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Tribology Lecture IIElastohydrodynamic
Lubrication
Hydrodynamic Lubrication
Fluid Layer p
Pressure required to support the load is generated by motion and geometry of the
bearing in concert with the viscosity of the lubricant
w
Hydrodynamic Lubrication
Fluid Layer p
Pressure is generated by motion and geometry of the bearing in concert with the viscosity of the lubricant
w
Hydrodynamic LubricationPoint Contact
hc
R
288 2
25
UR
2W
2
Fluid Layer hc
U
R
Sphere
w
Hydrodynamic Lubrication(Refinement: Both surfaces moving)
hc
R
288 2
25
U R
W
2
Fluid Layer hc
U2
R
Sphere
U1
U 1
2U1 U2
“Entrainment”or
“Rolling Velocity” 2
0 21
UUU
w
Hydrodynamic Lubrication(Refinement: two spheres)
hc
R
288 2
25
U R
W
2
hc
R1
U1
1
R
1
R1
1
R2
Where R is now “reduced” radius
12 RRR
R2
U2
w
Hydrodynamic Lubrication
hc
R
288 2
25
U R
W
2
hc
R
288 2
25
U R
W
2
hc
R1
U1
R2
U2
Nice theory but as a rule itgreatly under estimates hc
•Pressure is very high near contact
P >>1000atm ( 108 Pa)•Pressure Dependence of •Elastic Deformation of Sphere
Nice theory but as a rule itgreatly under estimates hc
•Pressure is very high near contact
P >>1000atm ( 108 Pa)•Pressure Dependence of •Elastic Deformation of Sphere
w
Pressure and Temperature Dependence of Viscosity
Viscosity increases exponentially with pressure:
Barus Equation:
0eP
pressure viscosity coefficient
0 (cp)
SAE 10 266 2.51x10-8
SAE 30 105 3.19x10-8
larger larger hc for a given load
Large stresses lead to elastic deformation
R1
R2
Conformal Contact
Contact Circle (radius a)Contact Point
Point Contact
R1
R2
ww
Large stresses lead to elastic deformation
R1
R2
R1
R2
Conformal Contact
Contact Circle (radius a)Contact Point
Point Contact
w w
R1
R2
Elastic Deformation of Sphere
a3 3WR
4E*
2aR is the reduced radiusE* contact modulus
1
E* 1 1
2
E1
1 2
2
E2
w
E1
E2 E2
E1
E2
1
E* 1 1
2
E1
1 2
2
E2
E2>>E1
E* E1
1 12
E1>>E2
E* E2
1 22
E1
•Either way contact becomes conformal
Because of rise in viscosity with pressure deformation is about the same with the lubricating fluid present
E1
E2
hc
E2
E1E1
hc
•Surfaces are parallel at contact - i.e. “conformal”•Lower E* ( larger a for same load ) larger hc
E1
E2
hc
U2
U1
Elastohydrodynamic Lubrication (EHD L)
To variables for hydrodynamic lubrication
R, W , 0, U
add , E*
•How does hc depend on these parameters?
w
Hamrock & Dowson Equation
hc
RK E*
a 0U
E*R
b
W
E*R2
c
hc
RK E*
a 0U
E*R
b
W
E*R2
c
material speed load
Elastohydrodynamic Lubrication (EHD L)Dimensional Analysis
02
0.67 .0670.53*1.9 2* *2 2
ch U WE
R E R E R
0
2
0.67 .0670.53*1.9 2* *2 2
ch U WE
R E R E R
•Dependence on load is very weak 2.067=1.048
Hamrock & Dowson Equation (clarification from lab manual)
H* hP /R 1.90 U * 0.67W * 0.067
G * 0.53
where
U* uOIL
E R, W *
WE R2 , G* E , R Rb
u = rolling velocityOIL= zero pressure oil viscosity, = oil viscosity at higher pressure = pressure-viscosity index from the equation, = OILexp( P)
1E
1
2
1 d2
Ed
1 b
2
Eb
Note factor of 2
*2E E
Tribology Lab
•Measure hc as a function of U and W•Compare result with Hamrock Dowsen equation
Tribology Lab• Objectives: Characterize elastohydrodynamic (EHD) lubrication using an optical
technique. The study involves:– Measurement of the lubricating film thickness as a function of:
• rolling velocity• normal load
– Comparison of the measured film thickness with a theoretical film thickness (from the Hamrock & Dawson equation)
• Experimental Setup:
ME 4053
Nd Glass plate (connected to motor)
Steel ball
LightSource
MonitorCamera
LoadingMechanism
Light Source:
Contact Area
FiberopticCable
Camera
aperture
condenser
Semi-reflectiveSurface
Experimental Setup (cont’d)
rc
Nd
top view: side view:
W(load)
Fringe pattern
Camera
LightBeam
h
oilfilm
glassdisc u
Nd: rpm; u: rolling velocity; h: film thickness
Rolling velocity:60
2 dc Nru
Measured oil film thickness: )(2
N
nh , where:
: wavelength of light in air (600nm) N: fringe order
n: refractive index of oil (1.5) : phase shift constant (0.1)
fringes)(dark 0.5,1.5,
)fringesbright(,3,2,1
Experimental Procedure: obtain the following table for W=16N & W=30N
Fringe N Nd (rpm) Nd (rpm) u (m/s) h (nm) ht (nm)fringe order trial 1 trial2 velocity experimental theoretical
Dark 0.5 2 2 80Bright 1 180Dark 1.5 280Bright 2 380Dark 2.5 480Bright 3 580Dark 3.5 680Bright 4 780
measured computed from Nd, N computed fromHD equation
Theoretical Thickness, ht: The Hamrock & Dowson Equation
])()()(9.1[ 53.0*067.0*67.0* GWURht
R: ball radius W*: dimensionless load parameterU*: dimensionless speed parameter G*: dimensionless material parameter
-12.5
-12.0
-11.5
-11.0
-10.5
-10.0
-9.5
-27.0 -26.5 -26.0 -25.5 -25.0 -24.5 -24.0 -23.5 -23.0 -22.5
ln(U*)
ln(h
/R)
data model upper lim lower lim prediction
Results Presentation:
*Practical note on load adjustment:
Load = 2 x (spring value - tare value)
Ex: to get W=16N, set spring value to 11.2N16 = 2 x (11.2 - 3.2)
(tare = 3.2N)
Theoretical/Experimental Comparison:
ln(h
/R)
ln(U*)