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Reading material 3
Theories of strength
1.
Principal
stresses
The state of the
stress at a point in a structural member under a
complex system of loading
is
described
by
the
magnitude
and
direction
of
the
principal
stresses.
The
principal
stresses
are the maximum values of the normal
stresses at the point; which act on the planes on
which the
shear
stress
is
zero.
In
a
two-dimensional
stress
system,
Fig.1.11,
the
principal
stresses
at
any
poin
t are related to the
normal stress in the x and y directions
σ
x
and
σ
y
and the shear
stress τ
xy
at
the
point by the following equation:
?
1
?
1
1
2
(
?
y
?
?
x
)
2
?
4
?
xy
Principal stresses,
?
< br>?
(
?
y
?
?
x
)
?
?
2
?
p>
2
2
The maximum shear
stress at the point is equal to half the algebraic
difference between the
principal
stresses.
stresses:
Maximum
shear stress,
?
max
?
1
(
?
1<
/p>
?
?
2
)
2
Compressive
stresses are conventionally taken as negative;
tensile as positive.
2.
Classification
of pressure vessels
For
the
purpose
of
design
and
analysis,
pressure
vessels
are
sub-divided
into
two
classes
depending on the ratio of the wall
thickness to vessel
diameter
:
thin-wall vessels,
with a thickness
ratio of less than
1/10, and thick-walled above this ratio.
The principal stresses
acting at a point in the wall of a vessel, due to
a pressure load, are
shown in Fig.1.12.
If the wall is thin, the radial stress
σ
3
will be small
and can be neglected in
comparison with
the other stresses , and the longitudinal and
circumferential stresses
σ
1
and
σ
2
can
be taken as constant
over the wall thickness. In a thick wall, the
magnitude of the radial stress will
be
significant, and the circumferential stress will
vary across the wall. The majority of the vessels
used
in
the
chemical
and
allied
industries
are
classified
as
thin-walled
vessels.
Thick-walled
vessels are
used for high pressures.
3.
Allowable stress
In the
first two sections of this unit equations were
developed for finding the normal stress
and average shear stress in a
structural member. These equations can also be
used to select the size
of
a
member
if
the
member’s
strength
is
known.
The
strength
of
a
material
can
be
defined
in
several
ways,
depending
on
the
material
and
the
environment
in
which
it
is
to
be
used.
One
definition
is
the
ultimate
strength
or
stress.
Ultimate
strength
of
a
material
will
rupture
when
subjected to a purely axial load. This
property is determined from a tensile test of the
material.
This
is
a
laboratory
test
of
an
accurately
prepared
specimen,
which
usually
is
conducted
on
a
universal testing machine. The load is
applied slowly and is continuously monitored. The
ultimate
stress or strength is the
maximum load divided by the original cross-
sectional area. The ultimate
strength for most
engineering materials has been accurately
determined and is readily available
If
a
member
is
loaded
beyond
its
ultimate
strength
it
will
fail----
rupture.
In
the
most
engineering structures
it is desirable that the structure not fail. Thus
design is based on some lower
value
called
allowable stress
or
design stress. If, for example, a certain steel is
known to have an
ultimate strength of
110000 psi, a lower allowable stress would be used
for design, say 55000 psi.
this
allowable stress would allow only half the load
the ultimate strength would allow. The ratio of
the ultimate strength to the allowable
stress is known as the
factor of
safety
:
Factor
of
saf
ety
?
ultimate
strength
Su
or
n
?
allowable
stress
Sa
We use S for strength or
allowable and σ for the actual stress in material.
In a design:
This
so-called
factor
of
safety
covers
a
multitude
of
sins.
It
includes
such
factors
as
the
uncertainty of the load,
the uncertainty of the material properties and the
inaccuracy of the stress
analysis. It
could more accurately be called a factor of
ignorance! In general, the more accurate,
extensive, and expensive the analysis,
the lower the factor of safety necessary.
4.
Theories of
failure
The failure of a simple
structural element under unidirectional stress
(tensile or compressive)
is easy to
relate to the tensile strength of the material, as
determined in a standard tensile test, but
for
components
subjected
to
combined
stresses
(normal
and
shear
stress)
the
position
is
not
so
simple,
and
several
theories
of
failure
have
been
proposed.
The
three
theories
most
commonly
used are described
below:
Maximum principal stress theory:
which postulates that a member will fail when one
of the
principal
stresses
reaches
the
failure
value
in
simple
tension,
σ
’
e
.
The
failure
point
in
a
simple
tension
is
taken
as
the
yield-
point
stress,
or
the
tensile
strength
of
the
material
divided
by
a
suitable
factor of safety.
Maximum
shear
stress
theory:
which
postulates
that
failure
will
occur
in
a
complex
stress
system when the maximum shear stresses
reaches the value of the shear stress at failure
in simple
tension.
For a
system of combined stresses there are three shear
stresses maxima:
In the tensile test,
?
p>
e
?
?
e
'
2
The maximum shear stress will depend on
the sign of the principal stresses as well as
their
magnitude,
and
in
a
two-
dimensional
stress
system,
such
as
that
in
the
wall
of
a
thin-walled
pressure
vessel,
the
maximum
value
of
the
shear
stress
may
be
given
by
putting
σ
3
=0
in
equations 1.10.
T
he maximum shear stresses theory is
often called Tresca’s, or Guest’s
theory.
Maximum strain energy theory: which
postulates the failure will occur in a complex
stress
system when the total strain
energy per unit volume reaches the value at which
failure occurs in
simple tensile.
The maximum shear-stress theory has
been found to be suitable for predicting the
failure of
ductile material under
complex loading and is the criterion normally used
in the pressure-vessel
design.
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