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Purdue University
EAS 557
Introduction to Seismology
Robert L. Nowac
Lecture !
Analysis o" Stress
The concept of stress involves the action of forces on a body. Twotypes are considered:
1) Body forces – . Which are generally forces per unit volume. For
gravitational forces these depend on the mass distribution withinthe body. These are generally non!contact forces.
") #urface forces – . These are forces per unit area acting along
surfaces of elemental volumes and are contact forces with ad$acent parts of the body. These forces give rise to the concept of traction
on e%ternal and internal surfaces. The traction on an e%ternalsurface of the body is related to the applied force by
where is the average force on the small surface centered on
the point &. is called the traction vector.
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'nits of traction and stress are in force(area. n cgs the units of stress
are dyne(cm". n # the units of stress are 1 *ewton(m" + 1 &ascal ,1 &ascal +1- dyne(cm"). ther units are
1 bar + 1-/ dyne(cm" + 1-0 &ascals
1 bar + 1.-1 2tmospheres 1 3ilobar + 10--- lb(in"
We now want to investigate tractions on internal surfaces within a
body. 4onsider a bar under tension
The e%ternal applied force results in tractions on the ends.
*ow cut the bar and apply forces on the two sides of the cut so that the
shape of either section of bar remains unchanged. 56uilibrium re6uires
that .
*ow define the tractions on the upper and lower
faces of the cut. From *ewton7s Third 8aw . Thus onthe arbitrary internal surface that we have constructed.
n !9 consider a cut of area at a point &. 8et be the force
applied to the side with normal
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2gain . n the other side of the cut .
From *ewton7s Third 8aw
Thus as in the case for the bar the tractions on either side of the cut are of the
same magnitude but opposite in sign.
f we made cuts in other directions say with normals and we
would obtain different values for the internal traction at &. *ote that for a
fluid the pressure is related to the traction by for any . But in a
solid the magnitude and direction of the traction depends on the orientation of
the surface element .
5%) 4onsider the walls of a house.
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For an elemental area of the wall at point . But at point
& will be non!ero and large.
t at first seems that there will be an infinite number of traction vectorsat a given point depending on the orientation of the small surface. But
4auchy proved that in fact all the various tractions at & can be derived from aset of si% numbers collectively grouped as the ;stress tensor
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where and are unit vectors in the x1 and x" directions. The vectors are
oriented in the conventional positive directions. Thus would be positive if they stretch the material. 2lso on the opposite faces
n 9 we will write
in which is the stress tensor at the point & where
are tensional or compressive stresses
are shear stresses
n inde% notation the stress tensor is where i is normal to coordinate
plane in which the traction acts and j indicates the component of the tractionvector.
4auchy showed that the stresses on any plane through an internal point
& can be written as a linear combination of the elements of the stresstensor. This is a fundamental theorem of solid mechanics. 4onsider the
triangle in "9 ,tetrahedron in !9)
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The traction on surface with normal is
. *ow we must find the condition of e6uilibrium of the
triangle. Balancing forces in the x1 and x" directions gives
n the x1 direction:
n the x" direction:
or
From geometry
We then find
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n inde% notation for !9 then
,with implied sum on j)
Thus the 3nowledge of the stress tensor specifies completely the state ofstress around the point &.
n order to prevent the body from spinning we also re6uire that the nettor6ue be ero. 5valuating the tor6ue for a reference point at the center of thes6uare we get
where is a force and is a moment arm. Then .
n the general !9 case . Because of this relation the stress
tensor is symmetrical where
with and . Thus only si% numbers areneeded to completely describe the state of stress of an internal point & in a
body.
t is important to separate between the isotropic and deviatoric part ofthe stress tensor . We define
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where is independent of the coordinate system and & is the pressure. Theminus sign is used to re6uire & to be positive when it is compressive. The
stress elements themselves are positive in tension. We rewrite as
or in inde% notation
where is the deviatoric part of the stress tensor.
For hydrostatic stress . For a hydrostatic increase ofstress with depth due to a uniform overburden then
where is the density of the overburden z is thic3ness and g is the
acceleration of gravity. 2s an e%ample the hydrostatic pressure at a depth of1- 3m underneath a thic3ness of roc3 with an average density of ---
3ilograms(m is
& + ,--- 3ilograms(m) ,1- % 1- m) ,=.> m(s")
+ ".=? % 1-> &ascals @ "=? A&a
+ ".=? 3bars
2t an average thic3ness of the crust of - 3m the hydrostatic pressure would be on the order of 1 &a or 1- 3bars.
#rans"ormations o" t$e Stress #ensor in Rotated %oordinate Systems
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The components of a vector in a rotated coordinate system can berelated to the components in the original system by a coordinate rotation
matri% . For e%ample the components of the vector above in twocoordinate systems can be written
where the components of are the direction cosines between the old and newcoordinate a%es. The rotation matri% is
2s an e%ample if then
8et then in the new coordinate system.
