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This document is part of the notes written by Terje Haukaas and posted at www.inrisk.ubc.ca.The notes are revised without notice and they are provided as is without warranty of any kind.
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Warping Torsion
Inadditiontoshearstresses,somememberscarrytorquebyaxialstresses.Thisiscalled warping torsion. This happens when the cross-section wants towarp, i.e.,displaceaxially,butispreventedfromdoingsoduringtwistingofthebeam.Notallcross-sectionswarp,andeventhosethatwarpdonotcarrytorquebyaxialstressesunless they are axially restrained at some location(s) along the member. Cross-sections that do NOT warp include axisymmetric cross-sections and thin-walledcross-sectionswithstraightpartsthatintersectatonepointthecross-section,suchas X-shaped, T-shaped, and L-shaped cross-sections. For these cross-sections alltorque is carried by shear stresses, i.e., St. Venant torsion, regardless of theboundaryconditions.
WarpingofI-sectionsAsapedagogicalintroductiontowarpingtorsion,considerabeamwithanI-section,such as awide-flange steel beam.When torsion is applied to the beam then theflanges of this cross-section experiences bending in the flange-planes. In otherwords, torsion induces bending about the strong axis of the flanges. When theflanges are fixed at some point, such as in a cantilevered beam with a fully
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clampedend,someofthetorqueiscarriedbyaxialstresses.Tounderstandthis,denotethebendingmomentandshearforceineachflangeby MandV,respectively,asshowninFigure1.
Figure1:WarpingofI-section
(zisthelocalaxisforbendingofflange,nottheglobalz-axisofthecross-section).
Thetorquethatthecross-sectioncarriesbybendingintheflangesis:
T = h !V
(1)where h is the distance between the flanges and V is positive shear force inaccordancewiththedocumentonEuler-Bernoullibeamtheory.Thatdocumentalsoprovides the equilibrium equation that relates shear force to bending moment,whichyields:
V =dM
dx ! T = h " dM
dx (2)
Thebeamtheoryalsoprovidetherelationshipbetweenbendingmomentandflangedisplacement,w:
M = EI! d2
w
dx2 " T = h !EI! d
3
w
dx3 (3)
where I is themoment of inertia of one flange about its local strong axis. Next,Figure1isreviewedtodeterminetherelationshipbetweenwand:
w = !"#h
2 $ T = !
h2
2#EI#
d3"
dx3 (4)
which resulted in the differential equation for warping torsion of an I-section.However,thisequationisgenerallywritteninthisformat:
T = !ECw "d
3#
dx3 (5)
whichimpliesthat,forI-sections,thecross-sectionalconstantforwarpingis:
Cw= I!
h2
2 (6)
!
z, w
h!
z, w
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whereitisreiteratedthatI is themomentof inertiaof one flangeabout its localstrongaxis.
CompleteDifferentialEquationforTorsion
As mentioned earlier, when warping is restrained the torque is carried by both
shear stresses, i.e., St. Venant torsion and axial stresses, i.e., warping torsion.Specifically,thetorquefromshearandaxialstressesaresuperimposed,whichleadstothefollowingcompletedifferentialequationfortorsion:
T = GJ!d"
dx# EC
w!
d3"
dx3 (7)
Whenequilibriumwithdistributedtorquealongthebeam, mx,isincluded,i.e.,mx=dT/dx,thenthefulldifferentialequationreads
ECw!
d4"
dx4#GJ!
d2"
dx2= m
x (8)
Solution
ThecharacteristicequationtoobtainthehomogeneoussolutionforthedifferentialequationinEq.(8)reads
!4 "GJ
ECw
#!2= 0 (9)
The roots are 0, 0, (GJ/ECw), and (GJ/ECw). Accordingly, the homogeneoussolutionis
!(x) = C1"e
GJ ECw "
x+ C
2"e
# GJ ECwx+C
3"x + C
4 (10)
whichguidestheselectionofshapefunctionsifanexactstiffnessmatrixwithbothSt.Venantandwarpingtorsionissought.Anotherwayofexpressingthesolutionis:
!(x) = C1 "sinh GJ ECw "x( )+C2 "cosh GJ ECw "x( )+C3 "x +C4 (11)
where the coefficients, Ci, in Eq. (10) are different from those in Eq. (11). Forexample,thehomogeneoussolutionforacantileveredbeamthatisfullyfixedat x=0andsubjectedtoatorque,To,atx=Lhasthesolution
!(x) =1
GJ ECw
"T
o
GJ"
tanh GJ ECw"L( ) " cosh GJ ECw "x( )#1$% &'
#sinhGJ EC
w "x
( )+ GJ EC
w "x
(
)
**
+
,
-- (12)
FromthissolutionthetorquecarriedbySt.Venanttorsioniscomputedby:
TSt.V.
