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7/28/2019 Design Notes3 (6)
1/34
The Design Core MarketAssessment
Speci f icat ion
Concept
Design
Detail
Design
Manufacture
Sell
DETAIL
DESIGN
A vast subject. We will concentrate on:
Materials Selection
Process Selection
Cost Breakdown
7/28/2019 Design Notes3 (6)
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Materials Selection with Shape
FUNCTION
MATERIAL
PROCESS
SHAPE
SHAPES FOR TENSION,BENDING, TORSION,
BUCKLING
--------------------
SHAPE FACTORS
--------------------
PERFORMANCE INDICES
WITH SHAPE
7/28/2019 Design Notes3 (6)
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Common Modes of Loading
7/28/2019 Design Notes3 (6)
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Moments of Sections: Elastic
SectionShape
A(m2)
I(m4)
K(m4)
2r 4
4r
4
2r
2b
12
4b414.0 b
ab ba3
4
)( 22
33
ba
ba
bh12
3bh
)(
58.013
3
bh
h
bhb
2
4
3a
332
4a
80
34a
rt
rr io
2
)( 22
tr
rr io
3
44 )(4
tr
rr io
3
44
2
)(2
A = Cross-sectional area
I= Second moment of area
tion ytion ybyAyI sec2
sec
2 dd
where yis measured verticallyby is the section width at y
K= Resistance to twisting of section
( Polar moment Jof a circular section)
tion rrJ sec3d2
GTLK
where Tis the torque
L is the length of the shaft
is the angle of twist
G is the shear modulus
7/28/2019 Design Notes3 (6)
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Moments of Sections: Elastic
bt4
tba )(
bt
hhb io
2
)(
)(2 bht
)(2 bht
2
22
41
dt
tb3
3
2
a
bta
31
4
3
2/
)(12
2
33
o
io
bth
hhb
h
bth
31
6
1 3
)4(6
23 btht
8
2dt
4
3 1
b
ttb
22
2/5)(4
ba
tab
bh
htb
222
b
hbt
41
3
2 3
)8(3
3
hbt
h
bht
41
3
2 3
SectionShape
A(m2)
I(m4)
K(m4)
7/28/2019 Design Notes3 (6)
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Moments of Sections: Failure
SectionShape
Z(m3)
Q(m3)
3
4r
3
2r
6
3b 321.0 b
ba2
4
)(
2
2
ba
ba
6
2bh
)(
8.13
22
bh
bh
hb
32
3a
20
3a
tr
rrr
io
o
2
44 )(4
tr
rrr
io
o
2
44
2
)(2
Z= Section modulus
my
IZ
where
ym is the normal distance from the neutral axisto the outer surface of the beam carrying the
highest stress
Q = Factor in twisting similar to Z
TQ
where
is the maximum surface shear stress
7/28/2019 Design Notes3 (6)
7/34
Moments of Sections: Failure
SectionShape
Z(m3)
Q(m3)
tb2
3
42
2 12
b
ttb
a
bta 31
4
2
)(
)(2 2/13
ab
bat
o
io
o
bth
hhh
b
336
h
bth 31
3
2
tbh2
b
hbt
41
3
2 2
)4(3
23 bthh
t )8(
3
2
hbt
h
bht
41
3
2 2
4
dt
7/28/2019 Design Notes3 (6)
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Shape Factors: Elastic
BENDING
3
1
L
EICSB
44
24 ArIo
Bending stiffness of a beam
where C1 is a constant depending on the
loading details, L is the length of the beam,
and Eis the Youngs modulus of the material
oBo
Be
B I
I
S
S
Define structure factor as the ratio of the
stiffness of the shaped beam to that of a
solid circular section with the same cross-
sectional area thus:
2
4
A
IeB
so,
TORSION
L
KGST Torsional stiffness of a beam
where L is the length of the shaft, G is the
shear Modulus of the material.
