surface Method – Global Approximation Method
• Genetic Algorithm – Exploratory Method
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Concept Design Synthesis - Topology Optimization
Topology Optimization
Geometry Extraction
Topology Optimization
Design Space and Loads
Size and Shape Optimization
Fine-tuning the Design
Topology
Optimization
Stiffness Material
Layout
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Pre World War II – Truss Type Designs
Dornier 728
Henkel
To obtain the airfoil lifting surface, early aeronautical structural engineers noticed Truss
type of structures and adopted a similar design for wings
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Post World War II Wing Designs
Spar location chart for Boeing 7X7 Series; they were evolved from practice
and testing and got standardized in each aircraft
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Post World War II Wing Designs
Spar location chart for Airbus Jets
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Post World War II Wing Designs
Spar location chart for DC-Series Jets
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Average rib spacing for Boeing 7X7 series
Post World War II Wing Designs
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Average rib spacing for Airbus jets
Post World War II Wing Designs
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Average rib spacing for DC-series jets
Post World War II Wing Designs
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Airbus A380 Droop Nose Leading Edge
Wing is over 36m long and 3m thick at its deepest section
14 Wing Ribs vary in Size from
• 3m x 2m x 0.12m to
• 1m x 0.89m x 0.12m
Courtesy of Airbus
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Topology Optimization
Geometry Extraction
ICAD Solid
Geometry Extraction
Size and Shape Optimization
Geometry Extraction
Topology Optimization Stiffness
Material Layout
Size and Shape Optimization
Buckling and Stress
Topology Optimization Design
Space and Load
Mass Savings of 44% (500kg) 13 Ribs developed in 7 weeks
Concept Design Synthesis - Topology Optimization
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Topology Derives Conventional Design Practice
13500 mm
4740 mm
Aluminum
Young’s Modulus = 70000 MPa
Poisson’s ratio = 0.33
Density = 2.60E-09 tn/mm3
Given the airfoil needed from CFD – develop the structure from here
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Aerofoil Section
Chord Length
0% 13% 40% 100%
Chord Length
At Root = 2680 mm
At Tip = 1390 mm
Pressure values were given at 0, 13, 40
and 100 percent of chord length
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Pressure Distribution
0
2000
4000
6000
8000
10000
12000
0 10 20 30 40 50 60 70 80 90 100
Chord Length (%)
Pre
ssu
re (
N/m
^2)
0 500 1000 1500 2000 2500 3000 3500 4000 4500
5000 5500 6000 6500 7000 7500 8000 8500 9000 9500
10000 10500 11000 11500 12000 12500 13000 13500
Wing Station (mm)
Pressure Distribution on Wing Stations
Vortex Lattice Method
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0% 13% 40% 100%
Loads – Flight Load
Pressure Distribution – Linear Interpolation
Cruise Conditions
Weight of Aircraft = 22000 Kg
Cruise Velocity = 510 Km/hr
Cruise Altitude = 25000 ft
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Fuel and Engine Loads
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Fuel Load = 1730 Kg per Wing
Fuel tank starts from 20% of first panel fuel tank ends at 85% of first panel
C.G location:
1.27 m from leading edge
2.5m wing root
Loads – Fuel Load
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Loads – Engine Load
Engine weight = 800 kg per engine
Located between 85% to 98% span of first panel
First Rib Second Rib
Front Spar 250 Kg 150 Kg
Rear Spar 250 Kg 150 Kg
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Iteration 1 Material Density Plot
Nature provides Stalk and Veins to support skins
Optimization follows nature – wants Spars and Ribs
Fuel Tank Region
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Bird Wings
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Objective: Minimize Wcomp
Constraints: Vol frac ≤ 0.3
Iteration 1 – Iso Density Plot
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Objective: Minimize Wcomp
Constraints: Vol frac ≤ 0.3
Extrusion Constraint
Non Design Region
Iteration 2
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Objective: Minimize Wcomp
Constraints: Vol frac ≤ 0.4
3 Extrusion Constraints
Non Design Region
Iteration 3
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Topology Optimization of Wing – Phase II
OB Flap Hinges
Aileron Hinges
Lugs
IB Flap Hinges
Proposed Geometry derived from initial topology iterations
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Material Density Plot - Spars
Side View
Box section for front spar and channel section for rear spar suggested
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Iso Density Plot for Spars > 0.3
Side View
Box section for front spar and channel section for rear spar suggested
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Aileron Hinges
OB Flap Hinges
IB Flap Hinges
Iso Density Plot for Hinges > 0.3
Predominantly V-shaped members for hinges, as usually practiced
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Material Density Plot – Mid Ribs
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Iso Density Plot – Nose Ribs
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Iso Density Plot – Mid Ribs > 0.3
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Iso Density Plot – End Ribs > 0.3
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Iso Density Plot – Front Ribs > 0.3
Truss pattern for the ribs suggested
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Final CAD Model Derived for the Wing
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Composite
• Consists of high strength and modulus fibers embedded in a matrix
or bonded to a matrix. Both the fibers and the matrix retain their
distinct properties and together they produce properties which
cannot be achieved individually.
