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Hydrodynamic BearingsHydrodynamic Bearings --TheoryTheory
Lecture 25Lecture 25
Engineering 473Engineering 473
Machine DesignMachine Design
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Lubrication ZonesLubrication ZonesBoundary
LubricationMixed-film
Lubrication
Hydrodynamic
Lubrication
CoefficientofFric
tion
Bearing Parameter
psiarea),jected(force/propressurep
rev/secspeed,rotationaln
sec/in-lb,viscositydynamic
p
n
ParameterBearing
2
Contact between
journal and bearing
Boundary LubricationBoundary Lubrication
MixedMixed--film Lubricationfilm Lubrication
Intermittent contact
Hydrodynamic LubricationHydrodynamic Lubrication
Journal rides on a fluid
film. Film is created by the
motion of the journal.
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Stable/Unstable LubricationStable/Unstable Lubrication
Boundary
LubricationMixed-film
Lubrication
Hydrodynamic
Lubrication
Coef
ficientofFrictio
n
Bearing Parameter
p
n
Hydrodynamic Lubrication
is often referred to as stable
lubrication.
If the lubrication temperature
increases, the viscosity
drops. This results in alower coefficient of friction,
that causes the lubrication
temperature to drop. => Self
Correcting.
Mixed-film lubrication is unstable an increase in lubrication
temperature causes further increases in lubrication temperature.
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Newtonian FluidNewtonian FluidA Newtonian fluid is any fluid whose shear stress and
transverse rate of deformation are related through the
equation.
dy
du =
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Dynamic ViscosityDynamic Viscosity
dy
du =
reyn
in
seclb
insec
inin
lb
2
f2
f
=
=
UnitsUnits
ipsips SISI
2
2
m
secN
msec
mm
N
=
Other common units are discussed in the text.
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Pumping ActionPumping ActionWhen dry, friction will cause the
journal to try to climb bearing
inner wall.
When lubricant is introduced, theclimbing action and the viscosity of
the fluid will cause lubricant to be
drawn around the journal creating a
film between the journal and bearing.The lubricant pressure will push the
journal to the side.
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Analysis AssumptionsAnalysis Assumptions
1. Lubricant is a Newtonian fluid
2. Inertia forces of the lubricant arenegligible
3. Incompressible
4. Constant viscosity
5. Zero pressure gradient along thelength of the bearing
6. The radius of the journal is large
compared to the film thickness
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Analysis GeometryAnalysis Geometry
Actual GeometryActual Geometry Unrolled GeometryUnrolled Geometry
From boundary layer theory, the pressure
gradient in the y direction is constant.
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XX--Momentum EquationMomentum Equation
pdydzdxdzdy
y
dxdzdydzdx
dx
dpp0Fx
++
+==
y
dx
dp
=
y
u
=
2
2
y
u
dx
dp
=
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XX--Momentum EquationMomentum Equation(Continued)(Continued)
( ) ( )xCyxCydx
dp
2
1u 21
2 ++=
0u0,y == ( ) 0xC2 =
-Uuh(x),y == ( )( )
( )dx
dp
2
xh
xh
UxC1 =
( )( )( )
yxh
Uyxhy
dx
dp
2
1u 2 =
Note that h(x) and
dp/dx are not known
at this point.
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Mass Flow RateMass Flow Rate
( )
( )( )( )
( )
( ) ( )
=
=
=
2
xUh
dx
dp
12
xh
m
dyyxh
Uyxhydxdp
21m
udym
3
xh
0
2
xh
0
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Conservation of MassConservation of Mass
Conservation of Mass RequiresConservation of Mass Requires
0dxmd =
( ) ( )
=
2
xUh
dx
dp
12
xhm
3
( ) 0dxdh
2U
dxdp
12xh
dxd
3
=
( )dx
dhU6
dx
dp
xh
dx
d3
=
ReynoldsReynolds EquationEquation
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h(x) Relationshiph(x) Relationship
e
( ) ( )
( )
( )
( )
+=
+=
=
+=
=
D
2xcos1cxh
1ch
1ch
cos1ch
ce
r
rmax
rmin
r
r
cr= radial clearance
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SommerfeldSommerfeld SolutionSolution
( )
dx
dh
U6dx
dp
xh
dx
d3
=
( )
+= D
2x
cos1cxh r
A. Sommerfeld solved these
equations in 1904 to find the
pressure distribution around thebearing.
It is known as a long bearing
solution because there is no flowin the axial direction.
( )( )( ) o222rp
cos12cos2sin6
cUrp +
+++=
r is the journal radius, is a chosen design parameter.
0
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OcvirkOcvirk ShortShort--Bearing SolutionBearing SolutionA short bearing allows lubricant flow in the longitudinal
direction, z, as well as in the circumferential direction, x.
( ) ( )x
h6U
dz
dp
xh
zdx
dp
xh
x
33
=
( )32
2
2
r cos1
sin3z
4
l
rc
Up
+
= 0
The Ocvirk solution (1955) neglects the first term
as being small compared to the axial flow.
GoverningGoverning
EquationEquation
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Short & Long BearingShort & Long Bearing
ComparisonsComparisons
%
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AssignmentAssignmentUse Matlab to plot the pressure distribution predicted by the
Sommerfeld equation for a journal bearing having a
clearance ratio of 0.0017, journal radius of 0.75 in, of 0.6,=2.2reyn, shaft rotational speed=20 rev/sec, and po=o.
First, generate the plot only for the range equals 0 to .
Second, generate the plot for the range equals 0 to 2.What happens to the pressure distribution from to 2. Is
this physically possible? Discuss what would happen to thelubricant if this pressure distribution occurred.