(x) =GJ!d"
dx (13)
andthetorquecarriedbywarpingtorsioniscomputedby:
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Twarping(x) = !ECw "d
3#
dx3 (14)
whereTSt.V.(x)+Twarping(x)=Toforall0
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thesedocuments.Althoughthisisashortcoming,thepresentedtheoryissufficientfor many practical applications. This is because many thick-walled cross-sectiontypes are difficult to fully restrain axially. In contrast, it is easier to imagineconnection designs for thin-walled cross-sections that provide sufficient axialrestrainttodeveloptorqueduetoaxialstresses.
Figure2:Beamaxissystemandcorrespondingdisplacements.
Kinematics
Theobjective inthissection istoestablish arelationshipbetweenaxialstrain,x,
andaxialdisplacement, u.Forthispurpose,letthecoordinate sfollowthecentrelineofthecontourofthecross-sectionandlet hdenotethedistancefromthecentreofrotation(ysc,zsc)tothetangentofthecoordinatelines,asshowninFigure2.They-z-axes originate in the centroid of the cross-section, while the shear centrecoordinatesyscandzscarepresentlyunknown.Analogoustotheomissionofsheardeformation in Euler-Bernoulli beam theory, the shear the shear strain xs isneglected in the combined theory of warping torsion and bending. In turn, thisprecludes shear stresses, but as in the beam theory they are recovered later byequilibrium. Furthermore, the shear stresses from St. Venant torsion aresuperimposed so that the total shear strain xs is equal to that from St. Venanttorsion.Moreprecisely,xsisequaltotheshearstrainatr=0fromSt.Venanttheory,
i.e.,atthemid-planeofthecross-sectionprofile.Inpassingitisnotedthataccordingto the St. Venant theory the shear strain at r=0 for open cross-sections is zero.Furthermore,asafundamentalkinematicspostulationit isassumedthatthecross-sectionretainsitsshape.Thisimpliesthats=s=0andthatthedisplacementinthes-directionis:
!v = !v "cos(#)+w "sin(#)+$"h (19)
T, !
y, v
z, w
s, !v
h
r
x, u
Shear centre / centre of twist (ysc,zsc)
Centroid (0, 0)
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wherevandwarethedisplacementsofthecross-sectionandistheanglebetweenthes-axisandthey-axes.ThecontributionstoEq.(19)areillustratedinFigure3.
Figure3:Contributionstothedisplacementalongthe s-axis.
Giventhepreviousassumptionstherelevantkinematicsequationsare !
x= u
,x
(20)
!xs = !v,x + u,s = !xsSt.V. (21)whereitisreemphasizedthat !
xs
StV= 0 foropencross-sections.SubstitutionofEq.
(19)intoEq.(21)yields
!dv
dx"cos(#)+
dw
dx"sin(#)+
d$
dx"h +
du
ds= %
xs
St.V. (22)
Next,therelationshipsbetweenthedifferentials ds,dy,anddzareestablished.WithreferencetoFigure3theyare:
dy
ds= !cos(")
dz
ds= sin(")
(23)
SubstitutionofEq.(23)intoEq.(22)yields
dv
dx!
dy
ds+
dw
dx!
dz
ds+
d"
dx!h +
du
ds= #xs
St.V. (24)
Solvingforduyields
du = !dv
dx"dy!
dw
dx"dz !
d#
dx"h ! $xs
St.V.%&'
()*"ds (25)
Itisdesirabletoexpress !xs
St.V. intermsofd/dxsothatthelattercanbepulledoutsidetheparenthesis.ThisisachievedbyutilizingequationsfromthetheoryofSt.
w
-v
!
s
(ysc,zsc) !v "cos(#)
!
w!sin(")
h
!"h
ds
dy
dz
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Venanttorsion.Foropencross-sections!xs
St.V. vanishes,butingeneralmateriallawyields
!xs
St.V.=
"xs
St.V.