• The fibers are usually the principal load carrying elements in the
composite and the purpose of the matrix is essentially to keep the
fibers in the desired location.
• The matrix also serves the purpose of protecting the fiber from heat,
corrosion and other environmental damages.
• The fibers may be glass, carbon, boron, silicon carbide, aluminum
oxide etc. One of the popular commercial fiber is Kevlar 49. These
fibers may be embedded in the matrix either in a continuous form or
in discontinuous form (chopped pieces of different lengths).
• The matrix usually consists of a polymer, metal or a ceramic.
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Laminate
• A laminate consists of several laminae (Plies) each with a fiber
oriented at a particular angle.
• This is generally made by stacking several thin layers of fibers
(Plies) at the desired locations and angles in a matrix and
consolidating them to give the required thickness.
• The fiber orientation in each thin layer can be arranged in a specific
manner so as to achieve the required properties of the structural
member.
• Since the fibers are of high strength in their axial direction and at the
same time very light compared to conventional metals, they find
many applications in aerospace, automobile industry etc.
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fmffmmff
mmff
c
c
mmffcc
mf
cmmmm
cffff
cmf
vvvv
AAA
AAA
PPP
EE
EE
1
1
0o Laminae – Load Parallel to Fibers
v is volume fraction
fmff
c
c vEvEE 111
12 is (major) Poisson’s ratiommffvv
12
E11 is longitudinal modulus
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0o Laminae – Load Perpendicular to Fibers
E22 is transverse modulus
21 is (major) Poisson’s ratio
fmmf
mf
vEvE
EEE
22
12
11
22
21
E
E
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0o Laminae – Shear Load
fmmf
mf
vGvG
GGG
12
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Orthotropic Material – Stiffness Matrix [C]
xy
xz
yz
zz
yy
xx
xy
xz
yz
zz
yy
xx
C
C
C
C
CC
CCC
66
55
44
33
2322
131211
00
000
000
000
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Orthotropic Material - Compliance Matrix [S]
xy
xz
yz
zz
yy
xx
xy
xz
yz
zz
yy
xx
S
S
S
S
SS
SSS
66
55
44
33
2322
131211
00
000
000
000
Altair Confidential
Orthotropic Material - Compliance Matrix [S]
xyxzyz
zz
yy
yz
yy
xx
xz
xx
xy
xx
GS
GS
GS
ES
ES
ES
ES
ES
ES
1
1
1
1
1
1
665544
33
2322
131211
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Specially Orthotropic Lamina
12
665544
33
23
22
22
13
11
12
12
11
11
1 0 0
0
0 1
0 1
GSSS
S
SE
S
SE
SE
S
12
22
11
12
22
11
12
11
12
22
11
0
0
0
1
0
000
0000
00001
00001
0
0
0
G
E
EE
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Angle Ply Lamina
sin
cos
n
m
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Angle Ply Lamina
xy
xx
yy
yx
xxxy
xy
yy
xx
E
E
nmGEEE
E
nmGEEGG
E
mnm
EGE
n
E
E
nnm
EGE
m
E
22
122211
12
11
12
22
122211
12
12
22
4
22
11
12
1211
4
22
4
22
11
12
1211
4
1121
11214
11
211
211
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Angle Ply Lamina – Stress Strain Relations
Altair Confidential
Angle Ply Lamina – Stress Strain Relations
xy
yy
xx
xy
yy
xy
yy
xx
xy
xx
xy
xx
xy
yy
xx
G
EE
EEE
1
1
1
mnnmEGE
nm
E
mnE
mnnmEGE
mn
E
nmE
xx
xy
xyyyxx
yyyx
xx
xy
xyyyxx
xxxy
22
33
22
33
2122
2122
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Composite Optimization Stages
• Free-sizing optimization
• Sizing optimization
• Ply-stacking optimization
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Free Sizing
Composite free-sizing optimization is to create design concepts that utilize all the potentials
of a composite structure where both structure and material can be designed simultaneously.
By varying the thickness of each ply with a particular fiber orientation for every element, the
total laminate thickness can change ‘continuously’ throughout the structure, and at the same
time, the optimal composition of the composite laminate at every point (element) is achieved
simultaneously.
Manufacturing constraints like lower and upper bound thickness on the laminate, individual
orientations and thickness balance between two given orientations can be defined.
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• Free size optimization was performed to
determine the thickness and laminate
family within the chosen regions of the
CAD model.
• The wing is divided in to regions for size
optimization as shown.
• Objective functions in this optimization
are mass and compliance and
minimization of the same.
Free Size Optimization
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Design Space: Ribs Material
Suggested minimum number of layers with orientation
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CFRP Properties
Symbol Units Properties
E E1 N/mm2 1.52×105
E E2 N/mm2 9650
G G12 N/mm2 5930
n NU12 0.321
r Rho Tonne/mm3 1.53×10-9
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Phase I - Concept: Free-Size or Topology optimization
Wing Ribs – Ply1
Wing Ribs – Ply4Wing Ribs – Ply3
Wing Ribs – Ply2
Max Thickness 10.16 mm Max Thickness 10.16 mm
Max Thickness 10.16 mm Max Thickness 10.16 mm
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Sizing Optimization
Sizing optimization is performed to control the thickness of each ply bundle, while
considering all design responses and optional manufacturing constraints. Ply thicknesses are
directly selected as design variables.
Composite plies are shuffled to determine the optimal stacking sequence for the given design
optimization problem while also satisfying manufacturing constraints like control on number
of successive plies of same orientation, pairing 45° and -45° orientations together etc.
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Level setting Ply-Bundles (+45°/-45° plies)Level setting Ply-Bundles (+0° plies)
Level setting Ply-Bundles (+90° plies)
0
90
45
-45
Illustration of Super-Ply Ply-Bundle Sizing optimization
Bundle 1 Bundle 2
Bundle 3 Bundle 4
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Phase 2: Ply-Bundle Sizing with Ply-Based FEA
modeling
• The size optimization of the Plies obtained in Phase 1 with Free Size
or Topology optimization was next performed to determine the
thickness and laminate family within all the Ribs, Skin and Spars.
• Objective functions are again mass and compliance and
minimization of the same.
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Phase II - System: Ply-Bundle Sizing optimization
Super Ply thickness Angle +45oSuper Ply thickness Angle 90o
Super Ply thickness Angle -45oSuper Ply thickness Angle 0o
Max Thickness 3.81 mm
Max Thickness 2.54 mm
Max Thickness 2.54 mm
Max Thickness 5.08 mm
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Max Thicknesses mm of Super-Plies in Ribs
Super Ply Angle Max Thickness
00 3.81
450 2.54
-450 2.54
900 5.08
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So far
• A review of the design process up to now reveals that we
established the optimum ply shape and patch locations in phase 1
(free size optimization) and subsequently optimized the ply bundle
thicknesses in phase 2 (ply bundle sizing optimization), allowing us
to determine the required number of plies.
• These ply bundles represent the Optimal Ply Shapes (Coverage
Zones).
