FORCES TENSION, COMPRESSION, SHEAR, AND TORSION Mr. Ruddle Construction Technology.
Shear _ Torsion - Handout
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Transcript of Shear _ Torsion - Handout
10/15/2012
1
Shear & Torsion
Shear stressIf two equal and opposite parallel forces Q, not in the
same line, act on parallel faces of a member then it is
said to be loaded in shear.
A shear stress () is defined as a stress which is
applied parallel or tangential to a face of a material.
Shear stressThe formula to calculate average shear stress is:
where = shear stress;F = force applied;A = cross sectional area.
Shear stress
AF
load resisting area
loadshear )( stress shear
The shear stress will always be tangential to the area on which it acts.
Example I:In a guillotine, Q is the total force exerted bythe blade. This force is balanced by an equaland opposite force provided at the edge of thetable.
The area resisting shear is measured by theplate thickness multiplied by the length of theblade.
Shear stress
Example II:
In a punching operation the area of the
resisting shear would be the plate thickness
multiplied by the perimeter of the hole
punched.
Shear stress
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The rivet is commonly loaded in shear:
Riveted Joints
In single-shear the area resisting
shear is the cross-sectional area of
the rivet, d2/4, where d is the
diameter of the rivet.
In double-shear the resisting area
is twice the area of section of the
rivet, and the load which it can be
carried is theoretically twice that in
the single shear.
Riveted Joints
The single shear takes place on the single plane and the
shear area is the cross - sectional of the rivet, whereas the
double shear takes place in the case of Butt joints of rivets
and the shear area is the twice of the X - sectional area of
Clevis
Riveted Joints
Torque
Torque, also called moment or moment of force, is the
tendency of a force to rotate an object about an axis,
fulcrum, or pivot. A torque can be thought of as a twist.
The magnitude of torque depends on three quantities:
First, the force applied; second, the length of the lever
arm connecting the axis to the point of force
application; and third, the angle between the two.
L) & Fbet (angle sinx L Length,x F , Force T ,Torque
Power
(kW) 1000
T*N*2 ower P where
N – number of revolutions per second;
T – torque (Nm).
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The ultimate shear stress or strength is defined
as:
Ultimate shear stress
shear resisting areaload punch maximum
Allowable working stress-factor of safety
The most suitable strength or stiffness criterion for
any structural element or component is normally
some maximum stress or deformation which must
not be exceeded. In the case of stresses the value
is generally known as the maximum allowable
working stress.Because of uncertainties of loading conditions, designprocedures, production methods, etc., designers generallyintroduce a factor of safety into their designs, defined asfollows:
stress working allowablestress maximum safety of factor
Factor of Safety
A factor of safety of 3 implies that the design is
capable of carrying three times the maximum stress
to which it is expected the structure will be
subjected in any normal loading condition.
Factor of Safety
Values are normally selected on the basis of a
consideration of the social, human safety and
economic consequences of failure. Typical values
range from 2.5 (for relatively low consequence,
static load cases) to 10 (for shock load and high
safety risk applications).
Load Factor
In some loading cases, e.g. buckling of struts, neither the
yield stress nor the ultimate strength is a realistic criterion for
failure of components. In such cases it is convenient to
replace the safety factor, based on stresses, with a different
factor based on loads. The load factor is therefore defined
as:
load working allowablefailureat load factor load
This is particularly useful in applications of the so-called plastic limit
design procedures.
Coupling Flanges
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Shear Strain
The object is rigidly fixed at one face and subject to a stress
q on the other parallel face. The object deforms sideways.
The shear strain is defined as the angle of deformation, θ in
radians. Given that the angle Φ is small,
lx
The shear strain is defined as theratio of the distance deformed tothe height.
Module of Rigidity
The modulus of rigidity, G is given by:
strain,shear stress,shear
G
G
A shaft is to be fitted with a flanged coupling having 8
bolts on a circle of diameter 150 mm. The shaft may be
subject either to a direct tensile load of 400 kN or to a
twisting-moment of 18 kNm. If the maximum direct and
shearing stresses permissible in the bolt material are 125
MN/ m2 and 55MN/m2 respectively, find the minimum
diameter of bolt required. Assume each bolt takes an
equal share of the load or torque.
Using this bolt diameter and assuming only one bolt to
carry the full torque what would then be the shearing
stress in the bolt?
Torsion of a Thin Tube
Torsion of a thin tube
Consider the thin tube of mean radius r, having a wall
thickness (t is very small compared with r).
If a torque T is applied to both ends of the tube, one end
will twist relative to the other. A strip AB parallel to the
tube axis will distort to AB'.
Torsion of a thin tubeIf it is assumed that the displacement BB' is small
compared with the length of tube AB, then AB' will be
approximately straight.
Then angle < BOB' is the angle of twist θ of the length
AB. The shear strain is:rad r
ABBB' strain,Shear
l
since BB' = rθ , and AB = length of tube l.
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Torsion of a thin tube
rT
F radiustorque
force,Shear
rt2
areaforceshear
stress,Shear
F
The shear force on the cross-section of the tube is:
This force acts on area 2rt, since the tube is thin.
Therefore
tr2T
rt2 2
rT /
then,/r and rigidity, of modulus theG, / since Also l
G /r
l
r l
GHence,
Notes:
For a given torque the angle of twist varies directly with the length;
In these formulae, the twist must be in radians.
