01 rolling contact bearing 2012 2
TRANSCRIPT
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Rolling-Contact
Bearings
Design II
Mechanical Engineering FacultyEngineering Division
Universidad Santo Toms
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initial test
Adapted from Budynas-Nisbett, 8ed.
1. Describe two differences between ball
and roller bearings
2. In a bearing mount with two bearings
of same reference (L10) what is reliabilityin this mount?
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Ball Bearing Nomenclature
Rotary ball bearings are
defined through geometry and
performance.Geometry:
Outside diameter
Inside diameter
Width
Adapted from Budynas-Nisbett, 8ed.
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Ball Bearing Nomenclature
Performance:
Load capacity (radial, axial,
moment)
Stiffness (radial, axial,
moment)
Runout
Bearing life
Allowable speed
Lubrication, etc.Adapted from Budynas-Nisbett, 8ed.
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Ball Bearing Types
Adapted from Budynas-Nisbett, 8ed.
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Roller Bearing Types
Adapted from Budynas-Nisbett, 8ed.
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Bearing Seals
Adopted from Juvinall RC, Marshek KM, Fundamentals Of Machine Component Design
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Ball and Roller Bearing
Types
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Ball and Roller Bearing
Types
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Ball vs. Roller Bearings
Roller bearings are stiffer and have a higher load
capacity than comparably sized ball bearings
This is due to the type of contact, line contact for
rollers vs. point contact for balls
Ball bearings have a lower friction
This also is a function of contact type.
Ball bearings can often be operated at higher speeds
Most ball bearings can take modest axial loads for free
Only tapered rollers can take axial loads
Ball bearings are less expensive than roller bearings
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Ball vs. Roller Bearings
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Bearing Failure Modes
Surface Fatigue Surface fatigue is the dominant
failure mode
The cyclic subsurface Hertzian
shear stresses produced by thecurved surfaces in rolling
contact may initiate and
propagate cracks that ultimately
dislodge particles and generate
surface pits
Typically, the raceways pit first,
resulting in noise, vibration, and
heat
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Bearing Failure Modes
Brinelling Static loads on stationary
bearings may cause brinelling
of the races The resulting local
discontinuities cause vibration,
noise, and heat
Adopted from
http://www.ejsong.com/mdme/memmods/MEM30009A/Bearings/Bearings.html
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Bearing Selection Criteria
When selecting bearings, both failure modes need
to be considered. As such, we need to examine:
Resistance to surface fatigue, expressed as basicdynamic load rating Cd
Resistance to brinelling, expressed as basic static
load rating C0
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Basic Load Ratings
Basic load ratings are a standardized measure provided
by the bearing industry to quantify the rolling element
bearings ability to resist surface fatigue and brinelling
The basic static load rating C0 is a measure of theresistance to failure by brinelling
The basic dynamic load rating (C)Cdis a measure of
resistance to failure due to surface fatigue
Adopted from SKF.com
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Bearing Life
Two identical bearings tested under different loads F1 and
F2will have respective lives L1 and L2according to:
Where: a = 3 for ball bearings; a = 10/3 for roller bearings
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Example 1: Timken Bearing
SKF ball bearing is rated as follows:
At a rated load of 2140 lb, the bearing has a life of 3000 hr at
500 rpm
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Basic Dynamic Load Rating
The basic dynamic load rating Cd is defined to be
the largest stationaryradial load that 90 percent of
a group of apparently identical bearings will survivefor 1 million revolutions (inner race rotating, outer
race fixed) with no evidence of failure by surface
fatigue..
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Basic Dynamic Load Rating
The bearing life L for a given load P can be determined as
follows:
Where: L = bearing life (revolutions to failure); Cd
= basic
dynamic load rating (90% reliability); P =applied bearing
loada =exponent (a = 3 for ball bearings and a = 10/3 for
roller bearings)
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Reliability Adjustments
Reliability adjustment factors, based on actual failure rate
data, allows a designer to select bearings for reliabilities
higher than 90%
LR= reliability-adjusted
bearing lifeKR= reliability life-
adjustment factor
L = bearing life
Adopted from Collins JA, Mechanical Design of Machine Elements and Machines
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Adjustments for Impact Loads
Rated load ratings are basic on static, continuous loading.
Time-varying loads reduce the bearing life and need to be
considered when selecting bearings.
Adopted from Collins JA, Mechanical Design of Machine Elementsand Machines
The applied equivalent
dynamic loadFeis
modified by the
estimated impact
factorIF
:
F = IF
Fe
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Adjustments for Impact Loads
You can also use.
Adopted from Urugal, A.C. Mechanical Design. 2004.
