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FAG special spherical roller bearingsfor vibratory machinery
X-life quality
Welcome to the Future! Unmatched Engineering Excellence. INA and FAG
X-life – this is the premium grade fromINA and FAG, offering you new oppor-tunities for success. Benefit from thecombined expertise of two brands with aworldwide reputation – in every area ofapplication covering automotive, machinebuilding and precision engineering.
In the Schaeffler Group, INA and FAGhave brought together their strengths to give a new dimension in quality:
X-life.Higher cost-effectiveness. Higher operational security.
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X-life offers excellent product quality thatfar exceeds previous standards.
Furthermore, X-life optimises all the parameters that are decisive for a problem-free production cycle. This includes correct fitting and dismantling,maintenance intervals matched to thespecific application and the selection of lubricants matched to operatingconditions.
A further convincing advantage of X-life isproduct characteristics that fulfil yourspecific requirements and offer additionalbenefits: for example, particularly low-noise, maintenance-friendly or highload capacity system solutions.
Your X-life advantages at a glance:
• product characteristics far above the norm
• lasting quality assurance and control• extremely high reliability• even greater security
in planning and systems• optimum availability• smooth-running work processes• reduced energy consumption• the maximum possible
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Contents 1 FAG spherical roller bearings for vibratory stresses 21.1 Operating conditions for bearings
in vibratory machinery 21.2 Bearing series and basic designs 21.2.1 X-life spherical roller bearings of series 223..-E1 21.2.2 Spherical roller bearings of series 223..-A 31.2.3 Spherical roller bearings of series 233..-A 31.3 Bearings with tapered bore 31.4 Bearings with coated bore 31.5 Specification T41A(D) 31.5.1 Tolerances for bearing bore and outside diameter 31.5.2 Radial internal clearance groups, reduction
in radial internal clearance of bearings with tapered bore 4
1.6 Permissible radial acceleration 61.7 Heat treatment 6
2 Dimensioning of bearings 62.1 Two bearing screen with circle throw 62.2 Two bearing screen with straight line motion 82.3 Eccentric screen 102.4 Nomogram for calculation of centrifugal force 112.5 Nomogram for calculation of basic load ratings 12
3 Design of bearing arrangements 133.1 Two bearing screen with circle throw
(grease lubrication) 133.2 Two bearing screen with circle throw
(oil sump lubrication) 143.3 Two bearing screen with circle throw
(recirculating oil lubrication) 153.4 Two bearing screen with straight line motion
(oil splash lubrication) 163.5 Four bearing screen (grease lubrication) 17
4 Lubrication of bearings 184.1 Grease lubrication 184.2 Oil lubrication 184.2.1 Oil sump lubrication 194.2.2 Recirculating oil lubrication 214.3 Recommended lubricants 22
5 Dimension tables for FAG special spherical roller bearings for vibratory machinery 23
5.1 Series 223..-E1-T41A(D) 235.2 Series 223..-A-MA-T41A 24
1 FAG spherical rollerbearings for vibratorystresses
1.1 Operating conditions forbearings in vibratory machinery
Vibratory screens used for gradingmaterials and other vibratorymachinery such as road rollers andsaw frames are among the machinessubjected to the most severestresses. The rolling bearings fitted in theexciter units of these machinesmust support not only high loadsand high speeds but alsoaccelerations and centrifugalforces. In many cases, theseapplications involve adverseenvironmental conditions such as contamination and moisture.The special spherical roller bearingsdeveloped by FAG are matched tothe operating conditions in vibratorymachinery and have proved highlysuccessful in practical use.In particular, the cages of therolling bearings are subjected tostresses arising from high radialaccelerations. In unfavourablecases, these may be overlaid byaxial accelerations as well. The rotating imbalance generatesrotating shaft deflection andadditional sliding motion withinthe bearings. This increases thefriction and therefore the operatingtemperature of the bearings. The special spherical roller bearingscan support dynamic angularmisalignments of up to 0,15°. If larger misalignments must beaccommodated, please consultour Application Engineering.
1.2 Bearing series and basicdesigns
FAG special spherical roller bearingsfor vibratory machinery have maindimensions corresponding todimension series 23 and 33 (E DIN 616: 1995-01 or ISO 15).For the particular stresses occurringin vibratory machinery, we manu-facture all the special sphericalroller bearings described in thispublication in accordance withspecification T41A(D), see alsosection 1.5.Very high load carrying capacity isachieved through optimum use ofbearing cross-section as a result offurther development of sphericalroller bearings of series 223..-E1.In the design for vibratory stresses,the bearings are supplied with borediameters of up to 150 mm. They have sheet steel windowcages of high structural fatiguestrength, surface hardened andguided on the outer ring. Bearings of dimension series with a bore diameter of more than150 mm are supplied by us indesign A. The inner ring has threerigid ribs. Inertia forces are directlyradially outwards by two solidbrass cage halves guided on theouter ring. Wider bearings of series 233..-Ahave an internal constructioncomparable to bearings of series223..-A. These bearings are used inspecial cases where very high loadcarrying capacity is required.
1.2.1 X-life spherical roller bearingsof series 223..-E1
FAG spherical roller bearings of theE1 design have an inner ringwithout a rib and are characterisedby very high load carrying capacity.This advantage is also offered byFAG special bearings for vibratorystresses of design 223..-E1-T41A(D),Figure 1. This is the new FAGstandard design for bearings with a bore diameter of 40 up to andincluding 150 mm (bore code 08 to 30). After extensive testing, bearings ofdesign 223..-E1-T41A have provedextremely successful in numerouspractical applications.The bearing has one sheet steelwindow half cage guided on theouter ring for each row of rollers.The cage halves are supported viathe cage guide ring in the outerring. The guide ring is of a singlepiece design. All cage parts aresubjected to a special surfacehardening process.
FAG spherical roller bearings for vibratory stressesOperating conditions · Bearing series and basic designs
2
1: X-life design 223..-E1-T41A(D) of specialspherical roller bearings for vibratorymachinery (bore code 08 to 30)
FAG spherical roller bearings for vibratory stressesBearing series and basic designs · Bearings with tapered bore · Bearings with coated bore · Specification T41A(D)
3
1.2.2 Spherical roller bearingsof series 223..-A
If the bore diameter is 160 mm or greater (bore code � 32), we recommend the proven specialspherical roller bearings of design223..-A-MA-T41A, Figure 2.The bearings have one rigid centralrib and two lateral retaining ribs onthe inner ring. The two-piece solidbrass cage (suffix MA) is guided onthe outer ring.
1.2.3 Spherical roller bearingsof series 233..-A
Where vibratory machinery requiresvery high basic load ratings, we canby agreement supply specialspherical roller bearings of series233..-A(S)-MA-T41A with a borediameter of 100 to 200 mm (bore code 20 to 40). These bearings have three rigidribs on the inner ring. The splitsolid brass cage (suffix MA) isguided on the outer ring.
1.3 Bearings with tapered bore
In special cases such as sawframes, bearings are also availablewith a tapered bore (taper 1:12).These designs have the suffixE1-K-T41A or A-K-MA-T41A.
1.4 Bearings with coated bore
In order to reduce or prevent frettingcorrosion between the bearing boreand the shaft, we can for specificorders (and as standard for 22317-E1-T41D to 22322-E1-T41D)supply spherical roller bearingswith a cylindrical bore treated witha thin layer chromium plating. This ensures that the possibility ofdisplacement (non-locating bearingfunction) between the bearing boreand shaft in response to thermalinfluences is maintained over andbeyond a long period of operation. The bearings with a coated borecorrespond in their dimensions andtolerances to, and are interchange-able with, the FAG standard bearingsfor vibratory machinery.Ordering example for a bearing witha thin layer chromium plated bore: 22324-E1-J24BA-T41A.
Note: This coating is applied to thebearings 22317-E1-T41D to 22322-E1-T41D as standard.
1.5 Specification T41A(D)
FAG spherical roller bearingsfor vibratory machinery aremanufactured in accordance withthe specification T41A(D). This takes into consideration theparticular requirements of theapplication. The specificationdefines the tolerances and radialinternal clearance of the specialspherical roller bearings.
1.5.1 Tolerances for bearing boreand outside diameter
Specification T41A(D) prescribes arestriction of the bore tolerance tothe upper half of the normaltolerance zone. For the outsidediameter, only the centre half ofthe normal tolerance zone ispermissible. In bearings with atapered bore, the reduced tolerancerange applies to the outsidediameter only. For tolerance values,see table, Figure 3 (page 4).Through these measures, thesliding fit required for the innerring is reliably achieved with shaft tolerances g6 or f6 and theinterference fit required for theouter ring is reliably achieved withhousing tolerance P6. The innerring does not have pure point loadand the outer ring is subjected tocircumferential load.The other tolerances are inaccordance with tolerance classPN to DIN 620.2: Design 223..-A-MA-T41A of special spherical
roller bearings for vibratory machinery(bore code � 32)
Nominal bearing bore diameter
Nominal outside diameter
Inner ringDimensions in mm
over 30 50 80 120 180 250incl. 50 80 120 180 250 315
Nominal bearing borediameter
1.5.2 Radial internal clearancegroups, reduction in radialinternal clearance of bearingswith tapered bore
Specification T41A(D) prescribes C4as the standard internal clearancegroup for all spherical rollerbearings of vibrating screen designand it is therefore not necessary toindicate this explicitly. In this way,radial preloading of the bearingsis prevented in the event ofunfavourable interaction betweenthe different influences such asfits, deformations, etc. This appliesespecially during the startup andrunning-in periods, during whichthe largest temperature differencesoccur between the inner and outerring.
FAG spherical roller bearings for vibratory stressesSpecification T41A(D)
4
Tolerances in μm
Deviation Δdmp 0 0 0 0 0 0–7 –9 –12 –15 –18 –21
3: Restricted tolerance according to specification T41A(D)
Tolerances in μm
Deviation ΔDmp –5 –5 –10 –13 –13 –15–13 –18 –23 –28 –30 –35
Outer ringDimensions in mm
over 80 150 180 315 400 500incl. 150 180 315 400 500 630
With cylindrical boreInternal clearance in μm
Internal clearance min 45 55 65 80 100 120 145 170 180 200 220 240 260 280group C3 max 60 75 90 110 135 160 190 220 240 260 290 320 350 370
Internal clearance min 60 75 90 110 135 160 190 220 240 260 290 320 350 370group C4 max 80 100 120 145 180 210 240 280 310 340 380 420 460 500
With tapered boreInternal clearance in μm
Internal clearance min 50 60 75 95 110 135 160 180 200 220 250 270 300 330group C3 max 65 80 95 120 140 170 200 230 260 290 320 350 390 430
Internal clearance min 65 80 95 120 140 170 200 230 260 290 320 350 390 430group C4 max 85 100 120 150 180 220 260 300 340 370 410 450 490 540
Dimensions in mmover 30 40 50 65 80 100 120 140 160 180 200 225 250 280incl. 40 50 65 80 100 120 140 160 180 200 225 250 280 315
4: Radial internal clearance of FAG spherical roller bearings
Control value for minimum radialinternal clearance after fitting
Displacementon taper 1:12
Reduction in radialinternal clearance
FAG spherical roller bearings for vibratory stressesSpecification T41A(D)
5
It is only necessary to consider aspecial radial internal clearance forspherical roller bearings in vibratorymachinery in rare cases, forexample if the material to bescreened is hot or the bearingarrangement is subjected toexcessive external heat.
In special cases such as sawframes, bearings with an internalclearance other than C4 may benecessary. The suffix for the radialinternal clearance, e.g. C3, mustthen be indicated explicitly. Wesupply bearings of this design byagreement. For radial internal clear-ance values of special spherical
roller bearings, see table, Figure 4.Bearings with a tapered bore aremounted on a conical shaft seat or,using a sleeve, on a cylindricalshaft. The reduction in the radialinternal clearance during mounting(see table, Figure 5) can be takenas an indication of the seatingbetween the inner ring and shaft.
d Shaft Sleeve CN C3 C4over incl. min max min max min max min min minmm mm mm mm
5: Reduction in radial internal clearance in mounting of spherical roller bearings with tapered bore (solid shaft)
30 40 0,02 0,025 0,35 0,4 0,35 0,45 0,015 0,025 0,0440 50 0,025 0,03 0,4 0,45 0,45 0,5 0,02 0,03 0,0550 65 0,03 0,04 0,45 0,6 0,5 0,7 0,025 0,035 0,05565 80 0,04 0,05 0,6 0,75 0,7 0,85 0,025 0,04 0,0780 100 0,045 0,06 0,7 0,9 0,75 1 0,035 0,05 0,08
100 120 0,05 0,07 0,7 1,1 0,8 1,2 0,05 0,065 0,1120 140 0,065 0,09 1,1 1,4 1,2 1,5 0,055 0,08 0,11140 160 0,075 0,1 1,2 1,6 1,3 1,7 0,055 0,09 0,13160 180 0,08 0,11 1,3 1,7 1,4 1,9 0,06 0,1 0,15180 200 0,09 0,13 1,4 2 1,5 2,2 0,07 0,1 0,16
200 225 0,1 0,14 1,6 2,2 1,7 2,4 0,08 0,12 0,18225 250 0,11 0,15 1,7 2,4 1,8 2,6 0,09 0,13 0,2250 280 0,12 0,17 1,9 2,6 2 2,9 0,1 0,14 0,22280 315 0,13 0,19 2 3 2,2 3,2 0,11 0,15 0,24
Nominal bearingbore diameter
1.6 Permissible radial acceleration
Since the centrifugal forces aresupported against the outer ring,high acceleration forces are possiblein special spherical roller bearingsfor vibratory machinery, see diagrambelow.Permissible radial accelerationvalues of special spherical rollerbearings for vibratory machinerya) n · dm = 350 000 min-1 · mm
Maximum possible values withoptimum mounting conditionsand oil lubrication, e.g. planetarygearbox
b) n · dm = 140 000 min-1 · mmNormal operating conditionsfor saw frames with greaselubrication
c) n · dm = 230 000 to 300 000 min-1 · mm Normal use for vibrating screenswith grease or oil lubrication
2 Dimensioning of bearings
Vibrating screen bearings arenormally designed for a basic ratinglife Lh of between 10 000 and 20 000 hours. This is calculated as follows:Lh = (C/P)p · 106/(n · 60) [h]C Basic dynamic load rating [kN],
see bearing tables, section 5P Equivalent dynamic load [kN],
see sections 2.1 to 2.3p = 3,33 Life exponent
for roller bearingsn Speed [min-1]
When determining the equivalentdynamic load P of spherical rollerbearings for vibrating applications,the influences that cannot beprecisely defined are taken intoconsideration by means of a safetyfactor fz of 1,2 times the radialbearing load Fr. Based on practicalexperience, this gives sufficientlylong running times.More precise calculation can beachieved using the expandedadjusted rating life Lhnm to ISO 281,Supplementary Sheet 1 (see alsoCatalogue HR 1). The fatigue limitload Cu required in this case isstated in the dimension tables.
2.1 Two bearing screen with circle throw
Figure 6 shows a schematic of animbalance-type two bearing screen. The bearing load imposed by thecentrifugal force of the screen boxis derived from the mass of thescreen box, the vibration radiusand the speed in accordance withthe following formula:
Fr =1
·m
· r · ω2 =z 103
FAG spherical roller bearings for vibratory stressesDimensioning of bearings
6
=1
·G
· r(π · n)2
[kN] (1)z g 30
Fr Radial bearing load [kN] m Mass of screen box [kg] r Vibration radius [m] ω Angular velocity [1/s] G Weight of screen box [kN] g Acceleration due to gravity
[9,81 m/s2]n Speed [min-1] z Number of bearings
The vibration radius r in two bearingscreens can be determined fromthe ratio of the screen box weightto the exciter weight. Since twobearing screens generally operatebetween the critical rangeapproaching the static amplitude, it can be assumed that the commoncentroidal axis of the two masses(screen box and exciter) ismaintained during rotation, Figure 7.
Based on this precondition:
G · r = G1 (R – r)
The vibration radius is thus
r =G1 · R
[m] (2)G + G1
whereG Weight of screen box [kN]G1 Weight of exciter [kN]R Distance between centre
of gravity of exciter andbearing axis [m]
r Vibration radiusof screen box [m]
G1 · R Imbalance momentof exciter [kN m]
G + G1 Total weight supported by springs [kN]
1.7 Heat treatment
All FAG spherical roller bearings ofseries 223 and 233 for vibratorystresses are heat treated such thatthey are dimensionally stable up to an operating temperature of200 °C.
50 100 20070Bearing bore
a
b
c
5
10
20
50
100
200
300
Acc
eler
atio
n
150mm
g
R
rR-r
G1
G
If (2) is incorporated in (1) and the expression is transformed, the radial bearing load is
Fr =1
·G1 ·
R ·(π · n)
2
[kN] (3)z g
1 +G1 30G
Example
Weight of screen box G = 35 kNVibration radius r = 0,003 mSpeed n = 1 200 min-1
Number of bearings z = 2Bearing load according to formula (1)
Fr =1
·35
· 0,003(π · 1 200)2
=2 9,81 30
= 84,5 [kN]
The equivalent dynamic bearingload required in order to determinethe necessary basic dynamic loadrating of the bearing is then
P = 1,2 · Fr = 1,2 · 84,5 = 101 [kN]
Dimensioning of bearingsTwo bearing screen with circle throw
7
6: Schematic of two bearing screen with circle throw
7: The vibration radius is determined by the ratio of the screen box weight to the exciter weight
Rr
G1
G
2.2 Two bearing screen withstraight line motion
In principle, the exciter in a twobearing screen with straight linemotion comprises two contra-rotatingsynchronous circular throw systems,Figure 8.The forces are determined byresolving the rotating centrifugalforce vectors of the imbalanceshafts into two components, in thedirection of the line connecting the two shafts and the directionperpendicular to this line. It can beseen that the components lying inthe direction of the connecting linecancel each other out, whereas theperpendicular components add up,generating a harmonic pulsatinginertia force that induces straightline vibration of the screen box.Since the so-called static amplitudeis induced in the direction ofvibration due to the supercriticaloperation and the commoncentroidal axis of the screen boxand the imbalance masses doesnot vary during vibration, thebearing loads are as follows:In the direction of vibration
Frmin =1
·m
· r · ω2 =z 103
=1
·G
· r ·(π · n)2
=z g 30
=1
·G1 · (R – r) ·(π · n)
2
[kN] (4)z g 30
wherer [m] Vibration radiusR [m] Distance between the centres
of gravity of the exciters andthe corresponding bearingaxes
Perpendicular to the direction ofvibration
Fr max =1
·G1 · R ·(π · n)
2
[kN] (5)z g 30
giving a somewhat larger bearingload.In contrast to a circle throw screen,in which the bearing load isconstant, the bearing load in astraight line screen alternates twiceduring one revolution of the excitershafts between Fr max and Fr min.If formula (4) is compared withformula (1), it can be seen that theminimum bearing load of a screenwith straight line motion is exactlythe same as the bearing load of acomparable circle throw screen.For a straight line screen with aload varying according to asinusoidal function, the bearingload can be determined accordingto the formula
Fr = 0,68 · Fr max + 0,32 · Fr min [kN]
Whereas the bearing load in a circlethrow screen can be determinedsimply from data for the screen boxG, vibration radius r and speed n,these data only allow calculation ofthe minimum load in a straight linescreen. For more precise calculation,it is also necessary to know eitherthe exciter mass G1 or the distanceR between the centres of gravity ofthe exciters from their bearingaxes. It is then possible using
G · r = G1 (R – r) [kN m]
to determine the unknown quantity.
Dimensioning of bearingsTwo bearing screen with straight line motion
8
Example
Weight of screen box G = 33 kNWeight of exciter G1 = 7,5 kNRadius r = 0,008 mSpeed n = 900 min-1
Number of bearings z = 4
With R =r (G +G1)
G1
=0,008 (33 + 7,5)
= 0,0432 [m]7,5
this gives, according to (4) and (5)
Frmin =1
·33
· 0,008 · (π · 900)2
4 9,81 30
= 59,8 [kN]
Fr max =1
·7,5
· 0,0432 ·(π · 900)2
4 9,81 30
= 73,3 [kN]
Bearing loadFr = 0,68 · 73,3 + 0,32 · 59,8 =
= 69 [kN]
The equivalent dynamic bearingload required in order to determinethe necessary basic dynamic loadrating of the bearing is then
P = 1,2 · 69 = 83 [kN]
Dimensioning of bearingsTwo bearing screen with straight line motion
9
8: Schematic of two bearing screen with straight line motion
R
G
2r
G12
2.3 Eccentric screen
In contrast to a two bearing screen,the vibration radius of an eccentricscreen is a function of theeccentricity of the shaft. The bearingfor the two inner rings is determinedusing the same formula as for thecircle throw screen
Fr =1
·G
· r ·(π · n)2
[kN] (1)z g 30
where r is the eccentric radius ofthe crankshaft and z is the numberof inner bearings, Figure 9.The influence of the supportsprings on the loading of the inner bearings can be regarded as negligible.The outer bearings of the eccentricscreen are only lightly loaded sincethe centrifugal force of the screenbox during idling is compensatedby counterweights (G2). The load onthese bearings is not constant; it varies according to a sinusoidalpattern due to the support springson the screen box. In operation, thematerial in the box interferes withthe balanced condition of themachine. This places additionalload on the outer bearings.However, this additional load isvery small. The selection of bearings is basedon the shaft diameter. This resultsin bearings whose load carryingcapacity is so high that a fatiguelife calculation is unnecessary.Since these bearings do not undergovibration, spherical roller bearingsof the standard design are sufficient.