*ote for rotation matrices since these are orthogonal
matrices. *ow assume a general relationship between two vectors and
n a rotated coordinate system
Then the general relationship between and can be written
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or
Thus in the new coordinate system where
with . This general relationship has the same form in any rotated
coordinate system with the coefficients depending on the orientation of thecoordinate system.
*ow consider the traction vector on an internal plane with normal
#ince this can also be written
or
n a rotated coordinate system the traction vector is
with
*ow we choose so that is a diagonal matri%. n this specialcoordinate system all the shear stresses are ero and the normal stresses are
called the &rinci&le stresses acting with respect to the three rotated coordinatea%es. 8et
where are the rotated a%es with respect to the unrotated
a%es. Then can be written as
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or for each then
forms an eigenvalue problem. To find the eigenvalues the determinant
of must be ero. Thus
to solve for . *e%t solve for the eigenvectors and ma3e sure to ad$ust
to unit length. #tandard computer software such as Aatlab can be used to
find the principle stresses and the principle stress directions ,i + 1).
These can be ordered such that . #ince these are positive
for tensional stresses provides the ma%imum compressive stress. Thereare no shear or tangential stresses act on these new coordinate faces only
normal stresses.
n the "!9 case it is useful to derive these relations in detail
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8et where
and . Then
This can be multiplied out and written in terms of components of as
f we let then we can find the rotation angle to be
#ince
f then will be the ma%imum and minimum normal
stress. Thus
These would then be the eigenvalues in the above eigenvector analysis in
"9. From we find that
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2s an e%ample of the calculation of the principle stresses in "9 let
then
This gives for the principle stresses
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Thus
Then
and
These must then be normalied to unit length to get and . 'sing the "!9
formulas
#tress maps showing the orientation of ma%imum horiontal shearstress have been developed based on orientations of earth6ua3e faulting and in
situ stress measurements. ne techni6ue for finding this is from brea3outones in boreholes which align with the principle stress directions and are
often consistent over regional distances. A solid body is in static equilibrium when the resultant force and moment on each axis
is equal to zero. This can be expressed by the equilibrium equations. In this article we
will prove the equilibrium equations by calculating the resultant force and moment on
each axis. A more elegant solution may be derived by using Gauss’s theorem and
auchy’s formula. This approach may be found in international bibliography.
onsider a solid body in static equilibrium that neither moves nor rotates. !urface and
body forces act on this body. "e cut an infinitesimal parallelepiped inside the body andwe analyze the forces that act on it as shown in #ig. $. "e will assume that the stress
field is continuous and differentiable inside the whole body.
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Figure 1: Infinitesimal parallelepiped in static equilibrium
The stress components on each side is a function of the position since we have a non
uniform but continuous stress field. #or example on side % the normal stress
is . &n the opposite side ' the normal stress
is . (y ta)ing under consideration Taylor’s theorem we may write*
+$,
The higher order terms have been neglected because they are relatively small. "e
follow the same procedure for all the components as shown if #ig. $.
-quilibrium of the body demand that the resultant forces must vanish. (y summing up
the forces with direction parallel to axis we get*
+',
where and are the dimensions of the parallelepiped and is the
component of the body force parallel to . (y dividing with we get*
+/,
!imilarly we can obtain the equations for the other two directions. The final set of
equilibrium equations is*
+%,
(y using index notation we may write the three equilibrium equations in compact form*
+0,
The resultant moment on each axis must also vanish. (y ta)ing under consideration all
the forces that contribute to moment about axis we may write*
http://www.rockmechs.com/stress-strain/fundamentals/index-notation-tensor-vector/http://www.rockmechs.com/stress-strain/fundamentals/index-notation-tensor-vector/
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+1,
by dividing with and ta)ing the limit and we
derive*
+2,
#ollowing the same procedure for the other two axes lead to the conclusion that the
stress tensor is symmetric*
+3,
It should be noted that the above symmetry holds true only if no external body
moments proportional to volume exist. -lse the stress tensor should be considered
asymmetric. 4owever for the ma5ority of 6oc) 7echanics problems the stress tensor is
symmetric.
#or the case of two dimensional problems equilibrium equations simplify as follows*
+8,
Example
onsider a solid body which is sub5ect to the following stresses*
+$9,
alculate the body forces in order to achieve static equilibrium.
!olution
The resultant force on each axis must vanish. (y using equations +%, we get*
+$$,
+$',
+$/,
Suggested Bibliography
:.. #ung. A #irst ourse in ontinuum 7echanics. ;rentice 4all -nglewood liffs
.-. 7alvern. Introduction to the 7echanics of a ontinuous 7edium. ;rentice 4all
-nglewood liffs