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OPTIMAL DESIGN OF A CLASS OF WELDED BEAMSTRUCTURES BASED ON DESIGN FOR LATITUDE.
Item Type text; Thesis-Reproduction (electronic)
Authors Gim, Gwang-Hun.
Publisher The University of Arizona.
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1323201
GIM, GWANG-HUN
OPTIMAL DESIGN OF A CLASS OF WELDED BEAM STRUCTURES BASED ON DESIGN FOR LATITUDE
THE UNIVERSITY OF ARIZONA M.S. 1984
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OPTIMAL DESIGN OP A CLASS
OF WELDED BEAM STRUCTURES
BASED ON DESIGN FOR LATITUDE
BY
Gwang-Hun Gim
A Thesis Submitted to the Faculty of the
DEPARTMENT OF AEROSPACE AND MECHANICAL ENGINEERING
In Partial Fulfillment of the Requirements For the Degree of
MASTER OF SCIENCE WITH A MAJOR IN MECHANICAL ENGINEERING
In the Graduate College
THE UNIVERSITY OF ARIZONA
19 6 4
-
STATEMENT BY AUTHOR
This thesis has been submitted in partial fulfillment of requirements for an advanced degree at The University of Arizona and is deposited in the Univesity Library to be made available to borrowers under rules of the Library.
Brief quotations from this thesis are allowable without special permission, provided that accurate acknowledgment of source is made. Requests for permission for extended quotation from or reproduction of this manuscript in whole or in part may be granted by the head of the major department or the Dean of the Graduate College when in his judgment the proposed use of the material is in the interests of scholarship. In all other instances, however, permission must be obtained from the author.
SIGNED: /^5^/c
APPROVAL BY THESIS DIRECTOR
This thesis has been approved on the date shown below:
May 9, 1984
K.£)M. Ragsdell Professor of Aerospace and Mechanical
Date
-
ACKNOWLEDGMENTS
The author wishes to thank Dr. K. M. Ragsdell,
Director of the Design Optimization Laboratory, for his
encouragement, guidance, and particularly for the insights
gained from discussions and hours of instruction. I am also
grateful to Dr. Don Claussing of Xerox Corporation for
leading us to the important area of design for latitude,
and for their support of the Design Optimization
Laboratory. 1 thank the other industrial sponsors of the
Laboratory (including Honeywell and IBM) as well for
providing much needed support which makes the research
environment of the Laboratory possible.
I am grateful for the support and encouragement of
Dr. Sangchul Kim, Dr. Yongchul Cho, Professor Sangug An,
Dr. Cnolhee Pak, Dr. Chongbo Kim, Dr. Yongsung Kim, Mr.
Sanghyuk Lee, and my other professors at Inha University,
Korea. Finally may I acknowledge the support and
encouragement of my father and mother, and other family
members and friends.
iii
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TABLE OF CONTENTS
Page
LIST OF ILLUSTRATIONS vi
LIST OF TABLES viii
ABSTRACT ix
1. INTRODUCTION 1
2. THE WELDED BEAM 5
2.1 Wela Shear Stress 7 2.2 Bar Bending Stress 10 2.3 Bar Buckling Load 10 2.4 Bar Deflection 11
3. FUNCTIONAL CONSTRAINTS 12
3.1 Constraints in General Forms 12 3.2 Dominant Constraints 14
3.2-1 The first constraint 15 3.2-2 The second constraint 16 3.2-3 The third constraint 17 3.2-4 The fourth constraint 18 3.2-5 The fifth constraint 19 3.2-6 Dominant constraints 20
4. OBJECTIVE FUNCTIONS 22
4.1 Objective Function for Sensitivity of a Design Object 23
4.2 Objective Function for Design Cost . . 27 4.2-1 Welding labor cost 27 4.2-2 Material Cost 28
5. TRADE-OFF STUDY 2 9
5.1 A Trade-off Curve 31 5.1-1 Method of specifications .... 31 5.1-2 Method of decomposition 32
iv
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TABLE OF CONTENTS—Continued
v
Page
5.2 Lagrange's Interpolation Formula .... 36 5.2-1 The error of the Lagrangian
formula 36 5.3 Newton's Method 39
5.3-1 Convergence of an iteration process 4-2
5.4 A Compromise Solution 44.
6. GENERALIZED REDUCED GRADIENT METHOD 50
7. NLP FORMULATION 54.
8. RESULTS 56
9. CONCLUSION 76
APPENDIX A: OBJECTIVE FUNCTIONS AWD CONSTRAINTS WITH RESPECT TO VARIATION OF UNCONTROLLABLE PARAMETERS BASED ON DESIGN VARIABLES 77
APPENDIX B: CONTOURS OF F. : SENSITIVITY BASED ON DESIGN VARIABLES 83
LIST OF REFERENCES 87
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LIST OF ILLUSTRATIONS
Figure Page
1. Welded Beam Structure 6
2. Weld Shear Stress 8
3. Characteristics of a Trade-off Curve Obtained by a Method of Specifications 33
4. Characteristics of a Trade-off Curve Obtained by a Method of Decomposition 34
5. Newton's Method AO
6. Flowchart of Newton's Method Algorithm . ... 4-1
7. Optimization Problem to find the minimum Distance from Utopia Point to Pareto-Minimal Set A5
8. Strategy for Reduced Gradient Method 51
9. Basic Flowchart of Reduced Gradient Algorithm, OPT, for Fully Constrainted Problem .... 53
10. First Objective Function: Sensitivity with respect to Variation of Uncontrollable Parameters 57
11. Second Objective Function: Design Cost with respect to Variation of Uncontrollable Parameters 58
12. First Dominant Constraint with respect to Variation of Uncontrollable Parameters ... 59
13. Second Dominant Constraint with respect to Variation of Uncontrollable Parameters ... 60
vi
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LIST OF ILLUSTRATIONS—Continued
vii
Figure Page
14. Fourth Dominant Constraint with respect to Variation of Uncontrollable Parameters . . . 61
15. Fifth Dominant Constraint with respect to Variation of Uncontrollable Parameters ... 62
16. Contours of F^ and All Dominant Constraints with respect to x^ and 64-
17. Contours of F^: Sensitivity with respect to x^ and x2 65
18. Contours of F.: Sensitivity with respect to and x^ 66
19. Contours of FDesign Cost with respect to x- and x, for the Case satisfying Minimum Sensitivity 67
20. Contours of Fp: Design Cost with respect to x2 and Xo for the Actual Case Minimizing only Design Cost 68
21. Contours of Fp: Design Cost with respect to x^ and xj for the Actual Case Minimizing only Design Cost 69
22. Trade-off Curve of a Welded Beam Obtained by Method of Specifications at v = .05. . 71
23. Trade-off Curve of a Welded Beam Obtained by Method of Decomposition with F = W-| F-j jj + W2?2N an
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LIST OF TABLES
Table Page
1. Utopia Point Obtained by a Method of Decomposition, F = W-j F-] n + W2F2N' (v = •®5)« • 74
2. The Chosen Data Point for Lagrange's Interpolation Polynomial, (v = .05) 74
3. Compromise Solution and the Related Design Variables, (v = .05) 74.
viii
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ABSTRACT
The traditional optimal design approach has
employed a single objective such as cost, weight, or
reliability. In this thesis, we examine a new approach
called Design for Latitude, where we seek to minimize
sensitivity to changes in uncontrollable parameters. This
new approach is demonstrated by application to the well
known welded beam problem of Ragsdell and Phillips. Next we
examine strategies for trading off cost and sensitivity in
a dual objective formulation. These studies require
identification of dominant constraints using the Wilde and
Papalambros regional monotonicity concepts. The resulting
nonlinear programs are solved using the powerful
generalized reduced gradient code, OPT. The numerical
results suggest the possibility of very useful compromise
between cost and latitude.
ix
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CHAPTER 1
INTRODUCTION
Nonlinear programming problems are frequently
encountered in many design activities, especially in the
design of machine elements and systems. The conventional
factor of safety concept in the design of machine elements
and systems has several limitations when material
properties, applied loads, assembly conditions, and other
parameters must be treated simultaneously or have random
characteristics. It appears that mechanical design problems
are best treated using now relatively well developed
nonlinear programming methods.
