122 MECHANICAL ENGINEERING PRINCIPLES
However, from Table 7.1, page 91, the polar second
moment of area of a circle,
J=
πR^4
2
,
hence, T=
Gθ
L
J
or
T
J
=
Gθ
L
( 10. 5 )
Combining equations (10.3) and (10.5) gives:
τ
r
=
T
J
=
Gθ
L
( 10. 6 )
For a solid section of radiusRor diameterD,
J=
πR^4
2
or
πD^4
32
( 10. 7 )
For a hollow tube of circular section and of internal
radiusR 1 and external radiusR 2
J=
π
2
(
R 24 −R^41
)
( 10. 8 )
or, in terms of external and internal diameters ofD 2
andD 1 respectively, (see Problem 12, Chapter 7,
pages 93),
J=
π
32
(
D^42 −D^41
)
( 10. 9 )
The torsional stiffness of the shaft,k, is defined by:
k=
GJ
L
( 10. 10 )
The next section of worked problems will demon-
strate the use of equation (10.6).
10.3 Worked problems on the twisting
of shafts
Problem 1. An internal combustion engine
of 60 horsepower (hp) transmits power to the
car wheels of an automobile at 300 rev/min
(rpm). Neglecting any transmission losses,
determine the minimum permissible diameter
of the solid circular section steel shaft, if the
maximum shear stress in the shaft is limited
to 50 MPa. What will be the resulting angle
of twist of the shaft, due to the applied
torque, over a length of 2 m, given that the
rigidity modulus,G=70 GPa? (Note that
1hp= 745 .7 W).
Power=60 hp=60 hp× 745. 7
W
hp
=44742 W
From equations (9.1) and (9.2), page 110,
power=Tω= 2 πnTwatts, wherenis the speed
in rev/s
or 44742 = 2 π
rad
rev
×
300
60
rev
s
×T
= 31. 42 Trad/s
from which, T=
44742 W
31 .42 rad/s
i.e. torqueT=1424 N m
(since 1 W s=1Nm)
From equation (10.6),
τ
r
=
T
J
i.e.
50 × 106
r
N
m^2
=
1424 N m
πr^4
2
and
r^4
r
=
1424 × 2
π× 50 × 106
m^3
from which, r^3 =
1424 × 2
π× 50 × 106
or shaft radius,r=^3
√(
1424 × 2
π× 50 × 106
)
= 0 .0263 m
Hence, shaft diameter,d= 2 ×r= 2 × 0. 0263
= 0 .0526 m
From equation (10.6),
τ
r
=
Gθ
L
from which,θ=
τL
Gr
=
50 × 106
N
m^2
×2m
70 × 109
N
m^2
× 0 .0263 m