22
24 ArKo 2
2
A
KeT
so,
oTo
Te
T K
K
S
S
Define structure factor as the ratio of the
torsional stiffness of the shaped shaft to that
of a solid circular section with the same
cross-sectional area thus:
7/28/2019 Design Notes3 (6)
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Shape Factors: Failure/Strength
BENDING
44
2/33 ArZo
ofo
ff
BZZ
MM
Define structure factor as the ratio of the failure
moment of the shaped beam to that of a solid
circular section with the same cross-sectional area
thus:
2/3
4
A
ZfB
so,
Z
M
I
Mym
ff ZM
The beam fails when the bending moment is largeenough forto reach the failure stress of the
material:
The highest stress, for a given bending moment M,
experienced by a beam is at the surface a
distance ym furthest from the neutral axis:
TORSION
Q
T
The highest shear stress, for a given torque T,
experienced by a shaft is given by:
22
2/33 ArQo 2/3
2
A
QfT
so,
ofo
ff
TQQ
TT
Define structure factor as the ratio of the failure
torque of the shaped shaft to that of a solid circular
section with the same cross-sectional area thus:
ff QT
The beam fails when the torque is large enough forto reach the failure shear stress of the material:
7/28/2019 Design Notes3 (6)
10/34
Shape Factors: Failure/Strength
Please Note:
The shape factors for failure/strength described in this lecture course are
those defined in the 2nd Edition of Materials Selection In Mechanical
Design by M.F. Ashby. These shape factors differ from those defined inthe 1st Edition of the book. The new failure/strength shape factor
definitions are the square root of the old ones.
The shape factors for the elastic case are not altered in the 2nd Edition.
7/28/2019 Design Notes3 (6)
11/34
Comparison of Size and Shape
Rectangular sections
I-sections
SIZE
7/28/2019 Design Notes3 (6)
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Shape Factors
SectionShape
Stiffness Failure/StrengtheB
eT fB
f
T
11 11
05.1
3
0.88 0.7418.1
3
2
b
a
b
a)( ba
b
a
22
2
ba
ab
b
h
3
)(
58.013
2
bh
b
h
h
b
2/1
3
2
b
h
)(
)/6.01(3
)/(22
2/1
bh
hb
hb
0.6221.133
2
73.0
35
2
2/12
t
r
t
r
t
r2/1
2
t
r
0.77
7/28/2019 Design Notes3 (6)
13/34
Shape Factors contd
SectionShape
Stiffness Failure/StrengtheB
eT fB
f
T
t
b
6
4
18
b
t
t
b
2
)/1(
)/31(
abt
aba
222
2/5
))((
)(8
babat
ab
bt
h
2
2
t
d
2
2
2)/1(6
)/31(
hbt
hbh
2
32
)/1(6
)/41(
hbt
hbth
3
22
)( bht
hb
2)/1(3
)/41(
bhb
bht
2)/1(6
)/81(
hbh
hbt
2)/1(3
)/41(
hbh
hbt
2/1
3
2
t
b22/1
12
b
t
t
b
2/3
2/1
)/1(
)/31(
ab
ab
t
a
2/32/1
2/1
)/1(
4
bat
a
2/1)(
2
bt
h
2/3
2/1
)/1(
)/31(
3
2
hb
hb
t
h
2/3
322/1
)/1(
)/41(
2 hb
hbt
t
h
2/1)(
t
d
2/32/1 )/1()(
2
bhbt
h
2/3
2/1
)/1(
)/41(
3
2
hb
bh
b
t
2/3
2/1
)/1(
)/81(
18 hb
hb
h
t
2/3
2/1
)/1(
)/41(
3
2
hb
hb
h
t
7/28/2019 Design Notes3 (6)
14/34
Efficiency of Standard Sections
2
4
A
IeB
ELASTIC BENDING
Shape Factor:
4loglog2log
e
BAI
Rearrange forIand take logs:
Plot logI against logA: parallel lines of slope 2eB
7/28/2019 Design Notes3 (6)
15/34
Efficiency of Standard Sections
2/3
4
A
ZfB
BENDING STRENGTH
Shape Factor:
4loglog
2
3log
f
BAZ
Rearrange forIand take logs:
Plot logI against logA: parallel lines of slope 3/2fB
7/28/2019 Design Notes3 (6)