G (26)
and !xsSt
.
V.
= d" dr where is Prandtls stress function, which is cross-sectiondependent.Forthin-walledcross-sectionswithonecellagoodstressfunctionis
!(s,r) = K "1
2+
r
t
#$%
&'( (27)
Asaresult,theshearstressis
!xs
St.V.="
,r=
K
t (28)
Toexpressthestressintermsofd/dxitisfirstnotedthat
T =GJd!
dx (29)
andthatthetorque,T,canberelatedtothestressbythestress-resultantequation
T = 2 ! "dAA
# (30)
ForthestressfunctioninEq.(27)theintegralevaluates
T = 2 !K!Am (31)
Finally,Eqs.(31)and(29)substitutedintoEq.(28)yieldsthedesiredexpression: !
xs
St.V.=
K
t=
T
t"2 "Am
=
GJ
2 " t"Am
"
d#
dx (32)
SubstitutionintoEq.(25)yields
du = !dv
dx"dy !
dw
dx"dz !
d#
dx" h !
J
2 " t"Am
$%&
'()"ds (33)
Integrationyields
u(y,z)=
u!
dv
dx"y!
dw
dx"z!
d#
dx"$
(34)whereuis theintegrationconstant,whichrepresentsauniformaxialdisplacementofthecross-sectionandhasbeendefinedas:
! " h #J
2 $ t$Am
%&'
()*ds+ (35)
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Itisreemphasizedthatthisexpressionisvalidforcross-sectionswithonecell.Foropencross-sectionstheshearstraininthemid-planeofthecross-sectionprofileiszero,whichimpliesthat
! " hds# (36)
Finally,combiningEq.(20)withEq.(34)yieldsthefinalkinematicsequation:
!x=
du
dx"d2v
dx2#y"
d2w
dx2#z "
d2$
dx2#% (37)
MaterialLaw
Hookeslawprovidestherelationshipbetweenaxialstressandaxialstrain:
!x= E"#
x (38)
SectionIntegration
Integrationofaxialstressoverthecross-sectionyieldstheaxialforce:
N = !xdA
A
" (39)
Integrationofaxialstressmultipliedbydistancefromthecentroidyieldsbendingmoment:
Mz = ! "x #ydAA
$ (40)
Integrationofaxialstressmultipliedbydistancefromthecentroidyieldsbendingmoment:
My = ! "x #z dAA$ (41)
Integrationofaxialstressmultipliedbythepreviouslydefinedquantityisdefinedasthebi-moment:
B ! " #x
$%dAA
& (42)
Equilibrium
Distributedaxial loadalongthebeamis relatedtotheaxialforcebythefollowingequilibriumequation:
qx= !
dN
dx (43)
Distributedloadinz-direction,whichisassumedtoactthroughtheshearcentreoritwillcontributetomx,isrelatedtotheshearforcebythefollowingequilibriumequation:
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qz = !
dVz
dx (44)
Equilibrium also provides the relationship between shear force and bendingmoment:
Vz =
dMy
dx (45)
Thecorrespondingequilibriumequationsintheotherdirectionare:
qy =
dVy
dx (46)
and
Vy =
dMz
dx (47)
Finally,equilibriumfordistributedtorquealongthebeamyields:
mx= !
dT
dx
(48)
DifferentialEquations
SubstitutionofthekinematicsequationinEq.(37)intothemateriallawinEq.(38)yields:
!x = E"du
dx#E"
d2v
dx2"y #E"
d2w
dx2"z #E"
d2$
dx2"% (49)
Substitution of Eq. (49) into the section integration Eqs. (39) to (42) yields thefollowingsetofequations:
N
Mz
My
B
!
"
##
$
##
%
&
##
'
##
= E(
dAA
) * ydAA
) * zdAA
) * +dAA
)
* ydAA
) y2 dAA
) y (z dAA
) y (+dAA
)
* zdAA
) y (z dAA
) z2 dAA
) z (+dAA
)
* +dAA)
y (+dAA)
z (+dAA)
+2 dAA)
,
-
.
.
.
.
.
.
.
.
.
.
/
0
1111111111
du
dx
d2w
dx2
d2v
dx2
d22
dx2
!
"
#####
$
###
##
%
&
#####
'
###
##
(50)
where symmetry is observed. Under certain condition described shortly, theequationsbecomedecoupledandreducesto:
N = EA !du
dx (51)
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My = EIyd
2w
dx2 (52)
Mz = EIzd
2v
dx2 (53)
B = !ECw
d2"
dx2 (54)
where the diagonal components of the matrix in Eq. (50) have been named asfollows:
A = dAA
! (55)
Iz = y2dA
A
! (56)
Iy = z2 dA
A! (57)
Cw= !2 dA
A
" (58)
For the system of equations in Eq. (50) to be decoupled, the six off-diagonalelements of the coefficient matrix must be zero. These six conditions form animportantpartofthecross-sectionanalysis.Infact,theydeterminethefollowingsixunknownsofthecross-section:
1. yo=y-coordinateofthecentroid
2. zo=z-coordinateofthecentroid3. o=orientationoftheprincipalaxes4. C
=normalizingconstantforthe-diagram
5. ysc=y-coordinateoftheshearcentre6. zsc=z-coordinateoftheshearcentre
Specifically,thecoordinatesofthecentroidofthecross-sectionaredeterminedbythetwoequations:
y dAA
! = z dAA
! = 0 (59)
Theorientationoftheprincipalaxesaredeterminedbythecondition: y !z dA
A
" = 0 (60)
Thenormalizationofthe-diagramiscarriedouttosatisfythecondition:
! dAA
" = 0 (61)
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Thefollowingequationsaresatisfiedifthe-diagramisestablishedwithrespecttotheshearcentre,whichimpliesthattheshearcentrecoordinatesaredeterminedbytheseequations:
y !" dAA
# = z !" dAA
# = 0 (62)
Adding equilibriumwith external forces yields the finaldifferential equations foraxialdeformationandbending
qx = !EA "d2uo
dx2
(63)
qz = EIyd
4wD
dx4
(64)
qy = EIzd
4vD
dx
4 (65)
The derivation of the differential equation that combines St. Venant torsion andwarpingtorsionstartswiththedefinitionofthestressresultant:
T = !xs " t"hdAA
# = qs "hdsA
# = qs d$A
# = qs "$[ ]% & $dqsA
# (66)
whereqsistheshearflowandtheboundaryterm[ qs]fromintegrationbypartsiszero.Becauseshearstrainsareomittedfromthewarpingtheoryitisnecessarytoemploy equilibrium to recover the shear flow. With reference to Figure 4,equilibriumyields:
d!x "ds " t+ d#xs "dx " t= 0 $ d!
x
dx" t+ d
#xs
ds" t= 0 $ dqs
ds= % d
!x
dx" t (67)
Figure4:Equilibriumtorecovershearstresses.
!x+ d!
x
!x
dx
ds
!xs+ d!
xs
!xs
x
s
t
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SubstitutionofEq.(67)intoEq.(66)yields:
T = ! "dqsA
# = " $d%x
dx$ t ds
A
# = " $d%x
dxdA
A
# =d
dx" $%x dA
A
# =dB
dx (68)
Adding the torque carried by shear stresses, i.e.,T=GJ(d/dx) and employing Eq.
(54)yields:
T = GJ!d"
dx# EC
w
d3"
dx3 (69)
Adding equilibrium with distributed torque from Eq. (48) yields the completedifferentialequationforSt.Venanttorsionandwarpingtorsion:
mx= EC
w
d4!
dx4"GJ#
d2!
dx2 (70)
ThesolutiontothisdifferentialequationwaspresentedinEq.(10).