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Optimal Ply Shapes (Coverage Zones): 0 Deg
Ply thickness Angle 0o
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Ply thickness Angle -45o
Optimal Ply Shapes (Coverage Zones): -45 Deg
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Ply thickness Angle +45o
Optimal Ply Shapes (Coverage Zones): +45 Deg
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Ply thickness Angle 90o
Optimal Ply Shapes (Coverage Zones): 90 Deg
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Optimal Ply shapes of Super-Plies in Ribs
Super Ply
Angle
Max
Thickness
Optimal Plies
00 3.81 3×1.27+1×0
450 2.54 2×1.27+2×0
-450 2.54 2×1.27+2×0
900 5.08 4×1.27
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Total Optimal Ply Shapes and thickness: Ribs
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Optimal Ply shapes of Super-Plies in Ribs
Super Ply
Angle
Max
Thickness
Optimal
Plies
Total Max
Thickness
00 3.81 3×1.27+1×0 3.81
450 2.54 2×1.27+2×0 2.54
-450 2.54 2×1.27+2×0 2.54
900 5.08 4×1.27 5.08
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Composite free size/sizing Optimization
Smeared Superply LevelSuperply Level
0°
+45°
-45°
90°
0°
+45°
-45°
90°
Optimized Ply-Bundle
* * *
• Baseline model with Super ply
• Free Size Optimization (FSO)
• Ply-Bundle Size Optimization
• Final Laminate stacking
Phases
Nondimensional FS optimization Dimensional
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Illustration Final Laminate stacking
• Symmetric Stack Required
• Number of plies in any one direction placed sequentially in the stack is limited
• Stack is balanced, i.e. the number of 45º and -45º plies is the same.
• Outer plies for the laminate should contain a particular ply (ie. ±45º )
• Minimize the number of occurrences of the 0° to 90° (or 90° to 0°) change in any two adjacent plies.
• Minimize the number of occurrences of 45° to -45° (or -45° to 45°) change
inside the stack by putting one 0° or 90° ply between them
Typical Ply Level Manufacturing Rules
Sized Ply Bundles
Algorithm based Conversion
Hyper Shuffle
Into local ply configuration
45 -45 0 0 0
45 -45 45 90
90 -45 45 -45 0 0
-45 90 45
(a) Ply Level (b) Superply Level
Final Laminate Stacking
0°
+45°
-45°
90°
Optimized Ply-Bundle
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45°
-45°
0°
90°
PCOMP
STACK
Free-sizing
optimization
Sizing optimization Ply stacking optimization
OU
TP
UT
,FS
TO
SZ
OU
TP
UT
,SZ
TO
SH
Pre Design Detailed Design Validation
Phase III – HyperShuffle for detailed stacking design
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Hyper Shuffle for detailed stacking design
45°
-45°
0°
90°
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Optimized thickness for one of the ribs
Total ply thickness in the ribs
varies from 2.54 to 13.97 mm
Mass saving is around 35.7% for the Wing
For the Full Wing Structure:
Optimized Composite mass~1350kg
Original Al mass ~2100kg
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Phase I Free Sizing optimization of Spars
Ply thickness Angle 0o Ply thickness Angle -45o
Ply thickness Angle +45o Ply thickness Angle 90o
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Phase II Size Optimization of Spars
Ply thickness Angle 0o Ply thickness Angle -45o
Ply thickness Angle +45o Ply thickness Angle 90o
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Phase II – Total Size Optimization of Spars
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Phase I - Concept: Free-Size Topology Optimization
Skin with Integrated StringersPly thickness Angle 0o Ply thickness Angle -45o
Ply thickness Angle +45o Ply thickness Angle 90o
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Phase II – Size Optimization - Skin with Integrated Stringers
Ply thickness Angle 0o Ply thickness Angle -45o
Ply thickness Angle +45o Ply thickness Angle 90o
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Phase II – Total Size Optimization of Skin with Stringers
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Blade Root Shape Optimization
X
Y
Z X
Y
Z X
Y
Z
Blade
Wheel
LETE
Cyclic Symmetry
Boundary Conditions
Pressure faces
Pre-twisted 290 mm long 60 blades
Blade root bottom radius 248 mm
Using mapped meshing options a
solid element mesh with 8 nodes is
generated, by capturing all the
critical regions with finer mesh.
Mesh around the singularities, blade
and disc dovetail root fillet regions
at higher radius, where the peak
stresses are expected are captured
with 2 to 3 layers of elements with
element size as low as 0.235 mm.
305524 elements and 344129 nodes.
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1825 MPa at node
153608 Average
Stress 256 MPa
Elastic Analysis
Stress Concentration Factor 7.1289
sector of the disk with one
blade Common nodes on the
pressure faces at six positions,
where the load transfer between
blade and disc takes place are
joined together. The blade and
disc are assumed to be made up
of same material with Yield
stress of 585 MPa, Young’s
Modulus 210 GPa, Density 7900
Kg/m3 and Poisson’s Ratio 0.3.
