Chapter 7 Rolling Contact Bearing-2
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Transcript of Chapter 7 Rolling Contact Bearing-2
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7.2 Loading and Failure Styles
(1) Axial load Fa
Well-distributed on all rolling
elements (such as ball, or roller).
(2) Radial load FrNo load on the upper semi,
uneven distributed load on the
lower semi.
F05Fr/Zif Point contact
F04.6Fr/Zif Line contact
ZNumber of rolling elements
1. Load distribution of rolling contact bearing
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Generally, the acting point of the radial load Frcan be
regarded as the middle point of width of bearing. =0
But for the angular contact ball bearing, and tapered roller
bearing, this rule is not valid. 0
If the span of the shaft is very small, the modeling error
could be significant.(2) Calculation of axial load
For the deep groove ball bearing
If the resultant force on the shaft is FA,
Fa=FA(the axial load of bearing withstanding FA);Fa=0 (the axial load of bearing not withstanding FA).
(1) Briefness of radial load
2. Load calculation of rolling contact bearing
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FS1.25Frtan
Type of
bearing
Angular contact ball bearing Tapered rollerbearing
70000C(=15) 70000AC(=25) 70000B(=40) 30000
Fs eFr 0.68Fr 1.14Fr Fr/(2Y)
The factor ecan be found in a bearing dictionary.
The factor Yis the factor of axial dynamic load. See Table 7-7.
Table 7-5 Formulas of calculating the additional axial load
But for the angular contact bearing, the radial load will
generate additional axial load Fs.
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The additional axial load path is from the outer race, to the balls,
to the inner race and shaft.
So we need to use the angular contact ball bearing in pair.
Face to face
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Before calculating the axial load Fa1and Fa2, we need to consider
Fs1, Fs2and working axial load FA. There are two cases:
Fa2=Fs1+FA
And the left bearing is relaxed,
where it is only applied by
additional axial force. So, we
have Fa1=Fs1
(1) If Fs1+FA>Fs2,
The shaft has an inclination of moving rightwards. We assume
the right bearing is already fixed, so the shaft can not move. The
right bearing has been pressed. Based on the force equilibrium,
we have
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(2) If Fs1+FA
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The main failure types of rolling contact bearing include:Fatigue pitting on the surfaces of raceway and rolling element;
Plastic deformation of bearing;
Abrasive wear.
(1) Fatigue pitting
The surfaces of race and rolling element are applied by
fluctuating load.
After a large number of cycles of loading, fatigue pitting may
occur.
If fatigue pitting happens, the vibration, noise and heat loss will
increase very significantly.
3. Failure types and calculation principles
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(2) Plastic deformation
Overloaded static force or impact will cause plastic
deformation. The failure is sometimes referred to as brinelling.
If plastic deformation happens, the starting torque, vibrationand noise will increase very rapidly, and the positioning
precision of bearing will decrease.
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(3) Abrasive wear
Poor sealing and lubrication may cause abrasive wear, which
may produce noise and vibration.
The positioning error of bearing will decreases.
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(4) Calculation principles
1) Common situation -- Fatigue life (pitting)
2) Low speed situation -- Checking the static strength
3) High speed -- Calculating the fatigue life, and checking the
limiting speed
(5) Performance parameters of bearing
1) Basic static load rating C0(C0r, C0a)
The load that bearing can withstand without permanent
deformation of any component.
2) Basic dynamic rating C (Cr
, Ca
)
The load to which the bearings can be subjected while achieving a
rated life (L 10) of 106revolutions.
3) Limiting speed (nlim)
For an instance, 6317, nlim
=5000r/min.
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7.3 Strength Features and Life Design
Fatigue pitting is a statistical phenomenon with considerable
spread of the actual life of a group of bearings of a given design.
The rated life is the standard means of reporting the results of
many tests of bearings of a given design.
It represents the life that 90%of the bearings would achieve
successfully at a rated load.
It also represents the life that 10% of the bearings would not
achieve.
