International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Experimental study of effect of viscosity of various oil in roller bearing
Praveen Sharma*1, Prof. A.K. Jain2
*1
ME IVth sem student, Jabalpur Engg. College Jabalpur (M P)
2
Associate professor, Jabalpur Engg. College Jabalpur (M P)
Abstract:
This work aims to characterize
vibration behavior of roller bearings as a
function of lubricant viscosity. Experimental
tests were performed in N205 roller
bearings, lubricated with mineral oil of
three different viscosity grades (ISO 10, 32
and 68). The mechanical vibration was
determined through the processing and
analysis of bearing radial vibration data,
obtained from each of the lubrication
conditions, during 2 h of test run for
temperature stabilization and under several
bearing shaft speeds. The applied radial
load was 12% of the bearing nominal load.
Through root mean square (RMS) analysis
of the vibration signals, it was possible to
identify specific frequency bands modulated
by the change in lubricant viscosity, which
was related to change in oil film thickness.
or to the directions of the loads (forces)
applied to the parts.
The term "bearing" is derived from
the verb "to bear"; a bearing being a
machine element that allows one part to bear
(i.e., to support) another. The simplest
bearings are bearing surfaces, cut or formed
into a part, with varying degrees of control
over the form, size, roughness and location
of the surface. Other bearings are separate
devices installed into a machine or machine
part.
2. Methodology
The tested rolling bearings were of N205
type, presenting the geometry shown in Fig.
.
Key Word- Roller bearing, Vibration,
Viscosity, Applied load
1 -Introduction- A bearing is a machine
element that constrains relative motion
between moving parts to only the desired
motion. The design of the bearing may, for
example, provide for free linear movement
of the moving part or for free rotation
around a fixed axis; or, it may prevent a
motion by controlling the vectors of normal
forces that bear on the moving parts.
Bearings are classified broadly according to
the type of operation, the motions allowed,
ISSN: 2231-5381
Figure 2.1-Roller bearing
Mineral oil without additive was used as
lubricant. Three different viscosity grades
were tested, ISO 10 (V1), ISO 32 (V2) and
ISO 68 (V3), with the purpose of obtaining
the vibration response related to different
lubrication regimes in the bearing element
contacts.
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Figure 2.2-Roller bearing with rotating
shaft
A system with pulleys transmits the power
from an electric motor to the bearing shaft.
Two ball bearings are used to support the
shaft. A frequency inverter controls the shaft
speed. Actually, machines have an inherent
vibration that characterizes the baseline of
their dynamical behavior. The baseline
dynamics certainly affects the vibration of
any monitored component.
observed during the first hour of test and a
trend of stabilization in the second hour.
This behavior is repetitive for the three
tested viscosity grades.
According to technical publications of
rolling bearings manufacturers , both
increase and stabilization of temperature
occur with any type of rolling bearing, and
the stabilization is due to equilibrium
between production and dissipation of heat
in the system. Also, it can be observed that,
for the studied viscosity grades, oil
temperature is proportional to the viscosity
degree.
This phenomenon is correlated with the
friction force that originated from viscous
action among the layers in the lubricant film
that separates the surfaces in contact. High
friction force (high viscosity) is related to
high loss of energy in the contact, resulting
in high heat generation .
V1=ISO10,V1=ISO32,V1=ISO68
Temperature is obtain by digital temperature
meter
Table 3.1-Oil temperatures
Sr.NO.
Figure 2.3- RPM is obtain from rpm
measurement device
1
2
3
4
5
6
7
8
9
Test
time in
minute
0
15
30
45
60
75
90
105
120
Oil
Temp.
of V1
22.2
24.2
29.2
33.8
37.8
40.2
44.2
44.2
44.2
Oil
Temp.
of V2
24.2
28.2
33.4
36.5
39.2
43.4
46.2
46.2
46.2
Oil
Temp.
of V3
28.2
32.2
36.2
38.2
42.4
45.3
48.2
48.3
48.3
3. Results and discussion
3.1.-Oil temperature
Oil bath temperature as a function of test
time, for the three tested viscosities. A
gradual increase in temperature can be
ISSN: 2231-5381
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Figure 3.1-Graph between two parameters
using V1
Figure 3.2-Graph between two parameters
using V2
Figure 3.4-Graph between two parameters
using V1, V2 and V3
3.2-Bearing vibration
Fig. shows the RMS vibration values of the
rolling bearing as a function of test time.
Comparing the results in this figure with
those in Fig., two main observations can be
done. First, it is observed that both
temperature and RMS values tend to
increase and stabilize with test time.
Secondly, vibration level is smaller as oil
viscosity degree becomes higher, in contrast
to the effect of temperature on oil viscosity.
An explanation for this fact is discussed in
the next sections, in terms of the tribological
condition of the contacts.
