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MECHANICS OFFourth Edition
MECHANICS OF MATERIALS
CHAPTER
MATERIALSFerdinand P. BeerE. Russell Johnston, Jr.John T DeWolf
Shearing Stresses in John T. DeWolf
Lecture Notes:Beams and Thin-Walled Members
J. Walt OlerTexas Tech University
Walled Members
© 2006 The McGraw-Hill Companies, Inc. All rights reserved.
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Shearing Stresses in Beams and Thi W ll d M bThin-Walled MembersIntroductionShear on the Horizontal Face of a Beam ElementExample 6.01Determination of the Shearing Stress in a BeamDetermination of the Shearing Stress in a BeamShearing Stresses τxy in Common Types of BeamsFurther Discussion of the Distribution of Stresses in a ...S l bl 6 2Sample Problem 6.2Longitudinal Shear on a Beam Element of Arbitrary ShapeExample 6.04pShearing Stresses in Thin-Walled MembersPlastic DeformationsSample Problem 6 3Sample Problem 6.3Unsymmetric Loading of Thin-Walled MembersExample 6.05
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Example 6.06
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Introduction• Transverse loading applied to a beam
results in normal and shearing stresses in i
• Distribution of normal and shearing
transverse sections.
( )dAMVdAF
dAzyMdAF xyxzxxx =−===
∫∫∫∫ ττσ
000
stresses satisfies
( ) MyMdAFdAzMVdAF
xzxzz
xyxyy=−=====−==
∫∫∫∫
στστ
00
• When shearing stresses are exerted on the vertical faces of an element, equal stresses must be exerted on the horizontal faces
• Longitudinal shearing stresses must exist in any member subjected to transverse
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y jloading.
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Shear on the Horizontal Face of a Beam Element
• Consider prismatic beam
• For equilibrium of beam element• For equilibrium of beam element( )∑ ∫ −+==
ACDx
MM
dAHF σσ∆0
∫−
=A
CD dAyI
MMH∆
dAQ ∫
• Note,
xVxdxdMMM
dAyQ
CD
A
∆=∆=−
∫=
dx
VQH ∆∆
• Substituting,
flowshearI
VQxHq
xI
VQH
==∆∆
=
∆=∆
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Ix∆
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Shear on the Horizontal Face of a Beam Element
flowshearI
VQxHq ==∆∆
=
• Shear flow,
Ix∆
• where∫= dAyQ
above area ofmoment first 2
1
∫=
=A
dAyI
y
sectioncrossfullofmoment second'
=
∫+AA
y
S lt f d f l• Same result found for lower areaq
IQV
xHq
′
′−=′
=∆
′∆=′
QQ==′+
axisneutraltorespect h moment witfirst
0
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HH ∆−=′∆
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Example 6.01
SOLUTION:
• Determine the horizontal force per unit length or shear flow q on the lower surface of the upper plank.pp p
• Calculate the corresponding shear force in each nail.
A beam is made of three planks, nailed together. Knowing that the spacing between nails is 25 mm and that the vertical shear in the beam is V = 500 N, determine the shear force ,in each nail.
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MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Example 6.01
SOLUTION:
• Determine the horizontal force per unit length or shear flow q on the lower surface of the upper plank.
AQ
pp p
m1016.20)m10120)(N500(
46-
36
×
×==
−
IVQq
( )( )36m10120
m060.0m100.0m020.0−×=
×== yAQ
mN3704=
( )( )
( )( )31
3121
m0200m1000[2
m100.0m020.0
m10120
+
=
×
I• Calculate the corresponding shear
force in each nail for a nail spacing of 25 mm.( )( )
( )( )46
212
m102016
]m060.0m100.0m020.0
m020.0m100.0[2
−×
×+
+mNqF 3704)(m025.0()m025.0( ==
N6.92=F
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m1020.16 ×=
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Determination of the Shearing Stress in a Beam
• The average shearing stress on the horizontal face of the element is obtained by dividing the y gshearing force on the element by the area of the face.
xVQxqH ∆∆∆
VQxtx
IVQ
Axq
AH
ave
=
∆∆
=∆∆
=∆∆
=τ
It
• On the upper and lower surfaces of the beam, τyx= 0. It follows that τxy= 0 on the upper and lower edges of the transverse sections.
• If the width of the beam is comparable or large relative to its depth, the shearing stresses at D1and D2 are significantly higher than at D.
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and D2 are significantly higher than at D.
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Shearing Stresses τxy in Common Types of Beams
• For a narrow rectangular beam,
VVQ 3 2 ⎞⎛
Vcy
AV
IbVQ
xy
3
123
2
2
⎟⎠
⎞⎜⎜⎝
⎛−==τ
A2max =τ
• For American Standard (S-beam) and wide-flange (W-beam) beams
ave
VIt
VQ=τ
webAV
=maxτ
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MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Further Discussion of the Distribution of St i N R t l BStresses in a Narrow Rectangular Beam
• Consider a narrow rectangular cantilever beam bj t d t l d P t it f d
⎟⎠
⎞⎜⎜⎝
⎛−= 2
21
23
cy
AP
xyτI
Pxyx +=σ
subjected to load P at its free end:
⎠⎝2 cA I
• Shearing stresses are independent of the distance from the point of application of the load.o t e po t o app cat o o t e oad.
• Normal strains and normal stresses are unaffected by the shearing stresses.
• From Saint-Venant’s principle, effects of the load application mode are negligible except in immediate vicinity of load application points.
• Stress/strain deviations for distributed loads are li ibl f t i l b ti f i t t
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negligible for typical beam sections of interest.
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 6.2
SOLUTION:SOLUTION:
• Develop shear and bending moment diagrams. Identify the maximums.g y
• Determine the beam depth based on allowable normal stress.
A timber beam is to support the three concentrated loads shown. Knowing that for the grade of timber used
• Determine the beam depth based on allowable shear stress.
that for the grade of timber used,
psi120psi1800 == allall τσ
d t i th i i i d d th
• Required beam depth is equal to the larger of the two depths found.
determine the minimum required depth d of the beam.
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MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 6.2SOLUTION:
Develop shear and bending momentDevelop shear and bending moment diagrams. Identify the maximums.
kips3=Vinkip90ftkip5.7
kips3
max
max⋅=⋅=
=MV
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MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 6.2• Determine the beam depth based on allowable
normal stress.maxM
in.lb1090psi1800 2
3
max
⋅×=
=S
Mallσ
31 dbI
( )in.26.9
in.5833.0p 2
=dd
D i h b d h b d ll bl2
61
3121
dbcIS
dbI
==
= • Determine the beam depth based on allowable shear stress.
3 max=V
allτ( )
( ) 2
261
in.5833.0
in.5.3
d
d
=
=
( )in.3.5lb3000
23psi120
2
=d
Aallτ
( ) ( )in.71.10=d
• Required beam depth is equal to the larger of the two.
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in.71.10=d
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Longitudinal Shear on a Beam Element f A bit Shof Arbitrary Shape
• We have examined the distribution of th ti l tthe vertical components τxy on a transverse section of a beam. We now wish to consider the horizontal
hcomponents τxz of the stresses.
• Consider prismatic beam with an element defined by the curved surfaceelement defined by the curved surface CDD’C’.
( )∑ ∫ −+∆== dAHF CDx σσ0a
• Except for the differences in integration areas, this is the sameintegration areas, this is the same result obtained before which led to
VQHqxVQH =∆
=∆=∆
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Ixq
I ∆
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Example 6.04
SOLUTION:
• Determine the shear force per unit length along each edge of the upper plank.
• Based on the spacing between nails,
A b b i d f
determine the shear force in each nail.
A square box beam is constructed from four planks as shown. Knowing that the spacing between nails is 1.5 in. and the beam is subjected to a vertical shear of magnitude V = 600 lb, determine the shearing force in each nail.
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g