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7/30/2019 Theories of Yielding.pdf
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Theories of Yield/Failure
Keeping the condition that satisfied the material which let to failure. i.e. it give material
indication of the failure at given point on material.
There are component of machine shaft which is made of some material. There are load applied toshaft such as force or bending moment. When this load are acting, there will some point in the
material which will be most critically loaded and at the condition at which material failure is give
by Theory of failure or yield.
Twokindsofstressstates(a)simplestressstate(b)compoundstressstateThe yield strength or yield point of a material is defined in engineering as the stress at which a
material begins to deform plastically. Before yield point the material is deforms elastically.
It is often difficult to precisely define yielding due to the wide variety of stress-strain curves
exhibited by real materials. In addition there are several possible ways to define yielding.
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Figure 1 tensional stress and strain diagram
True elastic limit: the lowest stress at which dislocations move. This defined is rarely used, since
dislocation move at very low stresses, and detecting such movement is very difficult.
Proportionality limit: up to this amount of stress, stress is proportional to strain (Hookes law) so
the stress-strain graph is a straight line, and the gradient will be equal to the elastic modulus of
the material.
Elastic limit (yield strength) beyond the elastic limit, permanent deformation will occur. Thelowest stress at which permanent deformation can be measured.
Yield point: The point in the stress-strain curve at which the curve levels off and plastic
deformation begins to occur.
Failure modes
Excessive elastic Deformation Yielding Fracture
Stretch, twist, or bending Plastic deformation atroom temperature
Sudden fracture of brittlematerial
buckling creep at elevatedtemperature
Fatigue (progressive fracture )
vibration yield stress is theimportant design
factor
Stress rupture atelevated temperatures
Ultimate stress is theimportant design factor
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Elastic deformation is temporary (reversible) and involves bond stretching. Plastic deformation is permanent (irreversible), and involves bond breaking. Fracture is catastrophic.
Effect of loading at a point
3-D x,, y, z, xy, yz ,zx and x, y, z
Principle stress and strain 1,2, 3 and 1, 2, 3
2-D x,, y, xy Plane stress
1,2, and 1, 2
Failure in tensile test Parameter
1) Maximum Principal stress
2) Maximum shear stress
3) Maximum Principal Strain
4) Total Strain Energy Density
5) Distortion Energy Density
Therefore, now we can say that the yielding of a material has been due to the Maximum
Principal stress,Maximum shear stress, Maximum Principal Strain, Total Strain Energy Density,
Distortion Energy Density. Basically, we can say that yielding phenomenal is based on stress and
strain of material which is under an applied load.
y==1
2max
y=
E
y =
E
yS
2
2
=
Ss vd S=
Gy
6
2
=
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Five Criteria of Failure
1) Maximum Principal Stress Criterion ( Rankine)2) Maximum Shear Stress criterion (Tresca)3) Maximum Principal Strain Criterion (St Venant)4) Maximum Strain Energy Density Criterion ( Haigh or Beltrami)5) Maximum Distortion Energy Density Criterion (Von-Mass)
Maximum Principle Stress Theory
Theories of yielding are generally expressed in terms of principle stress, since those completely
determine general states of stress. The elements of material shown in Fig. 2 (a) is subjected to
three principle stresses, and the convection to be used is that 1 >2 >3.The maximum principlestress theory, often attributed to Rankine, states that yielding will occur
in a material under complex stress when yt, in a simple tension test on the same material.
Yielding could also occur if the minimum stress 3, were compressive and reached the value of
yield stress in a simple compression test. Those statements may be written as
1=yt 3=ytfor yielding stress to occur.
Figure 2
Maximum Principle Strain Theory.St.Venant postulated that yielding commences when the maximumprinciple strain(tensile), 1
was equivalent to the strain corresponding to the yield stress in simple tension. For yielding incompression the minimum principle strain, 3, would equal the yield strain in simple
compression. If the strains are expressed in terms of stress, then
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=1 ( )[ ]3211
+E
And yield occurs when compression equalsE
Yt
( ) Yt=+ 321
Or compression
( ) Yt=+ 213
Maximum shear stress Criterion (Tresca)
Statement of the theory
When Yielding occurs in any material, the maximum shear stress at the point of failure equals or
exceeds the maximum shear stress when yielding occurs in the tension test specimen.
The theory applies to ductile materials only, because it is based on yielding.
The three-dimensional (triaxial) stress situation.
In the three-dimensional stress situation, the state of stress at a particular location is fully defined
by three principal stresses 1 , 2 , 3 .