The rated life is thus typically referred to as the L 10life at the
rated load.
If load increase, the life of bearings decreases. See Fig. 7-10.
Basic dynamic load rating C: The constant load that bearings
can endure under the 106revolutions.
1. Life of bearings
2. Basic dynamic load rating
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The basic dynamic load rating indicates the performance ofresisting fatigue pitting.
By experimentswe have10 constantP L C
Ball bearing 3
10Roller bearing
3Equivalent dynamic load, P
For the radial bearings, it refers to the radial basic load rating Cr;
For the thrust bearings, it refers to the axial basic load rating Ca;
Cr, and Cacan be found in a bearing dictionary.
Basic dynamic load rating
Fig. 7-10 Life and equivalent dynamic load of rolling bearings
3. Life calculation of bearing
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10P L C
If the equivalent dynamic load of bearings is given
we can have the rated life of bearings, L 10. That is
6
10 10C
L revP
6
1010
10 16670
60 60h
L C CL h
n P n n P
If the rotational speed of bearings is given
we can have the rated life of bearings, L 10h. That is
If the equivalent dynamic load Pand the design life L his given
we can calculated the allowable dynamic load rating C. That is
16670
hL n
C P
we can specify the number of bearing based on C.
C C.
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Table 7-6 Recommended design life of bearings
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Basic dynamic load rating Cincludes radial basic dynamic
load rating Crand axial basic dynamic load rating Ca.
If the radial load Frand axial load Faare applied on therolling bearings, they have to be transferred into equivalent
dynamic load P.
Equivalent dynamic loadP
can be calculated by
( )d r aP f XF YF
X
Factor of radial dynamic load, see Table 7-7;YFactor of axial dynamic load, see Table 7-7;
fdFactor of impact load, including the vibration and shock,
see Table 7-8.
4. Equivalent dynamic load
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Table 7-7 Xand Yfor calculating the equivalent dynamic load
of rolling contact bearing
TypesFa/C0r
e
Single row bearing Double row bearing
Fa
/Fr
e Fa
/Fr
>e Fa
/Fr
e Fa
/Fr
>e
X Y X Y X Y X Y
Deepgroove
ball
bearing
60000
0.014 0.19
1 0 0.56
2.30
1 0 0.56
2.30
0.028 0.22 1.99 1.99
0.056 0.26 1.71 1.71
0.085 0.28 1.55 1.55
0.11 0.30 1.45 1.45
0.17 0.34 1.31 1.31
0.28 0.38 1.15 1.15
0.42 0.42 1.04 1.04
0.56 0.44 1.00 1.00
In the relative axial load Fa/Cor, Coris the radial static load rating,
which can be found in a bearing dictionary; If the value of Fa/Coris an
arbitrary value, an linear interpolation is needed.
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TypesFa/C0r
e
Single row bearing Double row bearing
Fa/Fre Fa/Fr>e Fa/Fre Fa/Fr>e
X Y X Y X Y X Y
Angular contact
ball bearing
=15
70000
0.015 0.38
1 0 0.44
1.47
1
1.65
0.72
2.39
0.029 0.40 1.40 1.57 2.28
0.058 0.43 1.30 1.46 2.11
0.087 0.46 1.23 1.38 2.00
0.12 0.47 1.19 1.34 1.93
0.17 0.50 1.12 1.26 1.82
0.29 0.55 1.02 1.14 1.66
0.44 0.56 1.00 1.12 1.63
0.58 0.56 1.00 1.12 1.63
=25
, 70000 -- 0.68 1 0 0.41 0.87 1 0.92 0.67 1.41
=45 -- 1.14 1 0 0.36 0.57 1 0.55 0.67 0.93
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TypesFa/C0r
e
Single row bearing Double row bearing
Fa/Fre Fa/Fr>e Fa/Fre Fa/Fr>e
X Y X Y X Y X Y
Double row
angular contact
ball bearing
=30
- 0.80 -- -- -- -- 1 0.78 0.63 1.24
4-point contact
bearing =30
-- 0.95 1 0.66 0.60 1.07 -- -- -- --
Tapered roller
bearing 3000--
1.5 tan
1 0 0.40
0.4cot
1
0.45
cot 0.67
0.67
cot
Self-aligning
bearing-- 1.5 tan -- -- -- -- 1
0.42
cot 0.65
0.65
cot
Thrust selfaligning roller
bearing
-- 1/0.55 -- -- 1.20 1.00 -- -- -- --
The values of eand Yare decided by the contact angle , also can be
found in a bearing dictionary.