Stress contour beyond yield
across 3 elements over a depth of
1.22 mm.
60
1
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Elasto Plastic Analysis
Peak von Mises stress 768 MPa
at a node 176017 in the same
region which is beyond the yield
value 585 MPa. Plastic region
has not changed from the simple
elastic analysis result.
Peak stress value dropped from
1825 MPa to a value 768 MPa
just above the yield.
The material in the root region
around the stress raiser location
flows thus easing the stress and
raising the strain in accordance to
the hardening law given.
The peak strain observed at the
node 153608 in the same region
closer to peak stress location is
0.0153.
0
100
200
300
400
500
600
700
800
900
1000
0 0.002 0.004 0.006 0.008 0.01 0.012
Strain
Str
ess (
MP
a)
EP
Elastic
768 MPa
Average Stress 216.86 MPa
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Altair OptiStruct Shape Optimization
Shape variables are generated using mesh morphing
technique in Altair HyperMesh. Using the baseline
finite element model a suitable number of shapes in
the vicinity of baseline consistent with the available
design space is defined by modifying the grid point
locations, which are saved as perturbation vectors.
The shapes generated are combinations of
parameters shown. Shapes are then defined as
variables by assigning the lower and upper bounds
to it. Table gives the minimum and maximum
values adopted for defining the shape variables.
Shape variables can then be assigned as indicated to
perturbation vectors, which control the shape of the
model within a given bound. This is helpful in
generating the required shape bounds without re-
meshing the model. A shape optimization is then
carried out using OptiStruct code.
R2
R1
θ
W1
H
VW2
R2
R1
θ
W1
H
VW2
Minimum Value (mm) Maximum Value (mm)
W1 = 22.17 W1 = 25.76
W2 = 13.65 W2 = 13.86
R1 = 1.70, H = 5.67,
V = 4.13, R2 = 4.0
R1 = 2.14, H = 4.85,
V = 4.06, R2 = 3.37
θ = 29.860
θ = 16.250
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Mesh Morphing with Design Variables
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Mesh Morphing with Design Variables
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Altair OptiStruct Shape Optimization
OptiStruct uses an iterative procedure known as the local approximation method to
solve the optimization problem. The design update is computed using the solution
of an approximate optimization problem, which is established using the sensitivity
information. OptiStruct has three different methods implemented: the optimality
criteria method, a dual method, and a primal feasible directions method. The primal
method is more common in shape optimizations. This approach is based on the
assumption that only small changes occur in the design with each optimization
step. This method determines the solution of the optimization problem using the
following steps:
1. Analysis of the physical problem using finite elements.
2. Convergence test, whether or not the convergence is achieved.
3. Design sensitivity analysis.
4. Solution of an approximate optimization problem formulated using the
sensitivity information.
5. Back to 1.
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Altair OptiStruct Shape Optimization
323
MPa
1466
MPaBaseline Configuration
(mm)
Optimized Shape (mm)
4000RPM
Optimized Shape (mm)
8500RPM
W1 = 22.17 W1 = 25.72 W1 = 25.72
W2=13.65 W2 = 13.86 W2 = 13.86
R1 = 1.70, H = 5.67,
V = 4.13, R2 = 4.0
R1 =1.95, H = 5.05,
V = 4.03, R2 = 3.97
R1 = 2.10, H = 4.91,
V = 4.04, R2 = 3.98
θ = 29.860
θ = 16.250
θ = 16.250
Stress Concentration Factor 5.73 as
against 7.1289 of baseline. This
reduction enhances life considerably
Optimized Shape
Baseline Shape
Region of
interest
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Optimization through Altair HyperStudy
Altair HyperStudy is a multipurpose
DOE/Optimization/stochastic tool that
can be applied in the multi-disciplinary
optimization of a design combining
different analysis types. Once the finite
element model and shape variables are
developed, an optimization can be
performed by linking HyperStudy to a
particular solver of choice that can
include nonlinear analyses.
HyperStudy uses global optimization
methods which is very general in that
they can be used with any analysis
code, including non-linear analysis
codes.