Example
Weight of screen box G = 60 kNEccentric radius r = 0,005 mSpeed n = 850 min-1
Number of bearings z = 2Inner bearings: Bearing loadaccording to formula (1)
Fr =1
·60
· 0,005 · (π · 850)2
=2 9,81 30
= 121 kN
Dimensioning of bearingsEccentric screen
10
The equivalent dynamic bearingload required in order to determinethe necessary basic dynamic loadrating of the bearing is thenP = 1,2 · 121 = 145 [kN]
9: Schematic of an eccentric screen
G
r
G2
Spherical roller bearing(design T41A)
Spherical roller bearingNormal design
2.4 Nomogram for calculating the centrifugal force of the imbalance masses or the centrifugal force of the screenbox mass
Dimensioning of bearingsNomogram for calculation of centrifugal force
11
Fmax, Fmin and F are centrifugal forcesn is the speed [min-1]r is the vibration radius [m]R is the distance between the
centre of gravity of the exciterand the bearing axis [m]
b is the acceleration [m/s2] G is the weight of the screen box
[kN]G1 is the weight of the imbalance
mass [kN]g = 9,81 is the acceleration due
to gravity [m/s2]
Fmax =G1 · R ·(π · n)
2
[kN]g 30
Fmin =G1 · (R – r) ·(π · n)
2
[kN]g 30
F =G
· r ·(π · n)2
[kN]g 30
5 000
4 000
3 000
2 000
1 000
800
600
500
400
300
200
100 1 000800
600500400
300
200
10080
605040
30
20
10
8
654
3
2
10,8
0,60,50,4
0,01
0,020,03
0,05
0,1
0,20,3
0,5
1
23
5
10
2030
50
100
200300
500
1 000
2 0003 000
5 000
10 000
1 0,1
2
3
456
108
20
30
405060
80100
200
300
400500600
8001 000
0,2
0,3
0,40,50,6
0,81
2
3
456
810
20
30
405060
80100
1
4
3
5
2
Example: 1 n = 1 200 min-1
2 r = 3 mm3 b = 47,3 m/s2
4 G = 35 kN5 F = 168 kN
n G1, G Fmax, Fmin, Fb R, R-r, r
[min-1] [mm][kN][kN] [m/s2]
The following are required in orderto calculate the basic dynamic loadrating C [kN]:
n Speed [min-1]Lh Basic rating life [h]P Equivalent dynamic load [kN]
In two bearing screens with circlethrow and inner bearings witheccentric screens
P = 1,2 ·F
[kN]z
In two bearing screens with straightline motion
Dimensioning of bearingsNomogram for calculation of basic load ratings
12
P = 1,2 · (0,68 · Fmax + 0,32 · Fmin)z
where 1,2 is the safety factorz is the number of bearingsF is the centrifugal force according
to nomogram 1 (section 2.4)
5 000
1
4
3
5
2
Example: 1 n = 1 200 min-1
2 Lh = 10 000 h3 C/P = 7,24 P = 100 kN5 C = 720 kN
n P
[min-1] [kN][kN][h]
6 000
4 0003 000
2 000
1 000800
600500400300
200
10080
60504030
20
108
654
3
2
0,6
0,8
2
1
3
4
56
8
10
20
30
40
5060
80
100100
200
300
400
500600
CLh
50 000
40 000
30 000
20 000
10 000
8 000
5 000
4 000
3 000
2 000
1 000
6 000
3
4
5
6
7
8
9
10
12
14
16
18
20
5 000
4 000
3 000
2 000
1 000
800
600
500
400
300
200
100
C—P
2.5 Nomogram for calculating the basic dynamic load rating required
3 Design of bearingarrangements
3.1 Two bearing screen with circlethrow (grease lubrication)
Figure 10 shows the essentialbearing arrangement design of atwo bearing screen with circlethrow and grease lubrication. The imbalance shaft is supportedin two special spherical rollerbearings FAG 223..-E1-T41A. The bearing on the drive side isfitted as a locating bearing whilethe opposing bearing is a non-locating bearing.
Fitting and dismantling of bearings
After inspection of the adjacentparts, the bearing is then mountedin the housing bore. Smallerbearings can be pressed in whilecold. For larger bearings, thehousing is heated uniformly to the point where the interferencebetween the bearing outer ring andhousing bore is eliminated. As thehousing cools down, the interferencefit is achieved. The bearing andhousing are then slid onto theshaft.For dismantling, it is easier topress the bearing out of thehousing if the guard tube flange(part A in Figure 10) is replaced bya screw mounted ring equippedwith several extraction screws.
Lubrication and sealing
A favourable option is to feed thegrease as shown here via thecircumferential groove and thelubrication holes in the bearing
outer ring. In this way, the freshgrease is fed directly to the rollingand sliding surfaces of the rollingbearing, ensuring uniform lubricationof both rows of rollers. The fresh grease displaces the old,possibly contaminated grease fromthe interior of the bearing. On the inner side of the bearingarrangement, the old greaseescapes via the gap in the grease
Design of bearing arrangementsTwo bearing screen with circle throw (grease lubrication)
13
baffle and collects in the guardtube. On the outer side, it collectsat the grease collector pocket, fromwhich it is periodically removed.The bearing is sealed againstexternal influences by a labyrinththat can be relubricated and whosesealing action can be furtherincreased by a V ring on theinnermost labyrinth passage.