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Efficiency of Standard Sections
ELASTIC TORSION
2loglog2log;
22
e
Te
T AKA
K
TORSIONAL STRENGTH
2loglog
2
3log;
22/3
f
Tf
T AQA
Q
N.B. Open sections are good in bending, but poor in torsion
7/28/2019 Design Notes3 (6)
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Performance Indices with Shape
ELASTIC BENDING
3
1
L
EICSB Bending stiffness of a beam:
ELASTICTORSION
L
KGST Torsional stiffness of a shaft:
2/12
2/5
2/1
1
4
e
B
B
EL
C
Sm
f1(F) f2(G) f3(M)
2/1
1
)( eBEM So, to minimize
mass m, maximise
2
4
A
IeB
Shape factor:
3
2
1
4 L
AECS
e
BB
so,
2/1
2
)( eTEM
So, to minimize
mass m, maximise
2
2
A
KeT
Shape factor: L
AG
S
e
T
T
2
2
so,
2/1
22/32/12
e
T
TG
LSm
f1(F) f2(G) f3(M)
EG8
3
7/28/2019 Design Notes3 (6)
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Performance Indices with Shape
FAILURE IN BENDING
ff ZM Failure when moment reaches:
FAILURE IN TORSION
ff QT Failure when torque reaches:
3/2
3
)( fBfM So, to minimize
mass m, maximise
2/3
4
A
ZfB
Shape factor:
4
2/3AM
f
Bff so,
3/22/3
3/2)4(
f
Bf
f LMm
f1(F) f2(G) f3(M)
3/2
4
)( fTfM So, to minimize
mass m, maximise
3/2
2/33/2
4
f
Tf
f LTm
f1(F) f2(G) f3(M)
2/3
2
A
QfT
Shape factor:
4
2/3AT
f
Tff so,
)2( ff
7/28/2019 Design Notes3 (6)
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Shape in Materials Selection Maps
0.01
0.1
1
10
100
1000
0.1 1 10 100
Density, (Mg/m3)
Y
oung'sModulus,E
(GPa) Engineering
Alloys
Polymer
Foams
Woods
Engineering
Polymers
Elastomers
Composites
CeramicsSearch
Region
A material with Youngs modulus,Eand density,, with a particular
section acts as a material with aneffective Youngs modulus
and density
e
BEE
e
B
Performance index for elastic
bending including shape,
can be written as
2/1
1
)( EM
e
B
e
B
e
BEM
2/1
1
)(
EXAMPLE 1, Elastic bending
=1
=10
7/28/2019 Design Notes3 (6)
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Shape in Materials Selection Maps
A material with strength, fand
density,, with a particular
section acts as a material with aneffective strength
and density
2)( fBff
2)( fB
Performance index for failure in
bending including shape,
can be written as
3/2
3
)(f
f
BM
2
3/22
3)(
))((f
B
f
BfM
EXAMPLE 1, Failure in bending
EngineeringAlloys
Polymer
Foams
0.1
1
10
100
1000
10000
0.1 1 10 100
Density, (Mg/m3)
Strength,f(MPa)
Ceramics
Composites
Search
Region
Woods
Elastomers
Engineering
Polymers
=1
=10
7/28/2019 Design Notes3 (6)
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Micro-Shape Factors
Material Micro-Shape
+
Macro-Shape,
+
Macro-Shape from
Micro-Shaped Material,
=
Up to now we have only
considered the role of
macroscopic shape on the
performance of fully dense
materials.
However, materials can have
internal shape, Micro-Shapewhich also affects their
performance,
e.g. cellular solids, foams,
honeycombs.
Micro-Shaped Material,
=
Micro-Shaped Material,
7/28/2019 Design Notes3 (6)
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Micro-Shape Factors
Prismatic cells
Concentric cylindrical
shells with foam between
Fibres embedded
in a foam matrix
Consider a solid cylindrical beam expanded, at constantmass, to a circular beam with internal shape (see right).