Final-diagram
Eqs.(61)and(62)providetheconditionsthatthefinal -diagrammustsatisfy.Inparticular,thefinal-diagrammustbenormalizedanditmustbedrawnaboutthepoint(ysc,zsc),i.e.,theshearcentreofthecross-section.Inordertoarriveatthefinaldiagram,atrialdiagramisfirstdrawn.Thereafter,thetrialdiagramismodifiedtoobtainthefinalone.Forthispurposeitisusefultoestablishanexpressionthatrelatesthe-diagramdrawnaboutanarbitrarypointQtoanotherdiagramdrawnabout another pointSC.Sincethe-values consist of accumulateddouble sectorareas it is of interest to study a generic infinitesimal contribution. To this end,Figure5identifiesbygray-shadingthe-diagramcontributionsforaninfinitesimal
lengthdsofthecross-section.Thedoubleareaofthesector thatoriginatesin(ysc,zsc)is
d!sc = dy " z #zsc( )# dz " y# ysc( ) (71)
Thedoubleareaofthesectorthatoriginatesin(yQ,zQ)is
d!Q = dy " z #zQ( )# dz " y# yQ( ) (72)
Thedifferencebetweenthetwo-diagramcontributionsinFigure5is
d!sc " d!Q = ysc " yQ( ) #dz " zsc "zQ( ) #dy (73)
Integrationofinfinitesimalcontributionsyieldtheexpressionforthedifferencein-diagrams:
!sc "!Q = ysc " yQ( ) #z " zsc "zQ( ) #y +C (74)
whereCistheintegrationconstant.Rearrangingandrenamingsctoyields:
! =!Q + ysc " yQ( ) #z " zsc "zQ( ) #y+C (75)
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whichistheexpressionforthefinal-diagramonceC,ysc,andzscareknown.
Figure5:Relationshipbetweentwo-diagrams.
The integration constant, C, normalizes the -diagram and is determined byrequiringtheintegralofthe-diagraminEq.(75)tobezeroaccordingtoEq.(61):
!dAA"
= !Q dAA"
+ CdAA"
= 0 # C= $
!Q dA
A
"
A
(76)
wheretermscancelintheintegrationbecause yandzoriginateatthecentroidofthe cross-section. The shear centre coordinates ysc and zsc are determined byrequiringtheintegralsinEq.(62)ofthe-diagraminEq.(75)tovanish:
y !"dAA
# = y !"Q dAA
# $ zsc $zQ( ) ! y2dA
A
# = 0 % zsc = zQ +y !"Q dA
A
#Iz
(77)
z !"dAA#=
z !"Q dA
A#+
ysc $ yQ
( ) ! z2
dAA#
= 0
%ysc
=
yQ $
z !"Q dAA
#Iy (78)
where terms cancel in the integration becausey andz are principal axes of thecross-section. In summary, the following procedure is suggested for thedeterminationofC,ysc,zsc,andultimatelythe-diagram:
1. Selectanarbitrarypoint,Q,inthecross-section
(ysc,zsc)
(yQ,zQ) ds
dz
dy
(y,z)
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2. DrawthetrialQ-diagramaboutQ,i.e.,gathercontributionsaccordingtoEq.(35)alongcross-sectionpartsbyaclockwiseradarsweepabout Q,whileensuring that theQ-diagram is continuous (contributions that are madeclockwise are positive, while those that are made by a counter-clockwisesweeptoensurecontinuousdiagramarenegative)
3. DetermineCbyEq.(76)4. DetermineyscbyEq.(77)5. DeterminezscbyEq.(78)6. Determinefinal-diagrambyEq.(75)
Thereafter,thecross-sectionalconstantforwarpingtorsion,Cw,iscomputedbyEq.(58)andthestressesaredeterminedaccordingtothefollowingequations.
Stresses
Analogous totheEuler-Bernoulli beamtheory,axialstressesare obtainedbyfirstcombiningkinematics fromEq. (37)withmaterial law fromEq. (38),followedbysubstitutionof thefulldifferentialequationswithoutexternalequilibrium,i.e.,Eqs.(51)to(54),whichyields:
!x =N
A"Mz
Iz#y+
My
Iy#z +
B
Cw#$ (79)
Itisobservedthattheomegadiagramshowsthedistributionofaxialstressesinthecross-section due to torsion when warping is restrained. The shear flow isrecoveredbyequilibrium,whichwaspresentedinEq.(67):
qs = t!"xs = t!d"xs0
s
# = $ t!d%x
dxds
0
s
#
= $ t!dN
dx!1
A$dMz
dx!1
Iz!y+
dMy
dx!1
Iy!z +
dB
dx!1
Cw!&'
()
*+,dA
0
s
#
= $dN
dx!1
A!As +
Vy
Iz!Sy $
Vz
Iy!Sz $
dB
dx!1
Cw!S&
(80)
wherethefollowingdefinitionsaremade:
As= dA
0
s
! = t ds0
s
! (81)
Sy = ydA0
s
! = t"yds0
s
! (82)
Sz= zdA
0
s
! = t"z ds0
s
! (83)
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S! = !dA0
s
" = t#!ds0
s
" (84)