An optimal design for minimizing cost, volume,
weight, error, or operating time, so far, has been a
traditional optimization problem. The optimal design of
a welded beam for minimizing design cost was previously
examined by Ragsdell and Phillips (1976) for the case of
selected bar and weld materials and by G. Gim (1983) for
three different cases. These cases were (1) optimizing
design variables with chosen materials, (2) optimizing the
variables with six kinds of standard sizes, four kinds of
1
-
2
veld material, and four kinds of bar material, and (3)
combining (1) and (2). The optimal design performed by
minimizing the factors related to design cost may easily
fail to remain within the feasible region of given
constraints if variations of uncontrollable parameters are
present. Tnat is, a design object optimized by minimizing
design cost factors is usually very sensitive to these
variations.
The functional constraints are the relationships
between design variables for the feasible region of the
design to support applied loads. In case uncontrollable
parameters have variation from negative to positive values,
some of the constraints are more sensitive than others to
these uncontrollable parameters. Therefore, the worst case
for the optimal design should be chosen from all possible
cases whicn are caused by variations of uncontrollable
parameters. In other words, dominant constraints must be
selected for the worst case among all constraints which
include the variations.
Design for latitude means minimizing sensitivity of
a design object in the presence of variation of
uncontrollable parameters. The design for latitude
objective is formulated as the squared sum of the rate of
change of constraint values with respect to changes in
-
3
uncontrollable parameters. Since cost also is an important
factor as well as sensitivity of a design object, another
objective function for cost is considered. The design cost
for welded beam structure has two main components: (1)
welding labor cost and (2) material cost.
These two objectives conflict in the sense that
minimal sensitivity causes maximal design cost for the
welded beam structure. The best choice for the optimal
design can be made using a trade-off between these
contrasting objectives. To satisfy the multiple-criteria,
we examine two methods to choose design variables
satisfying both minimal sensitivity and design cost: (1)
method of specifications and (2) method of decomposition.
After the trade-off curve is constructed using the
method of decomposition, the compromise solution concept of
Salakvadze (1979) can be used to select the final design.
The compromise solution is obtained by drawing a line from
the Utopia point so that it enters perpendicular to the
Pareto-minimal set. An optimization problem is formulated
to find the closest point on the Pareto-minimal set from
the Utopia point and solved using the "maximum principal"
(Leitmann 1981) after a Lagrangian interpolation polynomial
is formed based on the Pareto-minimal set which is obtained
-
4
with different weighting factors selected suitably in the
method of decomposition.
This thesis shows how to minimize sensitivity
(maximize stability) of a design object (that is, design
for latitude) if variations of uncontrollable parameters
exist. With dominant constraints selected, two objective
functions for sensitivity of a design object and design
cost are formulated for a NLP problem, which is solved by
using the Generalized Reduced Gradient code, OPT (Gabriele
and Ragsdell 1976), and using a trade-off curve and the
compromise solution concept for the best solution
satisfying both minimal sensitivity and design cost.
Through current research, it is realized not only that
minimizing sensitivity of a design object is efficiently
performed, but also that the sensitivity is one of the most
important factors for an optimal design as well as design
cost.
-
CHAPTER 2
THE WELDED BEAM
In the practical design activities of machine
elements and systems, the problem of welded beam structure
is frequently encountered. Consider a welded beam, shown in
Figure 1, which is composed of bar and weld materials. The
properties , (T^, P, L, E, G, and Df are design parameters
which are assumed to vary without control, called
"uncontrollable parameters". h, 1, t, and b are design
variables used to satisfy the constraints and reduce the
objectives.
That is,
Design Variables:
x = lx-| ,X2 ,X3 ,x^ ]T (2.1)
x = lh,l,t,b]T
Uncontrollable Parameters;
u = lui ,U2 ,U3 ,u^ ,U5 ,u6 »u7]t (2.2)
where,
u = IT , (T ,P,L,E,G,D 1 T d d f
T d : d e s i g n s h e a r s t r e s s o f w e l d
-
p p
r B 1 L L
1
L
1
A
L
I H» P" 3
F i g u r e 1 W e l d e d B e a m S t r u c t u r e .
CT>
-
(Td
E
G
D _
design normal stress for beam material
Young's Modulus
Shearing modulus
design deflection
We assume that uncontrollable parameters may vary over the
range + v.
A welded beam structure has four principle failure
properties: (1) weld shear stress, (2) bar bending stress,
(3) bar buckling, and (4) bar deflection.
2.1 Weld Shear Stress
The weld shear stress (Shigley 1977) has two
components, X ' and x " t where "['is the primary shear stress
_ '/ acting over the weld throat area and t is a secondary
torsional stress, shown in figure 2.
-
T t / 2
V
H L
1/2-
F i g u r e 2 W e l d S h e a r
-
9
MR P(L + .51)(.51)
r i i _ x v ** J J
„ U q (U / + .5X2)X2 T (2.4)
y 2 0
MR P(L + .51)(.5t) -r* i ' _ j _ _____________
x 3 3
u3(u^ + .5X2)X3 X. = —— (2.5) x 2 3
where,
Xy' = y directional primary shear stress
= y directional secondary torsional stress
T " = x directional secondary torsional stress x
J = polar moment of inertia of weld group
3 2 i r + 3it
j -r 2»
6 JT
-
10
Therefore, the weld stress becomes:
1 ° J t x + t y
T - [ z + i y > z
2.2 Bar Bending Stress
The maximum bending stress is
MC PLt/2 (T = — =
( 2 . 6 )
I bt3/12
6u0u, (T--J-4- (2.7)
X3X4
2.3 Bar Buckling Load
in the case of a narrow rectangular cross section
where b/t is a small quantity, the approximate formula for
calculating the critical load can be put in the form
(Timoshenko 1961) :
• cr
4.013 E1C t — ( 1 - —
2L
EI
-
11
where,
4.013] U5IC
cr U "
(1 -12. 2u
u el ( 2 . 8 )
I = x3X^/12
C = x .x-^.u J'5 3 A o
2.4 Bar Deflection
To calculate the deflection, assume the bar to be a
cantilever of length L.
Thus,
PL? DEL =
DEL =
3EI 3Ebt3/12
4u3u2
U5X4X 3
(2.9)
-
CHAPTER 3
FUNCTIONAL CONSTRAINTS
The various failure conditions considered; namely,
due to combined stress in the weld, bar bending stress, bar
buckling, and excessive deflection are prevented by
application of inequality constraints which are functions
of the design variables and uncontrollable parameters. The
combined effect of simultaneous variation of the
uncontrollable parameters is difficult to predict. It is
possible that a particular constraint will be less
restrictive (i.e. increase the feasible set) while another
will be more restrictive (decrease the feasible set) when
the uncontrollable parameters do indeed vary. These trends
must be predicted in a meaningful design for latitude
formulation. Accordingly, we use monotonicity analysis to
select the "worst case" constraint set.
3.1 Constraints in General Forms
In the case of no variation of uncontrollable
parameters, 5 inequality constraints are in the form:
g^(x,u) = u1 - T(x-j »*2'x3 ,u3 ,UA) - 0 (3-1)
12
-
Where,
13
g2(x,u) = u2 - (r(x3,x^,u3,uA) > 0 (3.2)
g^(x) = x^, - x1 > 0 (3.3)
g^(x,u) = Pcr (x^x^u^u^u^) - u3 > 0 (3.4)
g5(x,u) = u? - DEL(x3,x^,u3,u^,u5) > 0 (3.5)
"Cu ,u) = maximum shear stress in weld
0"(x,u) = maximum normal stress in beam
Pcr(x,u) = bar buckling load
DEL(x,u) = bar end deflection
In addition, the design variables have lower and upper
bounds:
(3.6)
hl
VI
X1
VI
hu
*1 < x2 <
< x3 <
bl < x4 < bu
-
14
3.2 Dominant Constraints
Provided that variations of uncontrollable
parameters exist, dominant constraints have to be chosen
for the worst case among all constraints which include each
variation of uncontrollable parameters. Here we use
"detection of monotonic properties" as given by Papalambros
and Wilde (1980).
The model is put in the normalized form:
(3.7)
j = 1, • • • , J
Rj * 1
If • > 0 ; (3.8)
then is increasing with respect to uj
Tnat is, u^ is dominant; Rj = +
(«i )
If 9 R j
< 0 ; (3.9)
then R. is decreasing with respect to u^ then R. J
That is,
t where ui
-
15
3.2-1 The first dominant constraint
ll > 1 (3.10)
Normalize ,
then,
R!
T "2 + (T ' + T ")' L x L y L.y < 1 (3.11)
*1
Differentiate with respect to uncontrollable parameters.
Then,
(a) 3*
du.
1 ti'2 + *It + X;1) < 0 (3.12)
(b) 3*1
3»3 2"lJti'2 + It; + ty'>
, , > 0 I I \
(3.13)
where,
Q1 = 1 I I X
x3 (u4 + -5x2)
+ + x^') i jy x2(u^ + .5X2)
x.x 1*2
-
16
^ U 3 X 3 _ u 3 x 2 12 X-x ' — + ^ ( Xy + Ty ' ) j
3R, 2J y y 2J (c) IZIZ==ZZ=====I===I=^,-• > 0 (3.14)
3u
^ 2ulJ"^x'2 + (ty + "^y')2
Thus,
- + +
R-j = R-i (x,u-| ,U3 ,u^) (3.15)
and dominant constraint of g_^(x,u) becomes:
- + +
91 = 91 (x'u1 'u3'u^} (3.16)
That is, the worst case with respect to constraint one is
when u-| decreases, and u^ and u^ increase simultaneously.
U£, u^, u^, and u-y have no effect on constraint one.
3.2-2 The second constraint
6iuu/ g (x,u) = u ^-r-> 0 (3.17)
*A*3 '
Normalize g2
then,
6u~u, r2 V- < 1
X X u X A 3 2
-
17
Differentiate R2 with respect to uncontrollable parameters.
Then,
3r2 ^^3^/ (a) 2^ < 0 (3.19)
3U2 X4-X3U2
9r2 = 6uA
3u3 x^x3u2
(b) ^ >0 (3.20)
3R2 6UO (c) ^ > 0 (3.21)
au^ x^x3u2
Thus,
r2 = r2
-
18
3.2-4 The fourth constraint
4.013xo*^ X3U5 g lx,u) -(UcU^ ) - u3 > 0 (3.25)
6ut 4uA
Normalize g. , 4
then,
o/ 2 24u,Uo R, = * — $ 1 (3.26)
4.013x^x|(4u^ u^u^ - x^u^)
Differentiate R^ with respect to uncontrollable parameters.
Then,
3R, 24u? (a) Sl = = > 0 (3.27)
3u^ 4.013x^x^(4u^ - X3U5)
2 3R; 96U;Uo(2U; UcUi - XqUt)
(b) ^ 43 5 " 2J > 0 ,3.28) 3u^ 4.013x3x^ (4u^ U5U5 - X 3 U 5 )
3 dR/ 24u^u3(2u^ u6/u5 - x3)
(c) - « ^ < 0 (3.29) 4 . 0 1 3 x ^ x ^ ( 4 u ^ u ^ U £ , - X 3 U 5 )
3 3R^ 24u^u3(2u^ U5/U6)
(d) 3 s- < 0 (3.30) 3u6 4.013x3x^ (4u^ u5u£, - *3*5)
-
19
Thus,
+ + - -r4 = R4(x,u3,u4,u5,u6) (3.31)
and dominant constraint of g^(x,u) becomes:
+ + - -g4 = g4 (x,u3 'uvu5'u6> (3.32)
3.2-5 The fifth Constraint
„ 3 4u3
9r (x ,u) = u7 3 > 0 (3.33)
U5X4-X3
Normalize g_ , 5
then,
„ 3 4u3uA Rr = 3 0 (3.35)
3U3 X^U5U7
3R;- 12u^,u^ (b) J 4 - > 0 (3.36)
au^ *Ax§u5u7
-
20
3 3Rr 4UOU/
(c) 2_= yl
-
21
All dominant constraints are finally put in the worst case
form:
(a) g1 (x,u1,u3,u^) = !U1 - f + sy >- (3.41)
where,
Sx "
V- | (V- ] + .5X2)
2J
V 1 U 3 v1u3x2(v1uii + .5x 2 ) S = +
2x-|x2 2J
2 2 X1X2*X2 + 3x3>
(J — """""" 6j2~
6v*u„u
(b) ^2^x ,U2'U3'U^) * V 2 U 2 2 - 0 (3.42)
V3
(c) g^(x) = x^ - x1 > 0 (3.43)
3 , , 4.013x^x";v? x3uc;
(d) g U,u3,u ,u",uj) 4 fTft - ) - v,u3 > 0 * 6V1U, 4v-iU ,
1 A 1 ^ (3.44)
4V^u U"^ (e) g (xfu*#u1",u~,u") = v„u 3 4 > 0 (3.45)
5 3 4 i > / 2 / v u x x 3 " 2 5 4-3
-
CHAPTER 4
OBJECTIVE FUNCTIONS
For optimal design, design criteria should be
selected first on the basis of which the performance or
design of the system can be evaluated so that the "best"
design or set of operating conditions can be identified.
Cost, so far, has been a traditional objective for numerous
problems. However, the optimal design performed by
minimizing the factors related to cost may easily fail to
remain within the feasible region of given constraints in
case variations of uncontrollable parameters exist. In
other words, a design object optimized for the least cost
is usually very sensitive to these variations. Sensitivity
of a design object as well as design cost, therefore, is an
important factor in practical optimal design activities.
Consider two objective functions for (1) sensitivity of a
design object and (2) design cost.
22
-
23
4.1 Objective Function for Sensitivity of a Design Object
Assuming a feasible design exists, find the set of
design variables x^ , *2 ' x3 ' anc^ x4 w":i:'-ch gives the
smallest change in constraint function values for arbitrary
unit change in the uncontrollable parameters.
That is,
J I BR, 2 MIN: F1 (X,U) = £ZIZI 1H (4.1)
3=1 i=l dui
subject to gjj.(x,u) > 0 ; k = 1,2,3,. . • ,K
h^(x,u) =0 ; 1 = 1,2,3,• • • ,L
where
R- = normalized dominant constraint functions tj
= uncontrollable parameters
g^ = dominant inequality constraint functions
h-^ = dominant equality constraint functions
Since for the welded beam example considered here the third
constraint is independent of uncontrollable parameters, F^
becomes:
5 7 BR, 2 MIN: F-, (X,U) = nUZ 'L) (4.2)
j = l i = l j*3
-
24
3R, where —sL are given as follows:
aui
la) 3^
Bu.
2 2 Sx +
V2U1
(4.3)
where,
S = x
V^U^X^tV^U^ + .5X2)
23
S„ = v-jU^ v^u^xgtv-iu^ + -5x2)
2 x 1 x 2 2J
J =
2 „ 2 X-|X2(X2 + 3xo)
6 2
(b) Q1 6 R l
3^^ 2V2U-] + Sy (4.4)
where,
0 . Q ' M ' - 5 V 1 x J
2v v x (v u + .5x ) Syl J-+ —J—2 1-A SL-]
X . X 1 2
-
25
3R« Q?
lC) T~ = ^ 1 o 2" (4*5) du . 2v0u Js 2 + i 2 1J x y
where, 2 0
= V1U3X3 V1U3X2
x . i y
2 3R0 6v.i UnU,
(d) _2 1_3_L (4 6)
du2 V2U2X4.X3
dR2 6V^ u/ (e) = (4.7)
du3 v2u2xAx3
3R2 6v^U3 (f) = (4>8)
9u4 V2U2XAX3
3r4. 3̂ ( g ) = ( 4 . 9 )
3u3 u3^
where,
A 3 Q3 = 24V1U3U4
Q = 4.013x x3v (4v u u u - x u ) K 3 4 2 14 5 6 35
3r4 4Q3 (2v-[ u5u6 - X3U5) (h) (4.10)
au4 u4Q5
-
26
where,
= 4
^ 4. 013x^x^2
(i) 1*L= Q3(2v1UA Vu5 - x3> 9 u 5 Q 5
ID 1^1- 3Q6
U^Qy
d R 5 g 6 (m) i =
9 u 5 U ^ Q y
(4.11)
^ a3(2v1u^ "s /"f ,> u; _ " ^ (4.12)
3u6 Q5
R5 q6 (k) 1 = —2_
3u3 U3Q? (4,13)
where,
q6 = 4vtu3uI
&7 = V2X4.X3U5U7
(4.14)
(4.15)
-
27
4.2 Objective Function for Design Cost
The second objective function is total cost. The
major design cost components for such a weld assembly are:
(1) welding labor cost and (2) material cost.
F2(X,U) = C1 + C2 (4.17)
where,
C1 = welding labor cost
Co = material cost
4.2-1 Welding labor cost
Assume a welding labor rate of $12 per hour
(including operating and maintenance). Moreover, assume
that the machine can consistently lay down 6.54 cubic
inches of wela in an hour (Stewart 1981). This number does
not compare directly to that by Ragsdell and Phillips. The
labor cost C^, thus, becomes
C. = 1.835V (4.18) I W
C1 = 1.835x^ x2 $
where,
. 3 V = volume of weld material (in ) "W
2
-
28
4.2-2 Material Cost
Material cost contains two components: (1) weld
material and (2) bar material. Thus, material cost is:
C2 - CwVw + CBVB
where,
3 Cw = $ per volume of weld material ($/in )
3 Cg = $ per volume bar stock ($/in )
3 Vg = volume of bar (in )
= *3V\ + V Therefore, in the case of no variation of uncontrollable
parameters the objective function for design cost is:
F2 (x ,u) = C, + C2 (4.20)
= 1.835x^X 2 + C w x^x 2 + C B x 3 x A (u 4 + x 2 )
= (1.835 + Cw)x^x2 + CBx3xA(Uit + x2)
Assumming variations of uncontrollable parameters
exist, the objective function for design cost is put in the
form:
F2(X,U) = (1-835 + Cw)x^x2 + CBx3x^(Vlu^ + x2)
(4.21)
-
CHAPTER 5
TRADE-OFF STUDY
In optimization work the common practice is to use
an objective function that represents a single design
characteristic, such as cost, volume, weight, error, or
operating time, and so on. However, it frequently occurs in
practical applications that there is more than one design
characteristic which the design variables must satisty.
Very often these combined criteria are conflicting in the
sense that when one is increased for the optimal design,
the other is decreased. The best choice for the optimal
design can be made by using a trade-off (Siddall 1982)
between these contrasting design characteristics (objective
functions).
Trade-off curves have been proposed as a tool for
making the trade-off decision (Bartel and Marks 1974) , and
they do give considerable insight into the decision
problem. Trade-off curves can also be thought of as a plot
of optimum designs corresponding to variations in a design
specification.
29
-
30
After a trade-off curve is obtained, a compromise
solution (Vincent 1983) can be selected. To find the
compromise solution, four steps are needed:
(1) formulate Lagrange's interpolation polynomial of a
trade-off curve with the data points that are obtained
by suitably choosing and V«2 with the method of
decomposition.
(2) set up an optimization problem to find the minimal
distance from the Utopia point* to the Pareto-minimal
set**, and use the "maximum principle" for the optimal
solution.
*. A point G0gEr is a Utopia point if and only if for each i=l,2.3,• • »,r
G? = inf(G.iy) ly € Y}. i I
**. Definition of a Pareto-minimum (vector cost): A point y*€ Y is a Pareto-minimal point if and only if there does not exist a point y €_Y (y€BOY for local Parato-minimum) such that G(y) < G(y*). The notation < means "partially less than," that is, G^(y) < G^iy') for all i €. 11,• • «,r] and Gj (y) < Gj (y*) for at least one j € L1r * • *»rJ- The constraint set Y defined by Y = {y€Em such that g(y) =0 and h(y) > 0} where € is used to designate "an element of" and Em designates an m-dimensional space of real numbers. For each choice of y £ Y one or more objective functions may be defined by
G(y) = IG-| (y), • • • ,Gr (y) ] .
-
31
(3) using Newton's Method, find the compromise solution.
(4) suitably adjust and W2 in equation (5.4) to produce
the same objective value as the compromise solution;
then design variables , x2, x^/ and x^ can be
obtained simultaneously for a compromise solution.
5.1 A Trade-off Curve
Consider trade-off analysis for multiple-criteria,
minimizing sensitivity of a design object and design cost.
Two methods can be performed to decide design variables
satisfying minimal sensitivity and design cost: (1) method
of specifications and (2) method of decomposition.
5.1-1 Method of specifications
Trade-off curves give useful information on the
relationship of multiple-criteria and on certain
specifications. Specifications are interaction points with
other parts of the system, and a specification is commonly
an arbitray decision to permit suboptimization. When it is
possible to predict the penalty that is being paid in
trade-offs to achieve these specifications, the
specifications are usually subject to negotiation and are
really target values until the design progresses to the
final stages. By setting initial and final specifications
-
32
on the trade-off curves, the range of suitable design can
be chosen, as shown in Figure 3. The best solution can,
thereafter, be chosen from the available feasible designs.
5.1-2 Method of decomposition
There is always an interaction with other parts of
the device or system, to a greater or lesser extent. The
effort required to solve the total problem is minimized
when the system is decomposed into subsystems with least
interaction. The decomposition of a system uses the
interaction characteristics and divides the problem into
subproblems which can be handled more easily. We can,
thereafter, optimize a formulation of the whole system that
is composed of subproblems. In other words, the new
objective function composed of multiple-criteria can be
minimized to estabilish the best system design
specification. A trade-off curve can be formulated by
choosing suitable weighting factors, as shown in Figure 4.
-
33
F i n i a l S p e c i f i c a t i o n S e t t i n g
-
34
Pareto-minimal Set
/•^Compromise Solution
^N^Utopia Point
S E C O N D O P T I M I Z A T I O N C R I T E R I O N
F i g u r e 4 C h a r a c t e r i s t i c s b y M e t h o d o f
o f a T r a d e - o f f O e c o m p o s i t i o n .
C u r v e O b t a i n e d
-
35
That is,
MIN: F(x,u) (5.1)
where,
F(x/U) — W_| ^ + ^2^*2N (5.2)
or
1/F(x,u) = W^F^ + W2/F2N (5.3)
and V$2 are weighting factors of F^ and F2,
respectively;
W1 + W2 = 1 (5.4)
F^n and F2N are the normalized functions of F-j and
F„, respectively.
-
36
5.2 Lagrange's Interpolation Formula
When the independent values are not evenly spaced,
the Lagrangian polynomial (Gerald 1978) is used to fit a
polynomial based on the given data points. The Lagrangian
form is also the most straightforward way to get the
polynomial as an explicit function.
Suppose f(x) and x data pairs are given. The
Lagrangian formula then can be written in the form:
n n x
i=l j=l x± (5.5)
5.2-1 The error of the Lagrangian formula
The error of Pn(x) is zero at the n+1 values of x
that are fitted exactly.
That is,
E(x) = f(x) - Pn(x)
= (x-x1 ) (x-x2)« • • (x-xn+1 )g(x)
The auxiliary function W(t) is:
(5.6)
W(t) = f(t) - Pn(t)
- (t-x1 ) (t-x2 )• . (t-xn+1)g(x) ( 5 . 7 )
-
37
where W(t) = 0 for t = x-^xgr* * •Xn+i, and at t = x, for a
total of n+2 zeros.
Hence,
W (t) = 0
W ' - i t ) = 0
w(n+1)(t) = 0
Let 3^ be the value of t at which w^n+^) (t) = 0 and
xmin < ̂ < *max •
Then,
w(n+1) (^) = 0 = f(n+1) (^) - 0 - (n+1)Ig(x),
f ( n + 1 ) ( / } g (x) = z~
(n+1)1
The error then is:
£U+1)
E(x) = (x-x. ) (x-x9)... (x-x +1 ) (5.8) 1 ^ n 1 (n+1)!
The error can be bracketed between a maximum and a minimum
value only if we have information on the (n+l)st derivative
of the actual function f(x).
-
38
Finally, the Lagrangian formula can be used simply
to write out an interpolation polynomial. The main
advantages of the Lagrangian formula are two: (1) to find
any value of a function when the given values of the
independent variable are not equidistant, and (2) to find
the value of the independent variable corresponding to a
given value of the function.
-
39
5.3 Newton's Method
In practical engineering problems, finding roots of
a system of equations is frequently encountered. One of the
most widely used methods of solving equations is Newton's
method (Ragsdell 1982) because it is rapidly convergent at
least in the near neighborhood of a root, shown in Figure
5. The procedure is known as Newton-Raphson iteration. A
flowchart for Newton's method is given in Figure 6.
In Newton's method it is assumed at once that the
function f(x) is diferentiable. This implies that the graph
of f(x) has a definite slope at each point and hence a
unique tangent line. Starting from an initial estimate
which is not too far from a zero of the equation,
extrapolate along the tangent to its intersection with the
x-axis, and take that as the next approximation. This step
is continued until either the successive x-values are
sufficiently close, or the value of the function is
sufficiently near zero.
Consider the Taylor Series Expansion of f(x) about
a given point "x.
-
40
f(x)
F i g u r e 5 N e w t o n ' s M e t h o d .
-
41
(NEWT)
DEFINE: XO.N.EPSI
* •
XOLD = XO
< •
I " LL
• ITER = I
F ( X O L D ) X N E W = X O L D - { }
D F ( X O L D )
I S F ( X N E W ) | < E P S A L P H A = X N E W
X O L D = X N E W
F i g u r e 6 F l o w c h a r t o f N e w t o n ' s M e t h o d A l g o r i t h m .
-
42
~ _ 0 0 ( x ) ^
f(x) = f (x) + > ( ) (x - x)n (5.9) n=l n!
where "x is a point near x. Truncate all terms of degree
greater than one:
f (x") = f (x) + f' (x) (x - x) (5.10)
and force f ("x) to zero to get the formulation of Newton's
method,
~ - f ( * )
x — x (5.11) f' (x)
In general the iteration prescription is:
f (x^) x. = x — (5.12) J+1 J f'txj)
5.3-1 Convergence of an iteration process
Newton's Method is quadratically converged, in the
sense that the error of each step approaches proportionally
to the square of the error of the previous step. Consider a
nonlinear function of a single variable, f(x) in class C^
which has a single zero in the interval x fc (a,b).
-
43
Define a class of iteration algorithms of the form:
' 3 + 1 = 9Uj> (5.13)
Thus, from eqns. (5.12) and (5-13)
g(Xj) = X j -"x.i>
f'Uj)
f ' (Xi)f • ( X i ) - f ( X i)f ' ' ( X j ) • I X . ) = 1 i *
l f ' ( X j ) ]
f ( X j )f ' • ( X j )
I f ' ( X j ) ] 2
(5.14)
(5.15)
Successive iteration converge if lg'(x)| < 1.
Therefore,
an interval of convergence for Newton's method is defined
as:
f (x)f " (x)
Lf1(x)] < 1 (5.16)
The method will converge for any initial value x-| in the
interval. The condition is sufficient only if f(x) is
continuous and f'(x) exists.
-
44
5.4 k Compromise Solution
The compromise solution concept of Salakvadze
(1979) may give useful information on the best decision,or
the recommended solution for a final design choice. The
idea behind this concept is to find the "closest" point on
the Pareto-minimal set to a Utopia point (Vincent and
Grantham 1981) , shown in Figure 4. The closest point, the
compromise solution, on the Pareto-minimal set is obtained
in this case by drawing a line from the Utopia point so
that it enters perpendicular to the Pareto-minimal set.
For finding the compromise solution, set up an
optimization problem to get the minimal distance from the
Utopia point to the Pareto-minimal set on the trade-off
curve, shown in Figure 7.
That is,
Min: ^dt (5.17)
X| = cosU (5.18)
X2 = sinU (5.19)
with target 0= X2 - Pn (Xj ) = 0 (5.20)
where Pn (X-j ) is Lagrangian interpolation polynomial that is
obtained with n+1 numbers of given data points. These data
-
45
( X ° , X ° )
F i g u r e 7 O p t i m i z a t i o n P r o b l e m t o f i n d t h e m i n i m u m D i s t a n c e f r o m U t o p i a P o i n t t o P a r e t o - M i n i m a l S e t .
-
46
points are gained by setting different and in eqns.
(5.2) or (5.3).
Integrate (5.18) and (5.19), then
X1 = X° + (cosU)t (5.21)
x2 = X° + (sinU)t (5.22)
tanU = (X2 - X°)/(X1 - X°) (5.23)
Let's use "Maximum Principal" (Leitmann 1981) for an
optimal solution of eqns. (5.17) - (5.20).
H = o + A-jCOsU + 2sinU = 0 (5.24)
)\ o < 0 (5.25)
3H -Ai it) =— = 0
9X-,
J\-| (t) = A-1 = const (5.26)
dH -Aolt) = 0
3x 2
7l2(t) = }\ 2 = const (5.27)
Use a given terminal condition,
Ai(tf) (5.28) ^ X-]
-
47
\ D ̂ ® A2 (tf} =P (5.29)
9X2
From (5.26), (5.27), (5.28), and (5.29)
JN-, (tf > " (5.30)
^ 2 ( t f } = ̂ 2 ( 5 - 3 1 )
For the minimal solution,
3H * * -_^1sinU +^?cosU = 0 (5.32)
3U '
tanD* = ̂ - = (fl— )/($££-) (5.33)
-
48
or
* 0 * n (X1 " X1 )
X* = xO (5.37) 2 2 JPnlX^/ax-i
since
*• %
ae _ dix2 - pn(xi)i
ax2 dx2
= 1 (5.38)
96 _ aix2 - Pn (X1) ] _ 3Pn (^ )
3x1 ax-, ax-, (5.39)
To get X^ and ^ , substitute (5.37) into (5.20)
then,
0 = Xg - Pn(X^) = 0
* 0 0 (X-j - X-| ) #
0= lx2 * 1 - pn(xl) - 0 (5-40> 3Pn
-
49
compromise solution, and P2» suitably adjust and W2
in equation (5.2) or (5.3) to get the same value of the
compromise solution, then simutaneously design variables
x^, x3» and *4 can t>e obtained for a compromise
solution.