Stiffness of the solid beam:3
1
L
IECS ooBo
On expanding the beam, its density falls from to ,
and its radius increases from to
o
oo rr
2/1
or
oo
oo IrrI
2
4
2
4
44
The second moment
of area increases to
o
o
EE
If the cells, fibres or rings are
parallel to the axis of the beam then
The stiffness of the
expanded beam is thus
ooB
L
EIC
L
EICS
3
1
3
1Shape Factor:
o
o
e
BS
S
7/28/2019 Design Notes3 (6)
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Function
Tie
Beam
Column
Shaft
Mats. Selection: Multiple Constraints
Objective
Minimum cost
Minimum weight
Maximum stored
energy
Minimum
environmental impact
Constraint
Stiffness
Strength
Fatigue
GeometryMechanicalThermal
Electrical..
Index
2/1
1
EM
Index
3/2
2fM
7/28/2019 Design Notes3 (6)
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Materials for Safe Pressure Vessels
DESIGN REQUIREMENTS
Function Pressure vessel =contain
pressurep
Objective Maximum safety
Constraints (a) Must yield before break
(b) Must leak before break
(c) Wall thickness small toreduce mass and cost
Yield before break
2
2
,
f
IC
CC
IC K
Caa
CK
f
ICKM
1
Leak before break
f
IC
ICC
f
KpRC
t
CKta
pR
tt
pR
22
4
2/2
2,2
f
ICKM
2
2
Minimum strength
f
M 3
7/28/2019 Design Notes3 (6)
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Materials for Safe Pressure Vessels
SearchRegion
M3 = 100 MPa
M1 = 0.6 m1/2
f
ICKM
1f
ICKM
2
2 fM 3
Material M1
(m1/2)
M3
(MPa)
Comment
Tough steels
Tough Cu alloys
Tough Al alloys
Ti-alloys
High strength Al
alloys
GFRP/CFRP
>0.6
>0.6
>0.6
0.2
0.1
0.1
300
120
80
700
500
500
Standard.
OFHC Cu.
1xxx & 3xxx
High strength,
but low safety
margin. Good
for light
vessels.
7/28/2019 Design Notes3 (6)
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1. Express the objective as an equation.
2. Eliminate the free variables using each constraint in turn, giving a set of
performance equations (objective functions) of the form:
where f, gand h are expressions containing
the functional requirements F, geometry M
and materials indices M.
3. If the first constraint is the most restrictive (known as the active constraint)
then the performance is given by P1, and this is maximized by seekingmaterials with the best values ofM1. If the second constraint is the active
one then the performance is given by P2 and this is maximized by seeking
materials with the best values ofM2; and so on.
N.B. For a given Function the Active Constraint will be material dependent.
Multiple Constraints: Formalised
)()()(
)()()(
)()()(
)()()(
33333
22222
11111
iiiii MhGgFfP
MhGgFfP
MhGgFfP
MhGgFfP
7/28/2019 Design Notes3 (6)
27/34
Multiple Constraints: A Simple Analysis
A LIGHT, STIFF, STRONG BEAM The object function is ALm
Constraint 1: Stiffness where so,3
1
L
EICS
12
4tI
2/1
2/5
2/1
1
1
12
EL
C
Sm B
Constraint 2: Strength where so,Ly
ICF
m
ff
2 2
t
ym 3/23/5
3/2
2
2
6
f
f
LC
F
m
If the beam is to meet both constraints then, for a given material, its weight is
determined by the larger ofm1 orm2
or more generally, foriconstraints ).....,,max(~ 321 immmmm
Material E
(GPa)
f
(MPa)
(kgm-3)
m1
(kg)
m2
(kg) (kg)
1020 Steel
6061 Al
Ti 6-4
205
70
115
320
120
950
7850
2700
4400
8.7
5.1
6.5
16.2
10.7
4.4
16.2
10.7
6.5
m~Choose a material
that minimizes m~
7/28/2019 Design Notes3 (6)
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Multiple Constraints: Graphical
log Index M1
log
IndexM
2
Construct a materials selection map based on
Performance Indices instead of materials
properties.
The selection map can be divided into two
domains in each of which one constraint is active.
The Coupling Line separates the domains and iscalculated by coupling the Objective Functions:
where CCis the Coupling Constant.
22
2222
11111
)()(
)()(MCM
GgFf
GgFfM c
Coupling Line
M2 = CCM1
M1 Limited
Domain
M2 Limited
Domain
A
B
Materials with M2/M1>CC , e.g. , are limited by
M1 and constraint 1 is active.