Maximum shear stress at a location of the element
The extreme values of shear stresses 231312 ,, , in each of the three principal planes are then
given by the expressions:
2
2112
= ,
2
3113
= ,
2
3223
=
Expressing the principal stresses in the order of magnitude and sign 321 ff
Then the maximum shear stress is given by 23113
=
The case of Simple Tension Test When Yielding Occurs
For the simple tension test specimen, the three principal stresses when yielding occurs are:
1 = yS , 2 =0, 3 =0
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The maximum shear stress then becomes22
0
2
31max13
yy SS=
=
==
The case of three Dimensional Stress when Yielding Occurs
The maximum shear stress theory of failure states:
When Yielding occurs in any material, the maximum shear stress at the point of failure equals or
exceeds the maximum shear stress when yielding occurs in the tension test specimen.
22
31max
yS=
=
The above equation implies that the shear yield strength of the material2
ysy
SS =
But from analysis of plane stress situation, the maximum shear stress in plane stress is also given
in terms of plane stress elements
22
max2
xyyx
+
=
Design Equation Based on the Maximum Shear Stress Theory
This is derived by adjusting the shear yield strength of the material with an appropriate factor of
safety ..sf . The design equation then becomes:
..*2..2
31max
sf
S
sf
S ysy==
=
OR
..*2..2
22
maxsf
S
sf
S ysyxy
yx==+
=
for plane stress situation
Total Strain energy Theory
The theories put forward so far have postulated a criterion for yielding in terms of a limit value
of stress or strain. The present theory, as proposed by Beltrami, and also attributed to Haigh, is
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based on a critical value of the total strain energystored in the material, and this is a product of
stress and strain.It has been shown earlier that the work done in deformation or the stored elastic strain energy
may be written xW2
1or
2
12
1
=Ax
xW
per unit volumeIn a 3D stress system, the total strain energy is
332211 2
1
2
1
2
1++=UT
Now using a stress-strain relationship, the principal strain may be written as
( )[ ]32111
+=E
( )[ ]1322 1 += E
( )[ ]12331
+=E
Substituting for1, 2, 3 and rearranging it,
( ) ( ) 133221321 2222
2
1++++=
E
v
EUT
Yielding is said to occur when the above equals to the total energy at yield in simple tension. Ie.
By letting 2= 3=0 and 1=yt.
Therefore ( ) 1332213212222
2 ++++= vYt So
E
Yt
TU 2
2
=
In 2D system, 3=0 and
( ) 213212222
2v
Yt++=
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Distortion Energy Theory of Failure
Strain Energy due to Change of Volume (Hydrostatic stress) only
The stress that causes change of volume only (hydrostatic stress) may be considered as the
average of the three principal stresses av , and derived from the expression:
=av 3
321 ++
Substituting for the hydrostatic stress av , into equation strain theory equation yields:
=vU( )[ ]22 323
2
1avav
E
=vU[ ]
21
2
32
E
av=
[ ] 22
213av
E
Substituting the value of av into equation above equations yields:
=vU [ ]2
321
32213
++
E= [ ] ( )2321
2*9213 ++E
=vU[ ]
( )23216
21
++
E=
[ ]( )[ ]313221232221 2
6
21
+++++
E
=vU ( )[ ]313221
2
3
2
2
2
12
6
21
+++++
E
This vU is the strain energy per unit volume caused by the uniform (hydrostatic) stress, which is
part of the three principal stresses 1 , 2 , 3 .
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Distortion Energy at the location of principal stresses 1 , 2 , 3
The distortion energy can then be obtained as the difference between the total strain energy at thelocation of principal stresses, and the strain energy due to the hydrostatic portion of the stresses
at the same location. The distortion energy is then derived from the expression:=dU U - vU
Where,
=dU Distortion energy in the element at the location of principal stresses 1 , 2 , 3
=U ( )[ ]313221232221 22
1 ++++
E
=vU ( )[ ]313221232221 26
21
+++++
E
Therefore,
dU = ( )[ ]313221232221 22
1 ++++
E- ( )[ ]313221232221 2
6
21
+++++
E
dU = ( ) ( )[ ]313221232221 636
1 ++++
E-
( ) ( ) ( )[ ]313221232221313221232221 2*2*226
1 +++++++++
E
dU =( ) ( ) ( )
( ) ( ) ( )
++++++++
++++++
3132212
32
22
1313221
23
22
21313221
23
22
21
2*2*22
63
6
1
E
dU =( ) ( )
( ) ( )
+++++
++++
23
22
21313221
3132212
32
22
1
*22
22
6
1
E
dU = ( )( ) ( )( )[ ]222261
3132212
32
22
1 ++++++ E
dU =( ) ( ) ( )[ ]313221232221
6
221
++++
+
E
dU =( ) ( ) ( )[ ]313221232221
3
1
++++
+
E
But
( )3132212
32
22
1 ++++ =( ) ( ) ( )
2
231
232
221 ++
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Therefore
dU =( )
( ) ( ) ( )( )[ ]2312322213*2
1
++
+
E
dU = ( ) ( ) ( ) ( )( )[ ]23123222161 +++E
The case of Simple Test When Yielding Occurs
For the simple tension test specimen, the three principal stresses when yielding occurs are:
1 =yt, 2 =0, 3 =0
Substituting for the principal stresses
dU =( ) ( ) ( ) ( )( )[ ]222 0000
6
1++
+
ytyt
E
dU =( ) [ ]22
6
1yt
E
+
dU =G
yt
6
2
per unit volume
The case of three Dimensional Stress When Yielding Occurs
The distortion energy theory of failure states:
When Yielding occurs in any material, the distortion strain energy per unit volume at the point of
failure equals or exceeds the distortion strain energy per unit volume when yielding occurs in the
tension test specimen.
This can be restated that when yielding occurs in any situation:
dU =( )
( ) ( ) ( )( )[ ]2312322216
1
++
+
E
EQUALS
dU = ( )[ ]2
26
1yt
E +
( ) ( ) ( )2312
322
21 ++ =2
2 yt
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( ) ( ) ( )
++
2
231
232
221
= yt
Equivalent (Von-Mises) Stress
The expression on the left hand side of above equation is therefore considered as the equivalent
stress e , which causes failure by yielding. The equivalent stress is then given by:
e =( ) ( ) ( )
++
2
231
232
221
The equivalent stress e is also referred to as Von Mises stress.
Design Equation Based on the Distortion Energy Theory
This is derived by adjusting the yield strength of the material in simple tension with anappropriate factor of safety ..sf The design equation then becomes:
e =( ) ( ) ( )
++
2
231
232
221 =
..sf
yt
Application of the Design Equation
The principal stresses 1 , 2 , 3 are first determined by stress analysis. Such analysis describes
the principal stresses as a function of the load carried, and the geometry and dimensions of the
machine or structural element.
The equivalent stress in the design equation is then expressed in terms of the dimensions of the
machine or structural element, while the right hand side is the tensile yield strength of thematerial.
The factor of safety is simply a number chosen by the designer. The factor of safety togetherwith the strength of the material, gives the working
1(design, allowable) stress expected in the
machine part. The solution to the design equation then gives the minimum dimensions required
to avoid failure of the element by yielding.
SummaryMany experiments have been concluded under complex stress conditions to study the behaviour
of metals and test the validity of the foregoing theories. It has been shown that hydrostatic
pressure, and by inference hydrostatic tension, does not cause yielding. Now any complex stresssystem can be regarded as a combination of hydrostatic stress and a function of the differences of
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principle stress, and therefore a yield criterion such as that of Tresca or von Miseswhich is based
on principle stress difference would seem to be the most logical. It is now well established thatfor ductile metals, exhibiting yielding and subsequent plastic deformation, the shear strain energy
theory correlates best with material behavior. The maximum shear stress theory, although not
quit so consistent as the former, gives fairly reasonable prediction and is some times used in
design by virtue of its simpler mathematical form. The other theories are no longer used forductile metals, some being positively unsafe.
Examples 1
Given the material Yt, x, vand xy find the safety factors for all the applicable criteria.
(a)Pure alumimumYt=30MPa , x= 10MPa, y= -10MPa andxy= 0MPa
Example 2
The cantilever tube shown is to be made of 2014 aluminum alloy treated to obtain a specified
minimum yield strength of 276MPa. We wish to select a stock size tube (according to the table
below). Using a design factor of n=4. The bending load isF=1.75kN, the axial tension isP=9.0kNand the torsion is T=72N.m. What is the realized factor of safety?
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Example 3:
The factor of safety for a machine element depends on the particular point selected for the
analysis. Based upon the DET theory, determine the safety factor for points A and B.
This bar is made of AISI 1006 cold-drawn steel(Yt=280MPa) and it is loaded by the forces
F=0.55kN, P=8.0kN and T=30N.m