Global optimization methods use higher order
polynomials to approximate the original
structural optimization problem over a wide
range of design variables. The polynomial
approximation techniques are referred to as
Response Surface methods. A sequential
response surface method approach is used in
which, the objective and constraint functions
are approximated in terms of design variables
using a second order polynomial. One can
create a sequential response surface update by
linear steps or by quadratic response surfaces.
The process can also be used for non-linear
physics and experimental analysis using wrap-
around software, which can link with various
solvers.
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Optimization through Altair HyperStudy
Shape optimization is carried by using the
baseline model, having the cyclic symmetry
boundary conditions imposed on the disc, with
the objective to minimize the peak stresses.
Shape variables generated in the previous
section are used as design variables.
Optimization is carried out at two speeds,
4000 and 8500 RPM, with elastic properties.
Maximum stress has decreased from 404 to
325 MPa by 79 MPa (19.5% as against 20%
achieved in Optistruct) from baseline for 4000
RPM and from 1825 to 1501 MPa by 325 MPa
(17.7% as against 19.5% achieved in
Optistruct) for 8500 RPM from complete
elastic analysis. Note that the analysis in this
study is more accurate as the cyclic symmetry
conditions are directly applied instead of cut
boundary conditions in Optistruct analysis.
325
MPa
1501
MPa
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Optimization through Altair HyperStudy
Variation of Objective and Shape variables
during optimization
Optimized Shape
Baseline Shape
Region of
interest
Objective
value
Shape
Variables
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EP Optimization through Altair HyperStudy 8500 RPM
Maximum stress decreased marginally from 768 to 746 MPa by 22 MPa (2.86%) from
baseline elasto-plastic analysis for 8500 RPM; however the peak plastic strains reduced
from 0.0153 to 0.01126 by 26.4%. This is the major advantage in optimization for a blade
root shape. Many existing machines have roots designed by experience and there can be
considerable margin in lowering peak strains and therefore enhanced life.
• Von Mises Stress 746 MPa
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Fatigue Stress Concentration Factor
7.5256
1466
Nominal
Max S
SKt
r
KK
N
tf
1
11
N
6.4fK
ω = flank angle = 30 deg (At fillet region)
r = notch radius = 1.75 mm (At fillet region)
= Neuber’s parameter = 0.12 mm
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Nominal Stress Range
S
Peak steady stress = 0.9547 MPa
Peak dynamic stress = 0.9547 x 221.239
= 211.2168 MPa
Average von Mises stress = 0.13373 x 221.239
= 29.586 MPa
Alternating nominal stress range = 2 x 29.586
= 59.1725 MPa
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Local Stress and Strain and Life
'/12
'2
12
1n
f
KEE
SK
E
SK f
2
= 270 MPa
= 0.00125
cif
b
imf NNE
221
2
1 ''
Ni = 8.7E+06 cycles
At 344.50707 Hz life of the blade is 420.9 minutes which is 4.14 times the base line
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Weight Optimization – CAD Model
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Blade and Disk Separated
46970 Solid 45 elements
41811 nodes.106066 Solid 45 elements
121948 nodes.
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Surfaces constrained
using constrained
equations so as to
have cyclic symmetry.
This surface is constrained in all dofs.
ωz =
1156.62 rad/sec
Boundary Conditions
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Max. Von Mises Stress
787 MPaMax. Von Mises Stress
721 MPa
Baseline Results
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R
Blade Root and Shank
8 holes radius 1.75 mm provided in root and two cutouts in shank are allowed to
reduce the weight.
The blade root without any cutouts was 7890.34 mm3 and chosen as Objective
function and minimized subject to the peak stress limited to yield 820 MPa.
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W1b
D1W1a
Variable Range mm
D1 1.1 to 2.0
D2 1.1 to 2.0
W1a 4.75 to 6.5
W1b 13.94 to 15.5
W2a 4.44 to 6.0
W2b 13.64 to 16.0
R 1.75 to 2.25
Design Variables
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Variable Value mm
D1 1.64
D2 1.64
W1a 5.09
W1b 15.35
W2a 5.57
W2b 14.56
R 2.0
Optimization
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Max. Von Mises Stress
810 MPa
Max. Von Mises Stress
798 MPa
Optimized Results
Volume decreased from 7890.34 to 7098.93 mm3,
i.e., a reduction of 10.03%.
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Thank You
Any Questions?