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Todd Coburn
Cal Poly Pomona
Cal Poly Pomona
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LECTURE LECTURE07
07
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Bending
Bending
of
of
Composite Sections
Composite Sections
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•• CoConsnsididerer aa ststraraigightht bebeamam susubjbjecectetedd toto benbendidingng…… •• TTh eh e sst rt ra ia inn a ta t a na nyy p op ossi ti ti oi onn yy c ac ann
be
be written…written…
0 0 L L ! ! " " ==
•• AA clclososerer lolookok atat ththee dedefoformrmatatioionn o
off tthhee bbeeaamm aass aa ffuunnccttiioonn ooff R R provides… provides… •• WWee c ac ann s es eee t ht ha ta t…… R R L L y y 0 0 = = ! ! R R y y L L00 == ! ! •• SSoo…… R R y y = = ! !
•• ThThee foforcrcee onon ananyy elelememenentalstrtalstripip ofof mamateteririalal isis…… P P ii==! ! iiAAii
•• ItItss momomenmentt ababouttheoutthe neneututrarall axiaxis…s… M M ii== P P ii y yii==! ! ii A Aiiyyii ii ii ii ii total
total M M A Ayy
M
M =="" ==""! !
•• SothetotSothetotalmomalmomenentt isis……
•• FoForr momomenmentsts inin ththee elelasastiticc rarangnge…e…" " ii==E E ii ! ! ii
•• CoCombmbinininingg wiwithth ourstrourstraiain…n…
R R y y E E ii ii ii== ! ! • • InInsesertrtiningginintotoouourrtototatallmomomementnt&&rereararrarangngining…g… !!!! "" ## $$ $$ %% && ' ' = = R R y y A A E E M M ii ii ii total total 2 2 • • N oN ot it in gn gI=I=!!AA i iyyii22isisththeemomomementntofofininerertitia,a,ififEEisisconconststanant…t… R R E E I I M M total total = =
•• CoCombmbinininingg wiwith…th… ii yyii
R R E E = = !
! …&…& rearrarearranging…nging…
I I y y M M total total ii ii== ! ! W Wee find…find…
I I y y M M total total maxmax max max== ! ! max max y y I I M M all all all all ! ! = = $ $
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I I y y M M total total maxmax max max== ! ! max max y y I I M M all all all all ! ! = = 6 6
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momementnt onon ththee sesectctioionn gigivevenn by…by…
•• ReRecacalllliningg frfromom bebefoforere……
R R y y E E ii ii ii== ! !
•• WWee cacann ththenwrienwritete……
!! !! "" ## $$ $$ %% && ' ' = = R R y y A A E E M M ii ii ii total total 2 2
•• WWee nnootteedd II==!!AA
iiyyii22wawass ththee momomementnt ofof ininerertitia,a, &&
proceeded
proceeded withwith aa constantconstant E.E.
ii E E ii total total ii I I E E
y y M M = = ! ! 7 7
•• LeLet’t’ss ininststeaeadd dedefifinene IIEE==!!EEiiAAiiyyii22..
R R I I M M E E total total 11 = = …or… …or… R R y y E E ii ii ii 11 = = ! !
•• WWee cacann ththenwrienwritete……
ii ii ii E E total total y y E E I I M M ! ! = =
•• WhWhicichh memeanans…s…
•• I tI t i si s o fo ft et enn c oc on vn ve ne ni ei en tn t t ot o n on or mr ma la li zi zee a la lll EEiivavalulueses toto ononee ofof ththee vavalulueses
(Sa
(Say,Ey,Eref ref =E=Eminmin)) ……
Ref Ref E E E E n n ii ii = =
•• WWee ththendefendefininee IInn==!!nniiAAiiyyii22..
ii n n ii total total ii nn I I y y M M = = ! !
•• AnAndd ouourr ststreresssseses bebecomcome…e…
•• OrmorOrmoree gegeneneraralllly…y…
( ( )) ii n n ii total total ii n n ii nn I I y y Y Y M M n n A A P P !! + + = = " "
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Pictures Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9 Pictures Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9ththEdition).Edition).
Ref: Hibbeler.
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.6Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.6
Option 1
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Basic Tabular Method for Section Properties& Bending Analysis w/ Multiple Materials
Step 2: Compute Section Properties.