10: Two bearing screen with circle throw (grease lubrication)
1 Locating bearing2 Non-locating bearingA Guard tube flangeB Grease baffleC Grease collector pocket
1
2
B
A
C
3.2 Two bearing screen with circlethrow (oil sump lubrication)
Figure 11 shows the essentialbearing arrangement design of atwo bearing screen with circlethrow and oil sump lubrication.Sealing against entry of externalcontamination is provided by agrease-filled labyrinth that can berelubricated. A splash ring with aoil collector groove prevents egressof oil. On the bearing side, thesealing area is shielded by a flingerring.In order to prevent the grease inthe labyrinth entering the oilcavities, a V ring is fitted betweenthe labyrinth and splash ring. The connecting hole in the lowersection of the housing equalisesthe oil sump level between the twosides of the bearing. The oil levelshould be such that the lowestroller in the bearing is immersed toapproximately half its diameter inoil when the bearing is stationary.At this level, there is an overflowhole that is closed off after thehousing is filled. The oil outletscrew contains a small permanentmagnet that draws wear particlesout of the oil. The oil quantityshould be as large as possible sothat the oil does not need to bechanged too frequently. In general,the shaft guard tube is used as anadditional oil reservoir.
Design of bearing arrangementsTwo bearing screen with circle throw (oil sump lubrication)
14
11: Two bearing screen with circle throw (oil sump lubrication)
1
2
B
A
C
1 Locating bearing2 Non-locating bearingA Vent screwB Flinger ringC Oil overflow holeD Connecting holeE Oil outlet screw
D
E
3.3 Two bearing screen with circlethrow (recirculating oillubrication)
The design of the bearing arrange-ment with recirculating oil lubrica-tion shown in Figure 12 is similarto that of the bearing arrangementwith oil sump lubrication (seesection 3.2). The connecting holein the lower section of the housingequalises the oil level between thetwo sides of the bearing.
The sealing arrangement is takenfrom the oil sump lubrication. The oil outlet hole is located atsuch a level that, even if the oilfeed is interrupted, there is still anemergency oil reserve available.The oil is fed via the lubricationgroove and lubrication holes in thebearing outer ring. Oil filtration isabsolutely essential (cf. section4.2.2).
Design of bearing arrangementsTwo bearing screen with circle throw (recirculating oil lubrication)
15
12: Two bearing screen with circle throw (recirculating oil lubrication)
12
1 Locating bearing2 Non-locating bearing
3.4 Two bearing screen withstraight line motion (oil splash lubrication)
Figure 13 shows the bearingarrangement of an exciter for a twobearing screen with straight linemotion. The two contra-rotating,synchronously geared imbalanceshafts are fitted with FAG specialspherical roller bearings223..-E1-T41A. The bearings on thegear side are fitted as locating
bearings in order to preventdisruption to the gear cyclingbehaviour if length variations occur(temperature differences). The bearings are lubricated by theoil thrown off by the gears and aflinger shield. Baffle plates on thelower halves of the housing endfaces ensure that the oil levelreaches approximately the centre ofthe lowest roller in the bearings.
Design of bearing arrangementsTwo bearing screen with straight line motion (oil splash lubrication)
16
The passage for the drive shaft isequipped with a splash ring sealand – in order to prevent ingress ofcontamination – with a labyrinth. A V ring can also be fitted betweenthe labyrinth and splash ring. The oil level is just high enough thatthe lower gear and flinger shieldare immersed in the oil sump. The oil level is monitored by lateraloil level indicators.
13: Two bearing screen with straight line motion (oil splash lubrication)
1 Locating bearing2 Non-locating bearingA Baffle platesB Oil level indicator
1 2
A
A
B
3.5 Four bearing screen (grease lubrication)
Figure 14 shows the eccentric shaftof a four bearing screen. Since thestresses acting on the inner bearingsare comparable with those actingon the bearings of a two bearingscreen, these positions are fittedwith FAG special spherical rollerbearings of series 223..-E1-T41A.Although the interaction of therotating screen box centrifugalforce and the directionally constantspring forces does not give a purepoint load on the inner ring, thefits selected are generally the sameas for the two bearing screen. The outer rings have a P6 fit in thehousing, while the inner rings havean f6 or g6 fit on the shaft.One of the two inner bearings isfitted as a locating bearing, whilethe other is a non-locating bearingwith an inner ring that can bedisplaced along the shaft. In allother respects, the design of theinner bearing arrangement shownis identical to the bearingarrangement for a two bearingscreen with grease lubrication.Conditions are different in theouter bearings. In order to ensurethat, if possible, imbalance forcesare not transmitted to thefoundations and the bearing loadremains low, the imbalance momentof the screen box in the eccentricscreen is compensated by means ofcounterweights. During idling, theouter bearings are only subjectedto the forces exerted by the supportsprings.The support springs are preloadedto such an extent that the outerbearings are subjected to asinusoidally pulsating butdirectionally constant radial load.
Although the precisely balancedcondition is disrupted duringoperation by the material in thebox – the spring forces are overlaidby an uncompensated rotatingcentrifugal force – and the loaddirection may therefore vary withina certain angle, the bearing fits aredetermined on the assumption thatthe outer ring is subjected to pointload.A loose fit must therefore beselected for the outer rings in thehousing bore. The inner rings arenormally located on the shaft – asshown – using extraction sleeves. The bearing on the drive side isfitted as a locating bearing while the opposing bearing is a
Design of bearing arrangementsFour bearing screen (grease lubrication)
17
non-locating bearing with an outerring capable of axial displacement.