3.2.1- Using of V1
W=700N in mid way
Diameter of shaft d=25.4mm
Eccentricity of C.G.outer surface of
bearing ,e=0.02mm
Power consumption=One HP
Length of shaft L=400mm
E=1.96Χ1011 N/m2
Figure 3.3-Graph between two parameters
using V3
ISSN: 2231-5381
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Deflection,
δ=WL3/48EI=700Χ0.43Χ64/48Χ(1.9
6Χ1011)π(0.0254)4
r=
=
=0.813752
=
=
-4
=7.32Χ10
Amplitude
of
s=0.03920mm
Stiffness of shaft,
k=
of
transvers
r=
radian/s
3.2.1.1-RPM of shaft N=870 , Obtain from
rpm measurement device
r=
=
Test time in minute= 15 minutes
=
=0.84087
=
=
Amplitude of vibration , s=0.0482
mm
ω=91.06 radian/s
3.2.1.4-RPM of shaft N=965 , Obtain from
rpm measurement device
r=
Test time in minute= 60 minutes
=0.78662
ω=
=
=
ω=97.34 radian/s
=115.76
r=
Test time in minute= 45 minutes
ω=
ωn
ω=
,
3.2.1.3-RPM of shaft N=930 , Obtain from
rpm measurement device
=956031 N/m
Natural frequency
vibration
vibration
=
=
=
ω=101.003 radian/s
Amplitude
s=0.0324mm
of
vibration
,
3.2.1.2-RPM of shaft N=900 , Obtain from
rpm measurement device
Test time in minute= 30 minutes
ω=
=
ω=94.2 radian/s
r=
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r=
r=
=
=0.87252
=
Amplitude
of
s=0.06378mm
=
vibration
,
3.2.1.5-RPM of shaft N=988, Obtain from
rpm measurement device
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Test time in minute= 75 minutes
ω=
=
=
=
Amplitude
s=0.0946mm
ω=103.410 radian/s
of
vibration
,
3.2.1.8-RPM of shaft N=1005 , Obtain
from rpm measurement device
r=
r=
Test time in minute= 120 minutes
=0.8933
ω=
=
=
=
=
=
ω=105.19 radian/s
Amplitude of vibration,
s=0.07900mm
r=
3.2.1.6-RPM of shaft N=1002 , Obtain
from rpm measurement device
Test time in minute= 90 minutes
ω=
r=
=
=
=0.9086
=
=
Amplitude
s=0.0946mm
ω=104.876 radian/s
r=
of
vibration
,
3.2.2- Using of V2
r=
W=700N in mid way
=0.9059
Diameter of shaft d=25.4mm
=
=
Amplitude
s=0.0914mm
=
of
vibration
,
Eccentricity of C.G.outer surface of
bearing ,e=0.02mm
Power consumption=One HP
3.2.1.7-RPM of shaft N=1005, Obtain
from rpm measurement device
Length of shaft L=400mm
E=1.96Χ1011 N/m2
Test time in minute= 105 minutes
ω=
Deflection,
δ=WL3/48EI=700Χ0.43Χ64/48Χ(1.9
6Χ1011)π(0.0254)4
=
ω=105.19 radian/s
r=
r=
=7.32Χ10-4
Stiffness of shaft,
=0.9086
ISSN: 2231-5381
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
k=
Amplitude
s=0.0147mm
=956031 N/m
Natural frequency
vibration
of
transvers
of
vibration
,
3.2.2.3-RPM of shaft N=752 , Obtain from
rpm measurement device
Test time in minute= 45 minutes
ω=
ωn
=115.76
ω=78.70 radian/s
radian/s
3.2.2.1-RPM of shaft N=695 , Obtain from
rpm measurement device
=
=
ω=72.74 radian/s
=
of
vibration
ω=81.74 radian/s
r=
Test time in minute= 30minutes
r=
=
=
Amplitude
s=0.0198mm
=
of
vibration
,
3.2.2.5-RPM of shaft N=810, Obtain from
rpm measurement device
r=
=
=0.7061
=
ω=75.46 radian/s
r=
=
,
3.2.2.2-RPM of shaft N=721 , Obtain from
rpm measurement device
ω=
=
Test time in minute= 60 minutes
=
ω=
Amplitude
s=0.0130mm
=
3.2.2.4-RPM of shaft N=781 , Obtain from
rpm measurement device
=0.6283
=
=0.6799
Amplitude of vibration , s=0.0171
mm
r=
r=
r=
r=
Test time in minute= 15 minutes
ω=
=
=0.6519
=
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Test time in minute= 75 minutes
=
ω=
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=
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
ω=84.78radian/s
Amplitude of vibration ,
s=0.00288mm
r=
r=
=
3.2.2.8-RPM of shaft N=850 , Obtain from
rpm measurement device
=0.732
=
Test time in minute= 120minutes
=
Amplitude of vibration , s=0.0230
mm
3.2.2.6-RPM of shaft N=836 , Obtain from
rpm measurement device
Test time in minute= 90 minutes
ω=
ω=
=
ω=88.966 radian/s
r=
r=
=0.7685
=
=
=
=
ω=87.50 radian/s
Amplitude
of
s=0.00288mm
r=
r=
vibration
,
3.2.3- Using of V3
=0.7558
W=700N in mid way
=
=
=
Diameter of shaft d=25.4mm
Amplitude of vibration ,
s=0.0266mm