-
CHAPTER 6
GENERALIZED REDUCED GRADIENT METHOD
The reduced gradient method is a technique for
handling constraints in conjunction with any of the methods
*/hich use successive one dimensional minimizations. The
generalized reduced gradient method is one of a class of
algorithms using implicit variable eliminations. This
method was first proposed by Wolfe (1963) who formulated
the method with only linear constraints ana named because
Vrf(x) can be viewed as the gradient of f(x) in the reduced
space of the x variables. McCormick (1969), thereafter,
modified the method by avoiding jamming. The method was
extended to nonlinearly constrained problems by Abablie and
Capentier (1969) who created the first general GRG code.
Gabriele and Ragsdell (1975) also successfully implemented
the generalized reduced gradient method for the solution of
the constrainted nonlinear programming problems, called
OPT.
The main idea (Siddall and Michael 1980) is that
all inequalities are converted to equalities using slack
variables and a search direction is chosen tangent to the
50
-
51
Contours for U
Equality constraint ^-0
n1
Starting point
F i g u r e 8 S t r a t e g y f o r R e d u c e d G r a d i e n t M e t h o d ,
-
constraint lines in the direction of reducing the objective
function. In this method two strategies are used, as shown
in Figure 8. A strategy is used to "scamper" back to
feasibility. After returning to feasibility, the same step
in the same direction is repeated until the minimum in the
search direction is bracketed at A and B. Another stategy
is used to pinpoint the minimum between A and B.
The major components of the GRG algorithm are given
in the flowchart of figure 9. Additional details of our
implementation of the generalized reduced gradient method
can be found in the OPT users manual (Gabriele and
Ragsdell, 1976).
-
53
START
S p e c i f y A n y B o u n d S t a t e V a r i a b l e s a s D e c i s i o n V a r i a b l e
C a l c u l a t e R e d u c e d G r a d i e n t
F o r m P r o j e c t e d R e d u c e d G r a d i e n t
D e t e r m i n e S e a r c h D i r e c t i o n (stoT)
T a k e S t e p A l o n g S e a r c h D i r e c t i o n ( • + —
A d j u s t S t a t e V a r i a b l e s U s i n g N e w t o n ' s M e t h o d
R e d u c e S t e p S i z e
I t e r a t e t o N e a r e s t B o u n d
B o u n d
R e f i n e t o L o c a t e M i n i m u m
N e w t o n M e t h o d
M 1 n i m u m B o u n d e d
Increase Step Size
F i g u r e 9 B a s i c F l o w c h a r t o f R e d u c e d G r a d i e n t A l g o r i t h m , O P T , f o r F u l l y C o n s t r a i n t e d P r o b l e m .
-
CHAPTER 7
NLP FORMULATION
Assume 1018 HR Steel and E6010 as bar and weld
materials, therefore;
(a) Applied load : P = 500 lb
Length of bar : L = 25 in
(b) Beam material: 1018 HR Steel
3 CB - .06509 $/in
0^ = 6385 psi
(c) Weld material: E6010
3 Cw = .09622 $/in
Xw = 3826 psi
Design Variables:
x = lxi ,X2,X3,X4 ]T = lh,1,t,b]T
Uncontrollable Parameters (mean values)
u = lu1,u2,u^,u^,u5,u6,u7]T
u = I T,r
-
55
Objective Functions
(7.1)
2 f^xru) = 1.93122x^x 2 + . 06509x^x^ (v-^ u^+ x2) (7.2)
Constraints
(a) Limit of sizes of design variables (4 constraints)
.1 < x-j < 2.0
. 1 < x 2 < 1 0 . 0
.1 < X3 £ 10.0
.1 < x^ £ 2.0
where upper limit of x-| and x^ can be chosen readily as 2.0
inches because x-| and x^ are less than one tenth of X3 in
the case of minimizing design cost.
(b) Limit of design properties (5 dominant constraints):
eqns. (3.41), (3.42), (3.43), (3.44), and (3.45).
-
CHAPTER 8
RESULTS
The curve of the first objective function
(sensitivity) versus variation of uncontrollable parameters
is shown in Figure 10 . As the variation increases from
-.05 to +.05 (from -5% to +5%), the value of the objective
function also increases, which implies that a design object
is inherently sensitive to uncontrolled variation. Figure
11 shows the second objective function (design cost) versus
the variation. Figure 11 also illustrates that design cost
becomes more expensive as the variation increases. The more
detailed figures are given in Appendix A.
It is shown that the value of constraints, which
include uncontrollable parameters, becomes decreased as the
variation increase from -.05 to +.05, in Figures 12, 13,
14, and 15. These Figures also give the tendency that a
design object becomes more sensitive as the variation
All figures in this thesis requiring contours of objective and constraints were prepared using OFCP (David, 1979).
56
-
57
.759960
1 0"* 025
F i g u r e 1 0 F i r s t O b j e c t i v e F u n c t i o n : S e n s i t i v i t y w i t h r e s p e c t t o V a r i a t i o n o f U n c o n t r o l l a b l e P a r a m e t e r s .
x = 2 . 0 x = 1 0 . 0 x 1 = 1 0 . 0 x f = 2 . 0 3 4
-
58
124.439
123.624
122.812 $
/
/J
/ 0.0 .025 .05
Figure 11 Second Objective Function: Design Cost with respect to Variation of Uncontrollable Parameters.
x . = 2 . 0 x _ = 1 0 . 0 = 1 0 . 0 x £ = 2 . 0
-
59
3700.38'
3599.20
.05 .025 0.0 v
Figure 12 First Dominant Constraint with respect to Variation of Uncontrollable Parameters.
x 1 = 2 . 0 x 2 = 1 0 . 0 X 3 = 1 0 . 0 = 2 . 0
-
60
6010 .00
5831.39
5652.31
.05 0.0 .025 v
Figure 13 Second Dominant Constraint with respect to Variation of Uncontrollable Parameters.
x = 2 . 0 x = 1 0 . 0 xl = 1 0 . 0 x f = 2 . 0 i 4
-
61
\ 1 \ \
\
\ \
\
\
i X x1 0 0.0 .025 .05
Figure 14 Fourth Dominant Constraint with respect to Variation of Uncontrollable Parameters.
1 _ 2 . 0 1 0 . 0
x 9 = 1 0 . 0 2.°
-
62
.05 .025 0.0 v
Figure 15 Fifth Dominant Constraint with respect to Variation of Uncontrollable Parameters.
x = 2 . 0 x ? « 1 0 . 0 x ^ = 1 0 . 0 x ^ = 2 . 0
-
increases. Finally, Figures 10, 11, 12, 13, 14, and 15
illustrates that an optimal design should be performed at
5% variation of uncontrollable parameters for the worst
case because at the case of 5% variation a design object is
the most sensitive amongst all variations from -5% to +5%.
Figure 16 showns all constraints and contours of
the first objective function. The upper limit of design
variables, = 2.0, X£ = 10.0, x^ = 10-0» and x^ = 2.0
inches, produces the minimal sensitivity of the welded
beam, as shown in Fig. 17 and 18. That is, minimal
sensitivity causes maximal strength and design cost. For
better understanding, more figures are given in Appendix B.
Figures 19 also presents that an optimal design
satisfying only minimal sensitivity is not practical. It is
shown, in Figures 19, 20, and 21, that there exist a big
difference of design cost between the cases for minimizing
only design cost and only sensitivity of a design object,
respectively. Therefore, the need of two objective
criteria, sensitivity and design cost, is readily realized.
-
64-
D C B A 1 0 . 0
U
0
0.0
1 0 . 0 5.0 x
F i g u r e 1 6 C o n t o u r s o f F - | a n d A l l D o m i n a n t C o n s t r a i n t s w i t h r e s p e c t t o X 3 a n d x ^ .