Materials with M2/M1
7/28/2019 Design Notes3 (6)
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Multiple Constraints: Graphical
Coupling Line
M2 = CCM1
Search
Area
C
log Index M1
log
Index
M2
M1 Limited
Domain
M2 Limited
Domain
A
B
C
C
A box shaped Search Region is identified with its
corner on the Coupling Line.Within this Search Region the performance is
maximized whilst simultaneously satisfying both
constraints. are good materials.
M1 Limited
Domain
M2 Limited
Domain
A
B
Coupling Line
M2 = CCM1
log Index M1
log
Index
M2
C
Search
Area
A C
Changing the functional requirements For geometry
G changes CC, which shifts the Coupling Line, altersthe Search Area, and alters the scope of materials
selection.
Now and are selectable.
7/28/2019 Design Notes3 (6)
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Windings for High Field Magnets
DESIGN REQUIREMENTS
Function Magnet windings
Objective Maximize magnetic field
Constraints (a) No mechanical failure(b) Temperature rise
7/28/2019 Design Notes3 (6)
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Windings for High Field Magnets
),(f
L
NiB foThe field (weber/m2) is
where o = the permeability of air, N= number of turns, i= current,f= filling factor,
f(,) = geometric constant, = 1+(d/r), = L/2r
CONSTRAINT 1: Mechanical Failure
Radial pressure created by the field
generates a stress in the coil
),(f2
2
o
Bp
d
rB
d
pr
o ),(f2
2
must be less than the yield stress of the coil material y
and hence 2/1),(f2
r
dB yofailure
So, Bfailure is maximized
by maximizingyM 1
7/28/2019 Design Notes3 (6)
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Windings for High Field Magnets
CONSTRAINT 1: Overheating
So, Bheat is maximized
by maximizing
e
pCM
2
The energy of the pulse is (Re = average of the resistance over the
heating cycle, tpulse = length of the pulse) causes the temperature of the coil to rise by
where e
= electrical resistivity of the coil material
Cp = specific heat capacity of the coil material
pulseetRi2
po
pulsee
Cd
tBT
22
2
If the upper limit for the change in temperature
is Tmaxand the geometric constant of the coilis included then the second limit on the field is ),(f
2/1
max
22
epulse
po
heat
t
TCdB
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Windings for High Field Magnets
Material
y
(MPa)
(Mg/m3)
Cp
(J/kgK)
e
(10-8m)
Bfailure
(wb/m2)
Bheat
(wb/m2) (wb/m2)
High conductivity Cu
Cu-15%Nb compositeHSLA steel
250
7801600
8.94
8.907.85
385
368450
1.7
2.425
35
6289
113
9230
35
6230
Pulse length = 10 ms
B~
),min(~ heatfailure BBB In this case the field is limited by the lowest ofBfailure and Bheat: e.g.
),(f
2/1
max
22
epulse
po
heatt
TCdB
2/1),(f2
r
dB yofailure
2212
),(fMCM
t
TrdM C
pulse
maxfo
Thus defining the Coupling Line
7/28/2019 Design Notes3 (6)
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10
100
1000
10000
100 1000 10000
Index M2 (10-8
m3/J)
IndexM1(MP
a)
Search Region:
Ultra-short pulse
Search Region:long pulse
Search Region:
short pulse
HSLA steels
CuAl-S150.1
Cu-4Sn
Cu-Be-Co-Ni
Be-Coppers
GP coppers
HC Coppers
Cu-NbCu-Al2O3
Cu-Zr
Windings for High Field Magnets
Material Comment
Continuous and long
pulse
High purity coppers
Pure Silver
Short pulse
Cu-Al2O3 composites
H-C Cu-Cd alloysH-C Cu-Zr alloys
H-C Cu-Cr alloys
Drawn Cu-Nb comps
Ultra short pulse,
ultra high field
Cu-Be-Co-Ni alloys
HSLA steels
Best choice for low field,
long pulse magnets (heat
limited)
Best choice for high field,
short pulse magnets (heatand strength limited)
Best choice for high field,
short pulse magnets
(strength limited)
e
pCM
2yM 1