3.2.2.7-RPM of shaft N=850, Obtain from
rpm measurement device
Eccentricity of C.G.outer surface of
bearing ,e=0.02mm
Power consumption=One HP
Length of shaft L=400mm
Test time in minute= 105 minutes
ω=
=
E=1.96Χ1011 N/m2
Deflection,
δ=WL3/48EI=700Χ0.43Χ64/48Χ(1.9
6Χ1011)π(0.0254)4
ω=88.966 radian/s
r=
r=
=
=7.32Χ10-4
Stiffness of shaft,
=0.7685
=
ISSN: 2231-5381
=
k=
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=956031 N/m
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Natural frequency
vibration
of
transvers
3.2.3.3-RPM of shaft N=582 , Obtain from
rpm measurement device
Test time in minute= 45minutes
ωn
ω=
=115.76
radian/s
ω=60.916 radian/s
3.2.3.1-RPM of shaft N=515 , Obtain from
rpm measurement device
Test time in minute= 15 minutes
ω=
r=
=0.5262
=
=
Amplitude of vibration , s=0.0076
mm
r=
=
r=
=
=
ω=53.90 radian/s
r=
=
3.2.3.4-RPM of shaft N=610 , Obtain from
rpm measurement device
=0.465
=
Test time in minute= 60 minutes
ω=
=
Amplitude of vibration ,
s=0.005524mm
=
ω=63.84 radian/s
r=
3.2.3.2-RPM of shaft N=545 , Obtain from
rpm measurement device
r=
=0.551
Test time in minute= 30 minutes
ω=
=
=
Amplitude
of
s=0.00872mm
ω=57.04 radian/s
r=
r=
=
=
=
vibration
,
3.2.3.5-RPM of shaft N=638, Obtain from
rpm measurement device
=0.492
=
Test time in minute= 75 minutes
ω=
=
Amplitude of vibration ,
s=0.00640mm
=
ω=66.77radian/s
r=
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
r=
=
3.2.3.8-RPM of shaft N=670 , Obtain from
rpm measurement device
=0.576
=
=
Test time in minute= 120 minutes
ω=
Amplitude of vibration , s=0.00995
mm
ω=70.12radian/s
3.2.3.6-RPM of shaft N=650 , Obtain from
rpm measurement device
r=
Test time in minute= 90 minutes
ω=
r=
=
=
=
vibration
Table 3.2 Amplitude of vibration,
(in mm)
,
3.2.3.7-RPM of shaft N=670, Obtain from
rpm measurement device
Sr.N
O.
Test
time
in
min
ute
1
2
3
4
5
6
7
8
15
30
45
60
75
90
105
120
Test time in minute= 105 minutes
=
ω=70.12radian/s
r=
r=
=
=
=0.5877
Amplitude
of
s=0.01055mm
ω=
=
Amplitude of vibration ,
s=0.0115mm
r=
=
=0.605
=
ω=68.03 radian/s
r=
=
=0.605
=
Amplitude
s=0.0115mm
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=
of
vibration
,
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Amplit
ude of
vibrati
on
,
(in
mm)
when
use in
V1
0.0324
0.0392
0.0482
0.0637
0.0790
0.0914
0.0946
0.0946
Amplitu
de
of
vibratio
n,(in
mm)
when
use
in
V2
Amplit
ude of
vibrati
on ,(in
mm)
when
use in
V3
0.0130
0.0147
0.0171
0.0198
0.0230
0.0266
0.0288
0.0288
0.0055
0.0064
0.0076
0.0087
0.0099
0.0105
0.0115
0.0115
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
Figure 3.5-Graph between two parameters
using V1
Figure 3.6-Graph between two parameters
using V2
Figure 3.7-Graph between two parameters
using V3
ISSN: 2231-5381
Figure 3.8-Graph between two parameters
using V1,V2 and V3
4-Conclusions:
Roller bearings were tested in order to verify
differences in vibration response when
lubricated with different viscosity oils. The
vibration behavior was studied in two main
frequency bands and by using a tribological
parameter (l factor). The main conclusions
are: Changes in lubrication regime of roller
bearings due to change in oil viscosity grade
could be detected by vibration monitoring.
In the tests with ISO 32 and ISO 68
viscosity grades, lubrication regime was of
full film type. With the ISO 10 grade,
lubrication regime was supposed to be very
near to that of mixed type. Two main
observations can be done. First, it is
observed that both temperature and RMS
values tend to increase and stabilize with
test time. Secondly, vibration level is
smaller as oil viscosity degree becomes
higher, in contrast to the effect of
temperature on oil viscosity.
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International Journal of Engineering Trends and Technology (IJETT) – Volume 4 Issue 8- August 2013
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