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Table 7-8 Factor of impact load
Load pattern Examplesfd
Uniform load or
slight impact
Electrical motor, water pumping,
ventilator and steam turbine1.0-1.2
Medium impact
Vehicles, machine tool, crane,
metallurgical machinery, andinternal combustion engine
1.2-1.8
Great impact
Crusher, rolling machine, vibrating
screen, construction machinery, and
Oil drilling machine
1.8-3.0
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If Fa/Freor Fa/Fr>e, Xand Yhave different values.
For the single row radial bearing or angular contact bearing,if Fa/Fre, Y=0, P=fdFr. That means the axial loads
contribution to the equivalent dynamic load can be ignored.
For the deep groove and angular contact ball bearings, e
keeps positively proportional to the ratio of Fa
/Cor
.
The ratio of Fa/Corindicates the relative magnitude of axial
load, and effects the values of eby the value of contact angle.
For cylindrical roller bearing and needle bearing, Pr=fdFr.
For thrust bearing,P
a=fdF
a.
5. Instructions on calculating equivalent load
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If the load and speed are variable, we calculate the bearing life by
kkm ananann .....2211
m
kkk
m
n
PanPanPanP
...222111
1 1 1 2 2 2
16670 16670
( ) ...h m m k k k
C CL
n P n a P n a P n a P
nmMean rotational speed;
P1,P
2, ,P
kEquivalent dynamic loads at different working situation;
n1, n2, , nk
Rotational speeds at different equivalent dynamic load;
a1, a2, , ak
Percentages of time among different working situation.
6. Bearing life under varying speed and varying load
PmMean equivalent dynamic load;
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L 10life indicates 90%probability that selected bearing would
carry its rated dynamic load for the specified number of design
hours.
That leaves a 10% probability that any given bearing would
have a lower life.
Certain applications call for greater reliability, such as
aerospace, military, instrumentation, and medical fields.
It is desirable to be able to adjust the expected life of a
bearing for higher reliability.
na 1 2 3 10L a a a L
7. Adjustment of life rating for reliability
a1Adjustment factor for reliability, see Table 7-10;
a2Adjustment factor for life;
a3Adjustment factor for working situation;
a2, and a3are proposed by the bearing producer.
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Reliability,%
40 50 60 70 80 90 95 96 97 98 99
a1
ball 7.01 5.45 4.14 2.00 1.961 0.62 0.53 0.44 0.33 0.21
roller 6.84 5.34 4.07 2.98 1.95
Table 7-10 Adjustment factor for reliability
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To avoid the plastic deformation, we need to check the static
strength of rolling contact bearings. We have0 0 0C S P
C0(radial C0r, axial C0a)Basic static load rating, which canbe found in the bearing dictionary.
S0Safety factor; if requiring high precision and smooth
rotation or great impact, S0=1.2-2.5; if the opposite condition,
S0=0.5-0.8; commonly, S0=0.8-1.2.
P0Equivalent static load.
For the bearings with 0 , P0r=max(X0Fr+Y0Fa, Fr)
X0Radial static load factor;
Y0
Axial static load factor;
X0, Y0can be found in the bearing dictionary.
For the radial bearings with =0, P0r=Fr;
For the thrust bearings with =90, P0a=Fa;
For the thrust self-aligning roller bearings, if Fr0.55Fa,
P0a=Fr+2.7Fa.