Step 1: Idealize & Characterize Section (Break it into slices)
Step 3: Determine loading.
ULooks like top & bottom of section in this case.
UWherever the y is greatest on area..
Step 4: Determine locations of potentially critical stress levels.
Step 5: Determine locations of potentially critical stress levels.
UCalculate Stresses.. Example: ( ) i n i i n i I n y Y M n A P f ! + =
UIdealize segments for material and geometry..
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SOLUTION:
• Transform the bar to an equivalent cross section made entirely of brass
• Evaluate the cross sectional properties of the transformed section
• Calculate the maximum stress in the transformed section. This is the correct maximum stress for the brass pieces of the bar.
• Determine the maximum stress in the steel portion of the bar by multiplying the maximum stress for the transformed section by the ratio of the moduli of elasticity.
Bar is made from bonded pieces of steel ( E s= 29x106 psi) and brass
( E b= 15x106 psi). Determine the
maximum stress in the steel and brass when a moment of 40 kip*in
is applied.
Fig. 4.22a Composite, sandwich structure cross section.
Chart developed from content provided by McGraw-Hill for [1].
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• Evaluate the transformed cross sectional properties
(
)( )
4 3 12 1 3 12 1 in. 063 . 5 in. 3 in. 25 . 2 = = = b h I T SOLUTION:• Transform the bar to an equivalent cross section made entirely of brass.
in 25 . 2 in 4 . 0 in 75 . 0 933 . 1 in 4 . 0 933 . 1 psi 10 15 psi 10 29 6 6 = + ! + = = ! ! = = T b s b E E n
• Calculate the maximum stresses
(
)( )
ksi 85 . 11 in. 5.063 in. 5 . 1 in. kip 40 4 = ! = = I Mc m " ( ) ( )max 1.933 11.85ksi max ! = = = m s m b n" " " " ( ) ( ) 22.9ksi ksi 85 . 11 max max = = s b ! !Fig. 4.22b Bar length and height dimensions.
Chart developed from content provided by McGraw-Hill for [1].
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Given
Solution Find
U Steel Core with ESt=29 Msi U Bronze Plating with EBz=15 Msi
U M = 40 in-kip U Max Stress in Steel U Max Stress in Bronze
(
)
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Picture & Problem Courtesy of Pearson ( Hibbeler’s Mechanics of Materials, 9thEdition).
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.6
P 4<B/<1).$ K$0B )1 B0($ <C @<<( 0'( #$)'C<#4$( @).9 0
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Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.6
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U `$ @)-- .#0'1C<#B .9$ 1$4.)<' )'.< <'$ B0($ $'.)#$-T <C 1.$$-; U \9$ .#0'1C<#B$( 1$4.)<' )1 01 19<@'; U \9$ -<40.)<' <C .9$ 4$'.#<)( V0-1< '$".#0- 0H)1W7 ( )150 9mm 200 12 = ! " # $ % & = = ww st nb b ( )( )( ) ( )( )( ) ( )( ) ( 0.020.15 0.009)( )0.15 0.03638m 15 . 0 009 . 0 095 . 0 150 . 0 02 . 0 01 . 0 = + + = = ! ! A A y y U \9$ B<B$'. <C )'$#.)0 <C .9$ .#0'1C<#B$( 1$4.)<' )1 U P//-T)'* .9$ C-$H"#$ C<#B"-07 .9$ '<#B0- 1.#$11 0. &O 0'($)1 U \9$ '<#B0- 1.#$11 )' .9$ @<<( 0." )1 ( )( ) ( )( )( ) ( )( ) ( )( )( ) ( )6 4 2 3 2 3 m 10 358 . 9 03638 . 00 095 . 0 15 . 0 009 . 0 15 . 0 009 . 0 12 1 01 . 0 03638 . 0 02 . 0 15 . 0 02 . 0 15 . 0 12 1 ! = "# $ %& ' ! + + "# $ %& ' ! + = n I ( )( )
( )( )
10 7.78MPa(Ans) 358 . 9 03638 . 00 2 MPa 6 . 28 10 358 . 9 03638 . 0 17 . 0 2 6 6 ' = = = ! = ! ! C B " "(
28.56)
1.71MPa(Ans) 200 12 '= = = B B n! !• Therefore,ERef =Est, nst= 1 & nw=Ew/Est,&
st
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Given
Solution Find
U Wood Block with EW=12 GPa
U Steel Plate with ESt=200 GPa U M = 2 kN-m
U Max Stress in Wood U Max Stress in Steel
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Given
Find
• Aluminum Section Shown.
– EAl=10.0Msi
• Titanium Fail Safe Chord.
– ETi=16.0 Msi
• S tr ess es a t A , B , C , D , E, F.
• Mx=10,000 in-lb.
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1D Solution
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Pictures Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9thEdition).
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.7
conc st E E n = Basic Procedure:
U Determine Transformation Factor for Steel U Determine Neutral Axis of Transformed Area
( ) ( )' ' 0 2 ' ' !nA d !h = h h b st ‘
(solve using quadratic equation) 0 ' ' ' 2 1 2 = ! +nAh nAd bh st st
U Proceed Using Composite Beam Approach
• Some materials cannot take tension.
• This necessitates additional effort to find the neutral axis.
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Picture & Problem Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9thEdition).
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.7
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Picture & Problem Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9thEdition).
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.7
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( )
( )
( )
2 3 3 mm 7856 982 10 25 10 200 '=nA st = = A(
)
(
)
mm 90 . 120 ' 0 33 . 20949 ' 37 . 52 ' 0 ' 400 7856 2 ' ' 300 0 ~ 2 = ! = " + = " " =#
h h h h h h A y(
)(
)
(
)
(
)
2 6 4 2 3 mm 10 67 . 788 9 . 120 400 7856 2 9 . 120 9 . 120 300 9 . 120 300 12 1 ! = " " # $ % % & ' ( + ) * + , - . + = I(
)
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Picture & Problem Courtesy of Pearson (Hibbeler’s Mechanics of Materials, 9thEdition).
Ref: Hibbeler. Mechanics of Materials. 9th Edition. Pearson, 2014., Sect. 6.7
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( ) ( ) ( ) MPa 23 . 21 ) 1000 1 ( 10 67 . 788 1000 1 9 . 120 400 000 , 60 ' (Ans) MPa 920 . 0 ) 1000 1 ( 10 67 . 788 1000 1 9 . 120 000 , 60 4 6 4 4 6 max = ! " # $ % & ' ( = = ! " # $ % & ' = mm m mm mm m mm mm Nm mm m mm mm m mm Nm conc conc ) )( )
( )
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Chart by Todd Coburn.
Stress Concentrations
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Stress concentrations may occur: • in the vicinity of points where the
loads are applied
I Mc K
m=
!
• in the vicinity of abrupt changes in cross section
Fig. 4.24 Stress-concentration factors for flat bars with fillets under pure bending.
Fig. 4.25 Stress-concentration factors for flat bars with grooves (notches) under pure bending.
Maximum stress:
Chart developed from content provided by McGraw-Hill for [1].
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Plastic Bending
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• For any member subjected to pure bending, the strain varies linearly across the section as follows…
m x c y ! ! ="
• If the member is made of a linearly elastic material , the neutral axis passes through the section centroid and we write…
I My
x=!
"
• For a member with vertical & horizontal planes of symmetry & the same tensile & compressive stress-strain relationship, the neutral axis is located at the section centroid & the stress-strain relationship maps the strain distribution from the stress distribution.
Fig. 4.27 Linear strain distribution in beam under pure bending.
Fig. 4.28 Material with nonlinear stress-strain diagram.
Fig. 4.29 Nonlinear stress distribution in member under pure bending.
Chart developed from content provided by McGraw-Hill for [1].
Recall from ARO326 (Lecture 7)…
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• When the maximum stress is equal to the ultimate strength of the material, failure occurs and the corresponding moment M U is referred to as the
ultimate bending moment .
• R Bmay be used to determine M U of any member made of the same material and with the same cross sectional shape but different dimensions.
• The modulus of rupture in bending, R B, is found
from an experimentally determined value of M U and a fictitious linear stress distribution.
I c M F F R U Rb b B= = =
Fig. 4.29 Nonlinear stress distribution in member under pure bending.
Fig. 4.30 Member stress distribution at ultimate momentM U .
Chart developed from content provided by McGraw-Hill for [1].