Normal machining tolerances thathave proved effective for the outerbearing seats are
Shaft: h8/h9 (shaft tolerance for location by extractionsleeve)
Housing: H7
Since the outer bearings do notundergo translation movement andare only subject to light loads,normal spherical roller bearingswith a tapered bore and normalinternal clearance can be selected.
14: Four bearing screen (grease lubrication)
A
r
1
2
1 Locating bearing2 Non-locating bearingA Counterweight
1
2
A
4 Lubrication of bearings
Spherical roller bearings in vibratorymachinery are subjected to veryhigh operating loads and adverseenvironmental conditions. The lubricant type, lubricationmethod and lubricant supply mustbe carefully selected and matchedin order to fulfil the requirementsfor functional suitability and servicelife of the vibratory machinerybearings.Depending on the operatingconditions, bearing size andparticular requirements of the plant operator, lubrication usinggrease or oil can be selected.
4.1 Grease lubrication
In most vibratory machinery, thespecial spherical roller bearings arelubricated using grease. Greaselubrication is normally used up to a speed parameter n · dm = 300 000 min-1 · mm(n operating speed, dm mean bearingdiameter). Only greases that havebeen tested and proven should beused, see section 4.3. Any changeof grease type should be avoided ifpossible. For normal operating conditions invibratory machinery, we recommendlithium soap greases with EP(extreme pressure) and anti-corrosionadditives corresponding topenetration class 2. The minimumrequirements described inDIN 51 825 are not sufficient forthis application. Instead, thesuitability of greases for use in therolling bearing must be demonstratedas is the case with, for example,the FAG greases Arcanol MULTITOPand LOAD400.
In applications with higher operatingtemperatures, for example inscreens for hot materials or wherethe bearings may in special casesundergo considerable heating bythe material in the box, specialgreases with high thermal stabilityshould be used.The base oil viscosity required isdependent on the operatingconditions. The aim should be to achieve a viscosity ratio κ = ν/ν1 � 2, where ν is theoperating viscosity and ν1 is thereference viscosity, see alsoCatalogue HR 1. When rolling bearings are fitted,the internal cavities of the bearingsmust be filled to capacity withgrease. In order to prevent excessiveworking of the lubricant, thehousing cavities on both sides ofthe bearing must remain empty sothat the excess grease can bedispersed into the free space in thehousing during the startup phase. It is recommended that relubricationshould be carried out via thelubrication groove and thelubrication holes that are presentas standard in the outer ring of allFAG special spherical roller bearings.This ensures uniform supply oflubricant to both rows of rollers.Where rolling bearings arerelubricated from the side, thedistance between the housing walland the end face of the bearingshould be as small as possible sothat the grease can reach thebearing interior quickly and withoutlosses. The grease outlet holeshould be located on the oppositeside of the bearing.In bearing arrangements for vibratorymachinery, it is advisable torelubricate the bearings with smallquantities of grease at short intervals.
Lubrication of bearingsGrease lubrication · Oil lubrication
18
The table in Figure 15 givesrelubrication quantities as afunction of bearing size and speed.These relubrication quantitiesrelate to a relubrication intervalof 50 operating hours and normaloperating temperatures.If continuous relubrication is carriedout by means of a central lubricantsupply system, the grease quantitym1 required per hour per bearingcan be determined using the formulam1 = 0,00004 · D · Bwherem1 = required grease quantity
[g/h]D = bearing outside diameter
[mm]B = bearing width [mm]
The labyrinth seals should berelubricated once per week, ormore frequently if operatingconditions are unfavourable (heavyexposure to dust, moisture, highoperating temperature). The greaseshould be the same as that used inthe rolling bearings.
4.2 Oil lubrication
If the speeds are above the normalrange for grease lubrication (i. e. speed parameter n · dm � 300 000 min-1 · mm), oil lubrication must be provided.Oil lubrication may also be necessaryif there is heating by external sourcesor for reasons of maintenance.For lubrication of bearings, werecommend mineral oils or syntheticoils with EP (extreme pressure) andanti-corrosion additives, see alsosection 4.3. Good quality multi-gradeoils can also be used.The viscosity ratio κ = ν/ν1
(ν = operating viscosity, ν1 = refer-ence viscosity) should be � 2.
Bore code
4.2.1 Oil sump lubrication (bath lubrication)
Oil sump lubrication is normallyused to a speed parameter n · dm = 300 000 min-1 · mm; withfrequent oil changes, it can be used
up to n · dm = 500 000 min-1 · mm. In this lubrication method, the lubricant is conveyed to therolling contact points by anygears, the imbalance mass or therolling elements themselves. The oil level in the machine or
Lubrication of bearingsGrease lubrication · Oil lubrication
19
bearing housing must be sufficientlyhigh that the gears or imbalancemasses are dipped in the oil andcreate a swirling effect. When thebearing is stationary, the lowestroller must be half immersed in theoil, Figure 16.