8. Static strength of rolling contact bearings
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Exceeding speed limits may result in excessively high operating
temperature due to friction between the cages supporting the
rolling elements.
Most catalogs list limiting speed for each bearing.
A given bearing will have a lower limiting speed as loads
increase.
The allowable speed ncan be estimated by
1 2 limn f f n
nlimLimiting speed of bearing;f1Factor of load varying, see Table 7-11;
f2Factor of load distribution, see Table 7-12.
9. Limiting speed of bearing
Table 7 11 Factor of load varying f
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Table 7-11 Factor of load varying, f1
Factorforloadvarying
f1
Value of P/C
1Self-aligning ball bearing;
2Self-aligning roller bearing;
3Tapered roller bearing;6Deep groove ball bearing;
7Angular contact ball bearing;
NCylindrical roller bearing.
Table 7-12 Factor of load distribution, f2
Contact angle
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We mount a pair of single-row angular contact bearing or
cylindrical bearing in the way of face-to-faceor back-to-back.
In the calculating process, we regard the pair of bearing as a wholebearing, satisfying that,
For angular contact ball bearing0.72 1.62r r rC C C
For tapered roller bearing 7/9
2 1.71r r rC C C
Their basic static load ratings are0 0
2r r
C C
Their limiting speeds are lim lim0.6 0.8n n
CrBasic dynamic load rating of single bearing;
C0rBasic static load rating of single bearing;
nlimLimiting speed of one bearing.
10. Calculations of angular contact bearings used in pair
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A pair of bearings 30308 are mounted as shown below. The applied
radial force Fr1=6000N, and Fr2=4000N, and the axial workingload FA=2500N. Try to find the axial load of each bearing.
Example 1
FS1
FS2
FA
1 2
Fr1 Fr2
11. Examples of bearing life design
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Solutions:
(1) Additional axial load FsFor the left bearing:
For the right bearing:
11
60001724
2 2 1.74
rs
FF N
Y
Pointing rightward
22
40001149
2 2 1.74
rs
FF N
Y
Pointing leftward
From a bearing dictionary, we have =125710.
So we have Y=0.4cot =0.4cot 12
5710=1.74.
(2) Axial load Fa
Because Fs1+FA-Fs2=1724+2500-1149=3075N>0, the shaft has an
inclination of moving rightward. The right bearing is pressed,
and the left bearing is relaxed.
1 1 1724a sF F N 2 1 4224a s AF F F N
FS1 FS2
FA
1 2
Fr1 Fr2
See Table 7-5
See Table 7-7
Example 2
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Example 2
Analysis the feasibility of mounting a pair of bearings 30309onto a
worm shaft. If it is not correct, please propose your improvement.
Question: Given that radial supporting forcesF
r1=1800N,Fr2=520N, the axial load on worm shaft FA=4100, shown below.
The rotational speed of worm n=1440r/min. Oil lubrication is
required. The design life of bearings L=11000h. It is under a
sizeable impact (Factor of impact load fd=1.3.)
FS2 FS1
FA
2 1
Fr2Fr1
Solutions:
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Solutions:(1) Calculation of bearing life
From a bearing dictionary, the basic dynamic load rating
C=64800N, basic static load rating C0=61200N. Under oillubrication, the limiting speed nlim=5000r/min. the contact angle
=125710. e=1.5tan =1.5 tan 125710=0.34.
1) Additional axial load Fs
0.4cot 0.4cot12 57 10Y
11 1800 517
2 2 1.74r
s FF NY
2
2
520149
2 2 1.74
rs
FF N
Y
2) Axial loadF
a
Fs2+FA-Fs1=149+4100-517=3732>0, so the shaft has an inclination
of moving rightward. That is the right bearing is pressed, and the
left bearing is relaxed. So we have
Fa1
=Fs1
+FA
=4249N
Fa2=Fs2=149N
FS2 FS1
FA
2
1
Fr2Fr1
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4) The bearing life is
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4) The bearing life is10
6 6310 10 64800
4913h