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• Rectangular beam made of an elastoplastic material
moment elastic maximum = = = = ! Y Y Y m m Y x c I M I Mc " " " " " "
• If the moment is increased beyond the maximum elastic moment, plastic zones develop around an elastic core. thickness -half core elastic 1 2 2 3 1 2 3 = ! ! " # $ $ % & '
= Y Y yY c y M M
• As the moment increase, the plastic zones expand, and at the limit, the deformation is fully plastic.
shape) section cross on only (depends factor shape moment plastic 2 3 = = = = Y p Y p M M k M M
Fig. 4.33 Bending stress distribution in a beam for: (b) yield impending, M = My, (c) partially
yielded, M > My, and (d) fully
plastic, M = Mp.
Chart developed from content provided by McGraw-Hill for [1].
Recall from ARO326 (Lecture 7)…
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• Plastic zones develop in a member made of an elastoplastic material if the bending moment is large enough.
• Since the linear relation between normal stress and strain applies at all points during the unloading phase, it may be handled by assuming the member to be fully elastic.
• Residual stresses are obtained by applying the principle of superposition to combine the stresses
due to loading with a moment M (elastoplastic deformation) and unloading with a moment -M (elastic deformation).
• The final value of stress at a point will not, in general, be zero.
Fig. 4.37 Elastoplastic material stress-strain diagram with load reversal.
Chart developed from content provided by McGraw-Hill for [1].
Recall from ARO326 (Lecture 7)…
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Elastic Bending: I c M e all all = ! 2 6 bh M e all = 3 12 1 2 bh h M e all ! " # $ % & = all all bh M e ! 2 6 1 = So… Plastic Bending: ( )[
]
! " # $ % & = 2 h A F M p p ult ult 4 2 h b all ! = ! " # $ % & ' ( ) * + , ! " # $ % & = 2 2 h h b M ult p - all e p all ult M M 4 6 = =1.5 e p all ult M Mk = for rectangular sections
Plastic Bending Shape Factor:
all all bh h b ! ! 2 2 6 1 4 = 5 . 1 =
Ref. [2], Fig. 6-48 (a)
Ref. [2], Fig. 6-48 (b)
Ref. [7], Fig. 6-48 (c) Ref. [7], Fig. 6-48 (d)
Ref. [7], Fig. 6-48 (e) Ref. [7], Fig. 6-48 (f)
Recall from ARO326 (Lecture 7)…
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Given Solution Find 7075-T6 Al Die Forging U Ftu=75 ksi U Fty= 65 ksi
U Max Elastic Moment
U Max Plastic Moment assuming Elasto-Plasto Material
Elastic Allowable: Elasto-Plasto Assumption:
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Ref: Bruhn. Analysis & Design of Flight Vehicle Structures. 2nd Ed. 1973., Sect. C3.4
Given Solution Find 7075-T6 Al Die Forging U Ftu=75 ksi U Fty= 65 ksi
U Max Elastic Moment
U Max Plastic Moment assuming Elasto-Plasto Material
Elastic Allowable: Elasto-Plasto Assumption:
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What is the maximum stress this section can
withstand?
F
tuWhat is the maximum elastic moment this
section can withstand?
M
max_el= (I/c) F
tuWhat is the maximum elasto-plastic moment a
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If you wish to determine the maximum elasto-plastic
moment this section can withstand, what is the best
way to idealize the thing for computing properties?
Why?
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1. Beer , Johnson, DeWolf, & Mazurek. Mechanics of Materials. 7th Edition. McGraw Hill. 2015.
2. Hibbeler. Mechanics of Materials. 9thEdition. Pearson, 2014.
3. Shanley. Strength of Materials. McGraw-Hill. 1957.
4. Bruhn. Analysis & Design of Flight Vehicle Structures. S.R. Jacobs & Associates. 1973.
5. Peery & Azar. Aircraft Structures. 2ndEdition. McGraw-Hill. 1982.
6. Budynas & Nisbett. Shigley’s Mechanical Engineering Design. 9thEdition.
McGraw Hill. 2011.
7. Roark, Young, Budynas, & Sadegh. Roark’s Formula’s for Stress & Strain, 8thEdition. McGraw Hill. 2012.
8. Ugural & Fenster. Advanced Strength & Applied Elasticity. 4th Edition. Prentice Hall, 2003.