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Bearing Selection Procedure
1. From free-body diagram, determine the radial
loadFr
and axial thrust loadFa
2. Determine the design life requirementLdfor the
bearing(calculate or use table of recommended
design life for bearings)
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Bearing Selection Procedure
Adapted from Budynas-Nisbett, 8ed.
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Bearing Selection Procedure
3. Determine the reliabilityRappropriate to the
application and select the corresponding life-
adjustment factorK
R
4. Assess the severity of any shock or impact
associated with the application and select an
appropriate Impact FactorIF
5. Select the type of bearing
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Bearing Selection Procedure
6. Calculate the dynamic equivalent radial loadPe
Where: V = 1 when the inner ring rotates, and V = 1.2 when the outer
ring rotates. In Self-aligning bearings V = 1 for rotation of either ring.
In the first iteration use following table
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Bearing Selection Procedure
Others bearings: Checksuppliers engineering catalog
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Bearing Selection Procedure
7. Calculate the basic dynamic load rating requirement:
Cd
= required dynamic load rating to give a bearing reliability of R percent
L = life (revolutions)
KR
= reliability adjustment factor
IF
= application impact factor
Fe = equivalent radial load
a = exponent equal to 3 for ball bearings or 10/3 for roller bearings
8. With Cd
enter a basic load rating table and find the
smallest bearing with a load rating of at leastCd
Fe
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Bearing Selection Procedure
9. Note C0 , f0and other design parameter.
10.To obtain a new value ofY2
11.Find Cd
12. If the same bearing is obtained, stop.
13.If not, take next bearing and go to step 7.
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Example 2: Rolling Element
Bearing SelectionA support shaft for a new product has been designed with a
diameter of 1.6 inches. The force analysis shows that:
Radial bearing load Fr = 370 lb Axial bearing load Fa = 130 lb
Shaft speed n = 350 rpm
Design life specification is 10 years of operation, 50
days/year, 20hr/day Design reliability specification is R = 95%
The shaft is V-belt driven
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Example 3: Rolling Element
Bearing SelectionThe shaft shown in Figure is to be supported by two
bearings, one at location A and the other at location B. The
shaft is loaded by a commercial-quality driven helical gearmounted as shown. The gear imposes a radial load of 7000
lb and a thrust load of 2500 lb applied at a pitch radius of 3
inches. The thrust load is to be fully supported by bearing
A(bearing B takes no thrust load). It is being proposed to use
a single-row tapered roller bearing at location A, and anotherone at location B.
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Example 3: Rolling Element
Bearing Selection
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Example 3: Rolling Element
Bearing SelectionThe device is to operate at 350 rpm, 8 hours per day, 5 days
per week, for 3 years before bearing replacement is
necessary. Standard strength-based analysis has shown thatthe minimum shaft diameter must be 1.375 inches at both
bearing sites. Select suitable bearings for both location A and
location B
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Bearing Mount for Thrust
WARNING!!!!!
Thermal expansion of the shaft creates thrust force,
possibly overloading the bearings..
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Bearing Mount for Thrust
RECOMMENDED!!!!
The thrust force is provided by a single bearing. The second bearing only
takes radial loads because it is allowed to slide axially.
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Bearing Mounting
Shaft/bearing bore has a light interference fit.
Housing/outer race has a slight clearance fit.
Check manufacturers catalog
Match maximum permissible fillet radius.
Shaft or housing shoulders not to exceed 20%
of diameter.
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Permissible misalignment
Cylindrical and tapered roller bearings is limited to
0.001 rad.
For spherical ball bearings, the misalignment
should not exceed 0.0087 rad.
But for deep-groove ball bearings, the allowable
range of misalignment is 0.0035 to 0.0047 rad.
Adapted from Budynas-Nisbett, 8ed.
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References
Norton, R.L. Machine Design: an integrated
approach. 3rd ed, 2006.
Budynas and Nisbett. Shigleys MechanicalEngineering Design. 8th ed, 2006.
Mott, R.L. Machine Elements in Mechanical
Design. 4th
ed, 2004. Urugal, A.C. Mechanical Design. 2004.
Collins JA, Mechanical Design of Machine
Elements and Machine, 2009.
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References
http:// www.skf.com
http://www.fag.com
http://www.timken.com/es-
es/Knowledge/students/Pages/default.aspx
http://www.fag.com/http://www.skf.com/http://www.fag.com/http://www.timken.com/es-es/Knowledge/students/Pages/default.aspxhttp://www.timken.com/es-es/Knowledge/students/Pages/default.aspxhttp://www.timken.com/es-es/Knowledge/students/Pages/default.aspxhttp://www.timken.com/es-es/Knowledge/students/Pages/default.aspxhttp://www.timken.com/es-es/Knowledge/students/Pages/default.aspxhttp://www.fag.com/http://www.skf.com/http://www.fag.com/ -
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any questions?