Torsion of Solid Shafts
Assumptions:1. The shaft is composed of a succession of thin
concentric tubes;
2. Each thin tube carries shear forceindependent of, and without interfering with,its neighbours.
3. Lines which are radial before twisting areassumed to remain radial after twisting;
4. The shaft is not stressed beyond the elasticlimit.
Area, dA = 2r x dr
If is the shear stress at radius r, then
Shear force on tube = 2r x dr x
Torque carried by tube = 2r x dr x x r
= 2r2 dr
lr
G
We know that
rl
G
drx rG
x r2 tube by carried Torque 2
l
dr rG
2 3
l
The whole torque T carried by the solid shaft is the sum of
all the elementary torques, ie
dr rG 2 TR
03
l
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Since radial lines before twisting remain radial after
twisting, is the same for all the thin tubes making up the
shaft. Also G and l are constant, therefore
dr r 2 G
TR
03
l pI G l
Ip is the polar second moment of area of a shaft
of circular section.
dr 2 IR
0p 3r
Rearranging G IT
p l
l
G Since
rτ
r G
lpIT
A useful re-arrangement
pGIT l
Another useful re-arrangement Important points:The angle of twist varies directly with length l ;
SincepI
Tr
for a given torque T, the shear stress q is
proportional to the radius r. Thus the
maximum shear stress occurs at the outside
surface where r=d/2, and the shear stress at
the centre of the shaft is zero.
A thin steel tube 90 mm inside diameter is subjected toa torque of 500Nm.
a) If the shear stress is not to exceed 28 MN/m2,calculate the tube thickness.
b) If the twist is not to exceed 2.5mm of arc on a600mm length what would be the thicknessrequired?
G = 84 GN/m2.
A thin tube 1.5 mm thick, 80 mm mean diameter is
subjected to a torque of 350 Nm. Calculate (a) the
shear stress in the tube, (b) the twist on a 1 m length.
G = 84 GN/m2.
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Twisting of Hollow shafts
dr r 2 G
TR
03
l
If d2 and d1 are the outside and inside diameters of
a hollow shaft subject to a twisting moment T then
the equation
may be rewritten as:
dr r 2 G T2/d
2/d
32
1
l
Twisting of Hollow shafts
dr 2 I2
1
d
dp
2
2
3/
/r
32)d - (d
I4
14
2p
The maximum shear stress for a given torque is again
at the outside fibres of the shaft, where r = d2/2.
r
pIT
Since
then
r . pI
T
Comparison of shear stress distributions in a solid and a hollow shaft
Stiffness and Strength
The stiffness or torsional rigidity of a shaft is the
torque to produce unit angle of twist. Thus if a
torque T produces a twist then
lpIG
T stiffness
Stiffness and Strength
The strength of a shaft is measured by the torque it
can transmit for a given permissible value of the
maximum shear stress.
For a given shear stress the strengths of two shafts
are the ratio of the corresponding torques.
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Power and Torque
(kW) 1000
T*N*2 ower P where
N – number of revolutions per second;
T – torque (Nm).
Compare the torsional stiffness of a solid
shaft 50 mm diameter, 300 mm long, with
that of a hollow shaft of the same
material having diameters 75 mm, 50 mm
and length 200 mm.
The propeller shaft of an aircraft engine
is steel tubing of 75 mm external and 60
mm internal diameter. The shaft is to
transmit 150 kW at 1650 rev/min. The
failing stress in shear for this shaft is 140
MN/m2. What is the safety factor?
7.87
Angle of Twist in Elastic Range
GITL
p
Angle of Twist in Elastic Range
i iip
ii
GILT
Angle of Twist in Elastic Range
L
0 p G (x)Idx T(x) φ
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Angle of Twist in Elastic Range
L
0 p G (x)Idx T(x) φ
(x)I J(x) p
Sign Convention
Sign Convention Sign Convention
A shaft is made of a steel alloy having an allowable shear
stress of allow = 120 N/mm2. If the diameter of the shaft is 15
mm, determine the maximum torque T that can be
transmitted.
What would be the maximum torque T′ if a 10-mm-diameter
hole is bored through the shaft? Sketch the shear-stress
distribution along a radial line in each case.
The solid shaft of radius r is subjected to a torque T.
Determine the radius r′ of the inner core of the shaft that
resists one-quarter of the applied torque (T/4). Solve the
problem by using the torsion formula.
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The shaft has an outer diameter of 25 mm and an inner diameter
of 20 mm. If it is subjected to the applied torques as shown,
determine the absolute maximum shear stress developed in the
shaft. The smooth bearings at A and B do not resist torque.
The steel shaft is subjected to the torsional loading shown.
Determine the absolute maximum shear stress in the shaft and
sketch the shear-stress distribution along a radial line where it is
maximum.
Torsion of Noncircular Members
3 - 58
Torsion of Noncircular Members
• At large values of a/b, the maximum shear stress and angle of twist for other open sections are the same as a rectangular bar.
GabcTL
abcT
32
21
max
• For uniform rectangular cross-sections,
• Previous torsion formulas are valid for axisymmetric or circular shafts
• Planar cross-sections of noncircular shafts do not remain planar and stress and strain distribution do not vary linearly