Basic Stresses
Transcript of Basic Stresses
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Dr. D. B. Wallace
Basic Stress Equations
Internal Reactions:
6 Maximum(3 Force Components
& 3 Moment Components)
Normal Force
)(
)(
Shear Forces
z
x
y
PVy
Vx
Torsional Moment)(
)(Bending Moments
z
x
y
TMy
Mx
or TorqueForce Components Moment Components
"Cut Surface" "Cut Surface"
Centroid ofCross Section
Centroid ofCross Section
Normal Force:
Axial Force
z
x
y
P
Centroid
Axial Stress
"Cut Surface" =P
Al Uniform over the entire cross section.
l Axial force must go through centroid.
Shear Forces:Cross Section
y
Aa
Point of interest
LINE perpendicular to V through point of interest
= Length of LINE on the cross section
= Area on one side of the LINE
Centroid of entire cross section
Centroid of area on one side of the LINE
= distance between the two centroids
= Area moment of inertia of entire cross sectionabout an axis pependicular to V.
V
b
Aa
y
I
"y" Shear Force
z
x
y
Vy
"x" Shear Force
z
x
y
Vx
=
V A y
I b
ab g
Note: The maximum shear stress for common cross sections are:
Cross Section: Cross Section:
Rectangular:
max = 3 2 V A Solid Circular: max = 4 3 V A
I-Beam or
H-Beam: webflange max = V Aweb
Thin-walled
tube: max = 2 V A
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Basic Stress Equations Dr. D. B. Wallace
Torque or Torsional Moment:
Solid Circular or Tubular Cross Section:
r = Distance from shaft axis to point of interest
R = Shaft RadiusD = Shaft Diameter
JD R
JD D
for solid circular shafts
for hollow shaftso i
=
=
=
4 4
4 4
32 2
32
e jTorque
z
x
y
T
"Cut Surface"
=T r
J
max
max
=
=
16
16
3
4 4
T
D
T D
D D
for solid circular shafts
for hollow shaftso
o ie j
Rectangular Cross Section:
Torque
z
x
y
T
Centroid
Torsional Stress
"Cut Surface"
1
2
a
b
Note:a > b
Cross Section:
Method 1:
max .= = + 12 23 1 8T a b a bb g e j ONLY applies to the center of the longest side
Method 2:
1 21 2
2,
,
=
T
a b
a/b
1.0 .208 .208
1.5 .231 .269
2.0 .246 .309
3.0 .267 .355
4.0 .282 .378
6.0 .299 .402
8.0 .307 .414
10.0 .313 .421
.333 ----
Use the appropriate from the table
on the right to get the shear stress at
either position 1 or 2.
Other Cross Sections:
Treated in advanced courses.
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Basic Stress Equations Dr. D. B. Wallace
Bending Moment
"x" Bending Moment
z
x
y
z
x
y
Mx
My
"y" Bending Moment
=
=
M y
I and
M x
I
x
x
y
y
where: Mx and My are moments about indicated axes
y and x are perpendicular from indicated axes
Ix and Iy are moments of inertia about indicated axes
Moments of Inertia:
h
c
b D
c RIb h
h
Z Ic
b h
is perpendicular to axis=
= =
3
2
12
6
ID R
Z Ic
D R
=
=
= =
=
4 4
3 3
64 4
32 4
Parallel Axis Theorem:I = Moment of inertia about new axis
I I A d= + 2
centroid
d
new axis
Area, A I = Moment of inertia about the centroidal axisA = Area of the region
d = perpendicular distance between the two axes.
Maximum Bending Stress Equations:
max =
323
M
D
Solid Circularb g max =
62
M
b h
Rectangulara fmax =
=M c
I
M
Z
The section modulus, Z, can be found in many tables of properties of common cross sections (i.e., I-beams,
channels, angle iron, etc.).
Bending Stress Equation Based on Known Radius of Curvature of Bend, .
The beam is assumed to be initially straight. The applied moment, M, causes the beam to assume a radius of
curvature, .
Before:
After:
M M
= Ey
E = Modulus of elasticity of the beam material
y = Perpendicular distance from the centroidal axis to the
point of interest (same y as with bending of a
straight beam with Mx).
= radius of curvature to centroid of cross section
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Basic Stress Equations Dr. D. B. Wallace
Bending Moment in Curved Beam:
Geometry:
r
r
e
rrn
o
i
centroidcentroidal
neutral axis
axis
o
i
ynonlinear
stressdistribution
M
c
ci
o
rA
dA
e r r
n
area
n
=
=
z
A = cross sectional area
rn = radius to neutral axis
r = radius to centroidal axis
e = eccentricity
Stresses:
Any Position: Inside (maximum magnitude): Outside:
=
+
M y
e A r ynb gi
i
i
M c
e A r=
o
o
o
M c
e A r=
Area Properties for Various Cross Sections:
Cross Section rdA
area z A
t
hriro
r
Rectangle
rh
i +2
tr
r
o
i
FHG
IKJ
ln h t
t
hri
ro
r
Trapezoid
ot i
rh t t
t ti
i o
i o
+ +
+
2
3
b gb g
For triangle:
set ti
or to
to 0
t tr t r t
h
r
ro i
o i i o o
i
+
FHG
IKJ
ln ht ti o
+
2
r
Hollow Circle
a
b
r 22 2 2 2
LNM
OQP r b r a
a b2 2e j
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Basic Stress Equations Dr. D. B. Wallace
Bending Moment in Curved Beam (Inside/Outside Stresses):
Stresses for the inside and outside fibers of a curved beam in pure bending can be
approximated from the straight beam equation as modified by an appropriate
curvature factor as determined from the graph below [i refers to the inside, and o
refers to the outside]. The curvature factor magnitude depends on the amount of
curvature (determined by the ratio r/c) and the cross section shape. r is the radius
of curvature of the beam centroidal axis, and c is the distance from the centroidal
axis to the inside fiber.
M
M
CentroidalAxis
r
c
Inside Fiber: i iKM c
I=
Outside Fiber: o oKM c
I=
0
1.0
0.5
1.5
2.0
2.5
3.0
3.5
4.0
1 2 3 4 5 6 7 8 9 10 11
K
i
o
Curvature
Factor
Amount of curvature, r/c
K r
b
c
b
c
b
c
c
b/2
b/3
b/4b/8
b/6
B A B A
B A
BA
B A
B A B A
Values of K for inside fiber as ati A
Values of K for outside fiber as at
oB
U or T
Round or Elliptical
Trapezoidal
I or hollow rectangular
Round, Elliptical or Trapezoidal
U or TI or hollow rectangular
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