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7/28/2019 Stress Strain Relationship for Mild Steel
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Professional Publications, Inc. FERC
13-1Mechanics of MaterialsStress-Strain Curve for Mild Steel
7/28/2019 Stress Strain Relationship for Mild Steel
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Professional Publications, Inc. FERC
13-2aMechanics of MaterialsDefinitions
Hookes Law
Shear Modulus:
Stress:
Strain:
Poissons Ratio:
Normal stress or strain =
Shear stress = || to the surface
" to the surface
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13-2bMechanics of MaterialsDefinitions
Uniaxial Load and Deformation
Thermal Deformation
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13-3aMechanics of MaterialsStress and Strain
Thin-Walled Tanks
Hoop Stress:
Axial Stress:
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13-3bMechanics of MaterialsStress and Strain
Transformation of Axes
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13-3cMechanics of MaterialsStress and Strain
Five simplified steps to construct Mohrs circle
1. Determine the applied stresses (x, y, xy).2. Draw a set of - axes.
3. Locate the center:
4. Find the radius (ormax):
5. Draw Mohrs circle.
"c =1
2("
x+"
y).
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13-3d1Mechanics of MaterialsStress and Strain
For examples 1 and 2, use the following illustration.
Example 1 (FEIM)The principal stresses (2, 1) are most nearly
(A) 62400 kPa and 14400 kPa
(B) 84000 kPa and 28000 kPa
(C) 70000 kPa and 14000 kPa
(D) 112000 kPa and 28000 kPa
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13-3d2Mechanics of MaterialsStress and Strain
The center of Mohrs circle is at
"max = (30000 kPa)2+ (24000 kPa)2 = 38419 kPa
"
1
= "c
# $max
= (#24000 kPa # 38419 kPa)= #62419 kPa
"2 = "c+ #max = ($24000 kPa+38419 kPa)=14418 kPa
Therefore, (D) is correct.
Using the Pythagorean theorem, the radius of Mohrs circle (max) is:"c =
1
2("
x+"
y) = 1
2(#48000 kPa+0)= #24000 kPa
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13-3d3Mechanics of MaterialsStress and Strain
Example 2 (FEIM):
The maximum shear stress is most nearly
(A) 24000 kPa
(B) 33500 kPa
(C) 38400 kPa
(D) 218000 kPa
Therefore, (C) is correct.
In the previous example problem, the radius of Mohrs circle (max) was
"max = (30000 kPa)2+ (24000 kPa)2
= 38419 kPa (38400 kPa)
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13-3eMechanics of MaterialsStress and Strain
General Strain
Note that "x is no longer proportional to #x.
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13-3fMechanics of MaterialsStress and Strain
Static Loading Failure Theory
Maximum Normal Stress: A material fails if
Or
" # St
" # Sc
This is true of brittle materials.
For ductile materials:
Maximum Shear
Distortion Energy (von Mises Stress)
Tmax
=max"1 # "2
2,
"1 # "3
2,
"2 # "3
2
$
%
&&
'
(
))>Syt
2
"# = 12
#1
$ #2( )
2
+ #1
$ #3( )
2
+ #2
$ #3( )
2%&' (
)*>S
yt
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13-3gMechanics of MaterialsStress and Strain
Torsion
For a body with radius rbeingstrained to an angle , the shear
strain and stress are:
" = r
d#
dz " =G# =Gr
d$
dz
For a body with polar moment of
inertia (J), the torque (T) is:
T=G
d"
dzr
2dA
A# =GJ
d"
dz
The shear stress is:
"#z=Gr T
GJ= Tr
J
For a body, the general angulardisplacement () is:
" =
T
GJdz
0
L
#
For a shaft of length (L), the totalangular displacement () is:
Torsional stiffness:
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13-3hMechanics of MaterialsStress and Strain
Hollow, Thin-Walled Shafts
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13-4aMechanics of MaterialsBeams
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13-4bMechanics of MaterialsBeams
Load, Shear, and Moment Relations
Load:
Shear:
For a beam deflected to a radius of curvature (), the axial strain at a
distance (y) from the neutral axis is "x = #y/$.
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13-4c1Mechanics of MaterialsBeams
Shear and Bending Moment Diagrams
Example 1 (FEIM):
Draw the shear and bending moment diagrams for the following beam.
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13-4c2Mechanics of MaterialsBeams
Shear is undefined at concentrated force points, but just short ofx= 12 m
Rl+Rr = 100 Nm
"
#$
%
&'16 m( ) =1600 N
Rl= (8)(R
r(4)= 0
Therefore, Rl= 533.3 N and Rr= 1066.7 N
So the shear diagram is:
From 0 m to 12 m, V= Rl" 100
N
m
#
$
%&
'
(x= 533.3 N" 100N
m
#
$
%&
'
(x; 0 m < x < 12 m
V(12") = 533.3 N" 100N
m
#
$%
&
'((12 m) = "666.7 N
V=1600 N" 100N
m
#
$%
&
'(x; 12 < x ) 16 m
From 12 m to 16 m, V=V(12")+R
r" (100 N)(x"12)
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13-4c3Mechanics of MaterialsBeams
The bending moment is the integral of the shear.
M= Sdx0
12
" + Sdx12
x
" = #800+ 1600 N#100N
mx
$
%&
'
()
0
12
" dx
= "800 N #m+ 1600 N( )x" 50N
m
$
%
&'
(
)x2
$
%
&'
(
)
12
x
M= 533.3x 50x2; 0 m < x< 12 m
M= "800 N #m+ 1600 N( )x" 50N
m
$
%&
'
()x
2 " 1600 N( ) 12 m( )+ 50N
m
$
%&
'
()12 m( )
2
M= "12800 N #m+ 1600 N( )x" 50N
m
$
%&
'
()x
2
12 m
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13-4c4Mechanics of MaterialsBeams
The bending moment diagram is:
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13-4d1Mechanics of MaterialsBeams
Example 2 (FEIM):The vertical shear for the section at the midpoint of the beam shown is
(A) 0
(B)
(C) P
(D) none of these
Drawing the force diagram and the shear diagram,
Therefore, (A) is correct.
1
2P
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13-4d2Mechanics of MaterialsBeams
Example 3 (FEIM):For the shear diagram shown, what is the maximum bending moment? The
bending moment at the ends is zero, and there are no concentrated couples.
(A) 8 kNm
(B) 16 kNm
(C) 18 kNm
(D) 26 kN
m
Starting from the left end of the beam, areas begin to cancel after 2 m. Starting
from the right end of the beam, areas begin to cancel after 4 m. The rectangle on
the right has an area of 16 kNm. The trapezoid on the left has an area of
(1/2)(12 kN + 14 kN) (2 m) = 26 kNm. The trapezoid has the largest bending
moment.
Therefore, (A) is correct.
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13-4eMechanics of MaterialsBeams
Bending Stress
Deflection
Shear Stress
Note: Beam deflection formulas are given in the NCEES Handbook for
any situation that might be on the exam.
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13-4fMechanics of MaterialsBeams
Example (FEIM):
Find the tip deflection of the beam shown. EI is 3.47 106 Nm2, the
load is 11379 N/m, and the beam is 3.7 m long.
From the NCEES Handbook:
" =w
oL
4
8EI=
11379N
m
#
$%
&
'(3.7 m( )
4
8( ) 3.47)106 N *m2( )= 0.077 m
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13-5aMechanics of MaterialsColumns
Beam-Columns (Axially Loaded Beams)
Maximum and minimum stresses in an eccentrically loaded column:
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13-5cMechanics of MaterialsColumns
Elastic Strain Energy:
Strain energy per unit volume for tension: