Mechanics of Materials Chapter two Stress and strain-axial ...
Transcript of Mechanics of Materials Chapter two Stress and strain-axial ...
MECHANICS OF MATERIALS
CHAPTER THREE TORSION
Prepared by : Dr. Mahmoud Rababah 1
3.1 INTRODUCTION
Transmission shaft
Steam turbine
Electric generator
Transmission shaft
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3.2 - 3.3 DEFORMATION IN A CIRCULAR SHAFT
Every cross-section remains plane and undistorted
i.e. each cross-section rotates as a rigid disk.
This is only applicable for circular cross-sections.
3
: the angle of twist
it is proportional to and L
T
For small shear strain
L
L
4
maxc
The shearing strain varies linearly
with the distance from the axis of
the shaft
SHEARING STRAIN ALONG THE RADIAL
DIRECTION
Shaft radius
5
Hook’s law is applied
Thus, linear variation in shearing
strain leads to linear variation in
shearing stress.
3.4 STRESSES IN THE ELASTIC
RANGE
max max
max
max
but
thus
G
G
c
c
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THE TORSION FORMULA
max
2ma
max
x
2
( )
but
(polar moment of inertia)
(Torsion formula)
A A
A
A
c
J
dA dAc
J
dAc
J dA
T
T
T
T
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POLAR MOMENT OF INERTIA
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max 120 MPa
Find
Example :
6 4 4
max
120 10 (0.03) (0.02)2 4.08 kN.m
0.03o
J
c
Solution :
T
9
1
2
max min
90 mm 0.045 m
120 mm 0.06 m
shafts and are solids of diameter
Find:
1- and in shaft .
2- diameter for 65 MPa.
BC inner
BC outer
all
d C
d C
AB CD d
BC
d
Example :
3
2max
4 4
1min max
2
20 10 0.061 86.2 MPa
(0.06) (0.045)2
64.7 MPa
BC
C
J
C
C
BCT
0
6 kN
20 kN
6 kN
AB
BC
CD
T
T
T
Solution :
M
( / 2)2 65 MPa
77.8 mm
all
AB
d
J
d
ABT
10
80 MPa
50 MPa
Find
1 for not exceeding the maximum shear stress in sleeve
2
all AB
all CD
s
CD
d
max
Example :
T
6 4 4
36
4
1
50 10 (0.08) (0.068)32 2.4 kN.m
0.04
2
2.4 10 ( / 2) 80 10 53.5 mm
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CDCD
CD
ABAB
AB
ss
s
C
J
C
J
dd
d
Solution :
T
T
T
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1000 N.m
56 mm and 42 mm
Determine the maximum shearing stress in both shafts.
AB CDd d
Example :
T
2500 N.mAB
AB CD
Tr r
CDAB
Solution :
TT 4
4
2500 0.02872.5 MPa
(0.028)2
1000 0.02168.7 MPa
(0.021)2
ABAB
AB
CDCD
CD
C
J
C
J
AB
CD
T
T
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100 N.m
21 mm, 30 mm and 40 mm
Determine the maximum shearing stress in the three shafts.
AB CD EFd d d
Example :
T
1
2
4
4
1 2
240 N.m
= 600 N.m
100 0.010555 MPa
(0.010
note: 60 mm a
5)2
240 0.01545.3 MPa
(0.015)2
6
nd 30 mm
AB CD
CD EF
ABAB
AB
CDCD
CD
EFEF
E
CD CD
F
r r
r r
C
J
C
J
J
r r
C
CDABCD
CD EFEF
AB
CD
EF
Solution
TTT
T TT
T
T
T
4
00 0.0247.7 MPa
(0.02)2
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3.5 ANGLE OF TWIST IN THE ELASTIC RANGE
maxmax
(analog
1
us to ) L
C C
L G J G
AJG E
L
P
T
T
For multi-sections
i i
i i i
L
J G
T
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SIGN CONVENTION
and are positive when right hand thumb
is outward of the surface
T
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Example:
/
70 1080 BC CDABA D
L LL
JG JG JG
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4
150 N.m
130 N.m
170 N.m
(0.007)2
150 0.4 130 0.3 170 0.50.2121 radi i
A
J
L
JG JG JG JG
AC
CD
DE
Solution :
T
T
T
T
9
14 mm
80 10 GPa
d
G
Example :
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ANGLE OF TWIST FOR VARIABLE CROSS-SECTION
0
( )
( )
L
d dxJG
xdx
J x G
T
T
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9
max
60 mm (solid shaft), 75 10
Find
1
2 C
d G
Example :
max4
/ /
1.5
4 9 4 90
3
1800 0.031 42.4 MPa
(0.03)2
1200 2000 N.m
1200 N.m
1200 0.8 1200 2000
(0.03) 75 10 (0.03) 75 102 2
5.344 10 rad
C C B B A
C
C
C
J
x
xdx
max
AB
BC
Solution :
T
T
T
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or apply superposition
=
+
1 2
14 9
1.
2
5
4 90
3
2
1200 2.3
(0.03) 75 102
2000
(0.03) 75 102
5.344 10 rad
C C C
C
C
C B
xdx
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RELATIVE TWIST ANGLES
/
/
E B E B
E B
TL
JG
21
22.5 N.mAB CDr r
CDABCD
Solution :
TTT
20 mm
80 GPa
45 N.m
d
G
AB
Example :
T
22
4 9
/4 9
/
22.5 1.50.0269 rad
(0.01) 80 102
0.0134 rad
45 20.0716 rad
(0.01) 80 102
0.085 rad
CDC
C C B B
B
ABA B
A A B B
L
JG
r r
L
JG
CD
AB
T
T
ENGAGED TWIST
ANGLES RELATIONS
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is steel
77 GPa
80 MPa
is Brass
38 GPa
50 MPa
Find and
steel
all steel
brass
all Brass
A
AB
G
CD
G
max
Example :
T
4 9 4 4 9
1005 0.3 1005 0.2
(0.02) 77 10 (0.04) (0.034) 38 102 2
0.01833 rad
AB CDA
steel steel brass brass
A
A
L L
J G J G
max maxT T
6
4
6
4 4
max
0.0280 10
(0.02)2
0.0450 10 2.4 kN
1.005 kN.
.m
(0.04) (0.03
m
4)2
all steel
all Brass
T
C
J
C
J
max
maxmax
Solution :
T
T
T
TT
24
25 mm
75 GPa
Find A
d
G
Example :90 N.mF
E
r
r
F ET T
FBD
25
3
4 9 4 9
3
/4 9
/
30 0.25 90 0.7520.86 10 rad
(0.0125) 75 10 (0.0125) 75 102 2
0.03129 rad
60 0.255.215 10 rad
(0.0125) 75 102
2.09 deg.
F
F F E E
E
A E
A E A E
r r
L
JG
Solution :
T
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60 mm
80 mm
2 kN.m, 4 kN.m
75 GPa
Find
and
AC
EH
A C
d
d
G
1 2
Example :
T T
FBD
8 kN.mD
B
r
r D BT T
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3
4 9
/
3
2/
4 9
/
1/
8 10 0.60.0159 rad
(0.08) 75 1032
1000.0159 0.0212 rad
75
4 10 0.60.025 rad
(0.06) 75 1032
0.025 0.0212 0.0462 rad
D EDD
ED
DB D
B
A B A B
ABA B
AB
A
C B C B
C B
T L
J G
r
r
T L
J G
T L
Solution :
3
4 9
2 10 0.90.01886 rad
(0.06) 75 1032
0.01886 0.0212 0.04 rad
BC
BC
C
J G
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0 0 (1) x A BM T T T
/ 0
0 (2)
From Eqs. 1 and 2
and
A B
AC BC
BC AC
L L
JG JG
L L
L L
A B
A B
T T
T T T T
3.6 STATICALLY
INDETERMINATE SHAFTS
one equation and two unknowns
the compatibility condition is
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Example:
d = 20 mm
Find TA and TB
0 800 500 0 (1) x B A
Solution :
M T T
30
/ 0
0.2 (800 ) 1.5 (300 ) 0.30 (2)
645 N.m
345 N.m
A B
JG JG JG
B B B
B
A
T T T
T
T
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4 4 9 4 9
250 0 (1)
(2)
(0.02) (0.01) 80 10 (0.01) 36 102 2
st br
L L
st br
st br
Solution :
T T
T T
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Example:
Tube of steel and core of brass
T = 250 N.m
Gst = 80 GPa, Gbr = 36 GPa.
max4 4 9
1
min max2
max4 9
min
From Eq. 1 and 2, we get
242.72 N.m
7.28 N.m
0.0220.6 MPa
(0.02) (0.01) 80 102
0.0120.6 MPa 10.3 MPa
0.02
0.014.63 MPa
(0.01) 36 102
0
st
st st
brbr
br
C
C
T
st
br
st
T
T
T
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3.7 DESIGN OF TRANSMISSION SHAFTS
2P w f T T
Power in Watt (N.m/s)
Angular velocity in rad/sec
Frequency in Hz (1/s)
Example:
a solid shaft is used to transmit 3750 W at angular 175 rpm. If
allowable shear is 100 MPa, find the diameter of the shaft.
2175 18.33 rad/sec
60
204.6 N.m
10.92 mm ( 22 mm)all
w
P T w T
T CC d
J
Solution :
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3.8 STRESS CONCENTRATION IN CIRCULAR
SHAFTS
Stress concentration occurs when variation
in the cross-section occurs
35
TCK
J
36
x
T
3.12 TORSION OF NON-CIRCULAR
MEMBERS
37
max 2
1
3
2
From elasticity theory
c ab
L
c ab G
T
T
38
3.15 THIN WALLED HOLLOW SHAFTS
0
( ) ( )
Thus,
constant (Shear flow)
A A B Bt x t x
t q
x
A B
F
F F
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( ) ( )
but
1
2
2
ave
ave
m
ave m
d h dF h tds
h tds q hds
dA hds
tA
T
T
T 2ave
m
T
tA
40
Example:
20.035 0.057 0.002 m
1.75 MPa2
2.92 MPa2
m
A
A m
B
B m
A
t A
t A
T
T
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END OF CHAPTER THREE
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