( v = . 0 5 x - | = . 2 0 X 2 = 5 . 0 )
C O N T O U R 1 0 A = . 0 0 7 B = . 0 0 1 C = . 0 0 2 D = . 0 1
-
65
D C B A 1 0 . 0
2
.0
.0 1 0 . 0 5.0 0.0 x
F i g u r e 1 7 C o n t o u r s o f F 1 : S e n s i t i v i t y w i t h r e s p e c t t o x 1 a n d x 2 .
( v = . 0 5 x 3 = 1 0 . 0 = 2 . 0 )
C O N T O U R I D A = . 0 0 0 1 3 4 8 2 1 B = . 0 0 0 1 3 7 C = . 0 0 0 1 4 5 D = . 0 0 1
-
D C B A 1 0 . 0
4
0
0.0
0.0 0 1 0 . 0 x
F i g u r e 1 8 C o n t o u r s o f F 1 : S e n s i t i v i t y w i t h r e s p e c t t o a n d x ^ .
( v = . 0 5 x 2 = 1 0 . 0 x 1 = 2 . 0 )
C O N T O U R I D A = . 0 0 0 1 3 4 8 2 1 B = . 0 0 0 3 5 C = . 0 0 1 0 = . 0 0 5
-
67
1 0. 0 B C D
5.0
0.0
0.0 5.0 x, 1 0 . 0
F i g u r e 1 9 C o n t o u r s o f F : D e s i g n C o s t w i t h r e s p e c t t o X o a n a X / f o r ' 1 t h e C a s e s a t i s f y i n g M i n i m u m S e n s i t i v i t y
( v = . 0 b
C O N T O U R I D A = 9 0 . 0 C = 1 2 4 . 0
X1 = 2 . 0
B = 1 0 5 . 0 D = 1 4 0 . 0
x 2 " 1 0 . 0 )
-
68
1 0 . 0
0.0 5.0 1 0 . 0
F i g u r e 2 0 C o n t o u r s o f F 2 : D e s i g n C o s t w i t h r e s p e c t t o X 2 a n d X 3 f o r t h e A c t u a l C a s e M i n i m i z i n g o n l y D e s i g n C o s t
( v = . 0 5
C O N T O U R I D A = 2 . 0 C = 3 . 0
x 1 = . 1 7 . 1 8 )
B = 2 . 5 0 D = 3 . 5 0
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69
ABCD 1 0 . 0
1 0 . 0
F i g u r e 2 1 C o n t o u r s o f F 2 : D e s i g n C o s t w i t h r e s p e c t t o X 3 a n d f o r t h e A c t u a l C a s e M i n i m i z i n g o n l y D e s i g n C o s t
( v = . 0 5
C O N T O U R I D A = 2 . 0 C = 7 . 0
*1 . 1 7
B = 3 . 5 0 D = 1 2 . 0
X2 • 6 . 0 )
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70
A trade-off curve is formulated based on the
sensitivity and design cost, as shown in Figure 22. After
setting initial and final specification, we can obtain the
recommended solution for the final decision of an optimal
design. For example, let's choose labels 8 and 5 as initial
and final specifications respectively, then the region from
5 to 8 can be used for the suitable design from the
available feasibility. The recommended solution also can be
obtained as follows:
F-| = .0022 + (.004866-.0022)/2
= .003533
= 8.488372 + (13.48532-8.488372)/2
= 10.986846
A/ /V where, F-j and Fg are the values at 50% from initial
to final specifications. From F-] and F2» we can obtain the
recommended solution that is the closest point on the A/
trade-off curve from the point (F"|#F2)* *n this example,
label 6 can be chosen as a recommended solution.
For a recommended solution, another method can be
used as follows: find a an Utopia point based on label 5
and 8, as shown Figure 22. Then get the closest point from
the Utopia point to the trade-off curve, as discussed in
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71
F1 F2 1 .045717 3.937362 2 .014748 4.912147 3 .010002 5.878498 4 .006880 7.077603 5 .004866 8.488372 6 .C03581 10.05805 7 .002751 11.73553 8 .002200 13.48532 9 .001826 15.28449 10 .001350 19.07323 11 .000935 26.80917 12 .000846 30.15035 13 .000671 42.90977 14 .000135 124.4390
.0229 "
'2
F 62.22
F i g u r e 2 2 T r a d e - o f f C u r v e o f a W e l d e d B e a m O b t a i n e d b y M e t h o d o f S p e c i f i c a t i o n s a t v = . 0 5
-
chapter 5. Label 6, in this example, can be chosen as a
recommended solution.
The Pareto-minimal set and Utopia point are
formulated by using a method of decomposition,
F = W-|F-|n + w2f2N' shown in Figure 23. Table 1 shows the
Utopia point. Before performing Lagrangian interpolation,
let's choose 5 points and scale these values, as shown in
Table 2, in order to adjust Lagrangian interpolation
polynomial to the trade-off curve given in Figure 23.
Lagrangian formula can be obtained thereafter. From
eqn.(5.40), a compromise solution and the related design
variables can be obtained, after three more steps are
performed, as discussed in chapter 5.
* A compromise solution, = .08964734 and
X* = .04989566, is obtained and multiplied by
F^ = 124.4390 and F. = .045717. Then the values, 2max 1 max tt tt
F^ = 11.15562 and F^ = .0022811, are almost same as those
of = .5 and W£ = .5.
Finally, a compromise solution and the related
design variables, shown in Table 3, can be obtained as
follows:
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73
No
045717 3.937362 .031641
004515 7.779320 .071566
002913 9.990186 .073655
002215 11.30412 .069650
001690 13.05326 .064134
001097 16.71004 .051564
000135 124.4390 .002950 0229
124.U us$
6 2 . 2 2
23 Trade-off Curve of a Welded Beam Obtained bv Method of Decomposition with
F * «1Fm + h2f2N and v " -05
-
74
T a b l e 1
U t o p i a P o i n t O b t a i n e d b y M e t h o d o f D e c o m p o s i t i o n , F = ^ F ^ N + W 2 F 2 N . ( v = . 0 5 )
F1 F2 F 1 / . 0 4 5 7 1 7 F 2 / 1 2 4 . 4 3 9
. 0 0 0 1 3 5 0 3 . 9 3 7 3 6 2 . 0 0 2 9 5 2 9 . 0 3 1 6 4 1 0
T a b l e 2
T h e C h o s e n D a t a P o i n t f o r L a g r a n g e ' s I n t e r p o l a t i o n P o l y n o m i a l . ( v = . 0 5 )
N o . W i w2 f1N f2N F - | / . 0 4 5 7 1 7 F 2 / 1 2 4 . 4 3 9
1 . 2 5 . 7 5 . 0 0 4 5 1 5 7 . 7 7 9 3 2 0 . 0 9 8 7 5 9 7 . 0 6 2 5 1 5 0
2 . 4 0 . 6 0 . 0 0 2 9 1 3 9 . 9 9 0 1 8 6 . 0 6 3 7 1 8 0 . 0 8 0 2 8 1 7
3 . 5 0 . 5 0 . 0 0 2 2 1 5 1 1 . 3 0 4 1 2 . 0 4 8 4 5 0 2 . 0 9 0 8 4 0 6
4 . 6 0 . 4 0 . 0 0 1 6 9 0 1 3 . 0 5 3 2 6 . 0 3 6 9 6 6 5 . 1 0 4 8 9 6 8
5 . 7 5 . 2 5 . 0 0 1 0 9 7 1 6 . 7 1 0 0 4 . 0 2 3 9 9 5 4 . 1 3 4 2 8 2 9
T a b l e 3
C o m p r o m i s e S o l u t i o n a n d t h e R e l a t e d D e s i g n V a r i a b l e s , ( v = . 0 5 )
U W 1
U 2
F*(«)
. 5 . 5 . 0 0 2 2 1 5 4 1 1 . 3 0 4 1 2
< ( i n ) ( i n ) *3 ( i n ) *
( i n )
. 2 8 6 2 2 3 4 o 7 5 2 8 9 1 0 . 0 0 0 0 . 5 2 2 8 0 7
-
•*
X1 = .286223 in
* x2 = 4.75289 in
X3 = 10.0000 in
* */, = .522807 in
-
CHAPTER 9
CONCLUSION
Herein we demonstrate an approach (Design for
Latitude) which minimizes sensitivity (maximizes stability
or latitude) in the presence of changes in uncontrollable
parameters. We conclude that maximum latitude gererally
correspons to maximum cost. The region selected by setting
initial and final specifications on a trade-off curve is
useful for an optimal design satisfying both minimal
sensitivity and design cost. Moreover, a compromise
solution obtained by the concept of Pareto-minimal set and
Utopia point gives an efficient guideline for the best
solution.
Dominant constraints, in the present reseach, are
suitably selected for the worst case. Moreover, two
objective functions for sensitivity of a design object and
design cost are efficiently handled as a NLP problem.
Finally sensitivity is found to be one of the most
important factors for an optimal design as well as design
cost.
76
-
A P P E N D I X A
O B J E C T I V E F U N C T I O N S A N D C O N S T R A I N T S W I T H R E S P E C T T O V A R I A T I O N O F
U N C O N T R O L L A B L E P A R A M E T E R S B A S E D O N D E S I G N V A R I A B L E S
.0
0
0
1 0 . 0 0.0 5.0 x
X - | = 2 . 0 X 2 = 1 0 . 0
C O N T O U R I D F , | ( X , U ) = . 0 0 0 3 5
1 : v • 0 . 0 2 : v = . 0 5 3 : v = . 1 0
77
-
1 0 . 0
0
0.0
1 0 . 0 5.0 0.0 X
X - i = . 1 7 = . 1 8
C O N T O U R I D F 2 ( X . U ) = 3 . 2 0
1 : v - 0 . 0 2 : v = . 0 5 3 : v = . 1 0
-
7.9
1 0 . 0
5.0
0.0 0 . 0 5 . 0 x 3 1 0 . 0
41
•
1 ^3
•
X 1 = . 2 0 X 2 = 5 . 0
C O N T O U R I D Q ^ X . U ) =
1 : v = 0 . 0 2 : v = . 0 5 3 : v =
0 . 0
. 10
-
80
X 1 = . 2 0 X 2 = 5 . 0
C O N T O U R I D g 2 ( x » u )
1 : v = 0 . 0 2 : v = . 0 5 3 : v
= 0 . 0
= . 10
-
02 * = A : e SO * = A ' -z 0*0 = A :I
o'o = (n'x)^6 ai ynoiNOO
o * s = z t o z * = L x
0"0 L o*$ 0*0
cafes
9i I £ 2 -
L8
-
X 1 = . 2 0 X 2 = 5 . 0
C O N T O U R I D g c ( X , U ) 5
1 : v - 0 . 0 2 : v = . 0 5 3 : v
= 0 . 0
= . 1 0
-
A P P E N D I X B
C O N T O U R S O F F : S E N S I T I V I T Y B A S E D O N D E S I G N V A R I A B L E S
DCB A
•v.
-g,
/
0.0 0 . 0 5 . 0 x 1 1 0 . 0
v = .05 x2 = 10.0 = 2.0
C O N T O U R I D A = . 0 0 0 1 3 4 8 2 1 B = . 0 0 0 4 C = . 0 0 1 D = . 0 0 5
83
-
84
DCBA
/ g3 /
/
0 . 0 5 . 0 x 1 1 0 . 0
v = . 0 5 x 2 = 1 0 . 0
CONTOUR ID A = .000134821 C = .001
x = 1 0 . 0 3
B = .0003 D = .005
-
85
1 0 . 0
5.0
0.0
I lv •——
I V . V .
h
/
0.0 5.0 1 0 . 0
v = .05 x-] =2.0
CONTOUR ID A = .000134821 C = .001
H = 2 - °
B = .0005 D = .005
-
86
1 0 . 0
5.0
0.0
V A
- A r -
A
- A r -V
0.0 5.0 1 0 . 0
v = . 0 5 x - i = 2 . 0 x 3 = 1 0 . 0
CONTOUR ID A = .000134821 C = .001
B = .0003 D = .005
-
LIST OF REFERENCES
Abadie, J., and Carpentier, "Generalization of the Wolfe Reduced Gradient Method to the Class of Nonlinear Constraints," Optimization (R. Flether, ed.), Academic Press, New York, P. 37, (1969).
Bartel, D. L., and Marks, R. W., "The Optimum Design of Mechanical Systems with Competing Design Objectives," ASME Journal of Engineering for Industry, pp. 171-178, (Feb. 1974)
David, J., and K. M. Ragsdell, "OFCP: An Optimization Contour Plotting Package," Design Optimization Laboratory, (1979).
Gabriele, G. A., "Application of the Reduced Gradient Method to Optimal Engineering Design," M.S. Thesis. School of Mechanical Engineering, Purdue University, (Dec. 1975).
Gabriele, G. A., and Ragsdell, K. M., "OPT: A Nonlinear Programming Code in Fortran, Users Manual," School of Mechanical Engineering, Purdue University, (1976) .
Gerald, C. F., Applied Numerical Analysis, (Second Edition) , Addison-wesley, (1978) .
Gim, G., "Optimal Design of a Class of Welded Beam Structures Using the Method of Multipliers," AME-507 Term Paper, Aerospace and Mechanical Engineering, The University of Arizona, (May 1983).
Leitmann, G., The Calculus of Variations and Optimal Control, Plenum Press, New York, (1981). ~
McCormick, G. P., "Anti-Zig-Zagging by Bending," Management Science. Vol.15, pp. 315-320, (1969).
87
-
88
Papalambros, P. and Wilde, D. J., "Regional Monotonicity in Optimum Design," Journal of Mechanical Design, Transactions of the ASME. Vol. 102, pp. 497-500, (July 1980).
Ragsdell, K. M., Applied Numerical Method, Design Optimization Laboratory Publication, (1982).
Ragsdell, K. M., and Phillips, D. T., "Optimal Design of a Class of Welded Sructures Using Geometric Programming," ASME Journal of Engineering for Industry, Vol. 98, Series B, No. 3, pp. 1021-1025, (August 1976).
Reklaitis, G. V., Ravindran, A., and Ragsdell K. M., Engineering Optimization: Method and Applications, Wiley Interscience, (1981) .
Salakvadze, M. E., Vector-Valued Optimization Problems in Control Theory, Academic Press, New York, (1979).-
Shigley, J. E., Mechanical Engineering Design, Third Edition, McGraw Hill, (1977).
Siddall, J. N., Optimal Engineering Design; Principles and Applications, Marcel Dekker, Inc., (1982).
Siddall J. P., and Michael W. K., "Interaction Curves as a Tool in Optimization and Decision Making," Transactions of the ASME. Vol. 102, pp. 510-516, (July 1980).
Stewart, J. P., The Welder's Handbook. A Prentice Hall Company, (1981).
Timoshenko, S. P., Theory of Elastic Stability, Second Edition, McGraw Hill, (1961).
Vincent, T. L., "Game Theory as a Design Tool," Journal of Mechanisms, Transmissions, and Automation in Design, Vol. 105, pp. 165-170, (June 1983).
Vincent, T. L., and Grantham, W. J., Optimality in Parametric Systems, A Wiley Interscience Publication, (1981).
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89
Wolfe, P., "Methods for Linear Constraints," Nonlinear Programming, Abadie, J., ed., North Holland, Amsterdam, (1967).