Speed min–1
500 600 700 800 900 1 000 1 200 1 400 1 600 1 800 2 000 2 200 2 400 2 600 2 800 3 000 3 200
15: Relubrication quantities in g for spherical roller bearings 223 in vibratory machinery (relubrication interval: 50 operating hours)
08 5 5 5 5 5 5 5 5 5 5 5 5 5 5 5 5 5 09 5 5 5 5 5 5 5 5 5 5 5 5 5 5 5 10 1010 5 5 5 5 5 5 5 5 5 5 5 5 10 10 10 10 15
11 5 5 5 5 5 5 5 5 5 5 10 10 10 10 15 15 2012 5 5 5 5 5 5 5 5 5 10 10 10 10 15 1513 5 5 5 5 5 5 5 10 10 10 10 15 15 20
14 5 5 5 5 5 5 10 10 10 15 15 20 2515 5 5 5 5 5 5 10 10 10 15 20 2516 5 5 5 10 10 10 10 10 15 20 25
17 5 5 10 10 10 10 10 15 20 25 3518 10 10 10 10 10 10 15 20 25 30 4019 10 10 10 10 10 15 15 25 35 45
20 10 10 10 10 15 15 20 30 4022 10 10 15 15 20 20 30 50 7024 15 15 20 25 30 35 55 85
26 15 20 20 25 35 40 6528 20 25 30 35 45 60 10030 25 30 40 50 65 90
32 25 35 45 60 80 10034 30 40 55 80 110 14036 35 50 65 90 120
38 45 65 90 13040 50 70 100 15044 70 105 160
48 105 17052 120 20056 190
b a
a is the normal oil levelb is the lowest permissible oil level
Bearing series 223a bmm
Bore code
A sufficiently large oil quantity willextend the oil change interval. If the cavities in the housings arenot sufficient, the shaft guard tubebetween the bearings can also beused as an oil reservoir or anadditional container can beprovided.
The oil change interval is dependenton the contamination and theageing condition of the oil. Guide values for the oil quantityand oil change intervals as afunction of the bearing bore aregiven in Figure 17. For furtherdetails, see publication
Lubrication of bearingsOil lubrication
20
WL 81 115/4 EA “Lubrication ofrolling bearings”.
We recommend regular oilinspection, since the results ofsuch inspections will allow moreprecise determination of oilchange intervals.
16: Determining the oil level at standstill
08 31 3409 35 3810 39 42
11 42 4612 46 5013 50 54
14 54 5915 58 6216 62 67
17 66 7118 69 7419 72 78
20 78 8422 86 9424 93 101
26 100 10928 107 11730 115 125
32 122 13334 129 14036 137 149
38 144 15640 152 16544 168 182
48 182 19552 196 21156 212 228
Lubrication of bearingsOil lubrication
21
4.2.2 Recirculating oil lubrication
If the speed parameter is higherthan the permissible value for bathlubrication or where specialconditions apply (increased heatdissipation required, insufficientlylarge oil cavities), recirculating oillubrication must be used. The oilshould be fed via the lubricationgroove and lubrication holes in thebearing outer ring. Guide values for normal oil flowrates can be determined from thediagram in Figure 18. In order to prevent oil backing upin the lubrication system, thecross-sections of the unpressurisedreturn ducts must be adapted tothe cross-sections of the feed ducts(4 to 5 times larger).In recirculating oil lubrication, it isabsolutely essential that a filter isprovided for retaining wear particlesand contaminants in order toprevent impairment of the bearingoperating life.Through evaluation of regular oilinspections, the oil change intervalscan be matched more accurately tothe operating conditions.
17: Oil quantity and oil change interval as a function of bearing bore diameter
18: Minimum oil flow rate for spherical roller bearings of series 223 in vibratory machinery
300mm200
100
60
40
20
100,2 0,4 0,6 1,0 2 4 6 8 10 l 20
dBearing
bore
Oil quantity
Oil change interval 2-3 months
10-12 months
10050
l/min2010
210,5
0,20,10,05
0,020,010,005
0,0020,001
10 20 50 100 200 500 1 000 mm 3 000
Oilquantity
Bearing outside diameter D
5
4.3 Recommended lubricants
Greases for vibrating screenbearing arrangements
The quality of FAG Arcanol rollingbearing greases is carefullymonitored by means of 100%inspection of every batch.
Greases for normal temperatures:Arcanol MULTITOPArcanol LOAD400Arcanol LOAD220
Greases for high temperatures:Arcanol TEMP120
In the case of greases that have notbeen subjected to our incominggoods inspection, we cannot makeany statements regarding batchfluctuations, formulation changesor production influences. However, we maintain a list ofsuitable commercial greases thatis regularly updated. The currentissue can be requested from us bytelephoning +49 9721 91-3883.
Oils for vibrating screen bearingarrangements
If oils are to be used for thisapplication, it must be demonstratedthat the additives package iseffective in the rolling bearing. In principle, it is possible to usemineral oils and synthetic oils, with the exception of silicone oils. It is not advisable to use oils withviscosity index improvementagents. A current list of oils thatmay be recommended can berequested from us by telephoning+49 9721 91-3883.
Lubrication of bearingsRecommended lubricants
22
Referencespeed
Limitingspeed
Fatigue limitload
FAG special spherical roller bearings for vibratory machineryWith cylindrical bore, series 223..-E1-T41A(D)
23
Ddd2
ns
B
r
r
D1
Shaft Dimensions Basic load Designation Massratings
d D B r ns D1 d2 dyn. stat. nG nB Bearing ≈min ≈ ≈ Cr C0r Cur
mm kN kN min-1 FAG kg
FAG special spherical roller bearings for vibratory machinery, with cylindrical bore, series 223..-E1-T41A(D)
40 40 90 33 1,5 4,8 76 52,4 156 150 13,1 7 500 5 800 22308-E1-T41A 1,0545 45 100 36 1,5 6,5 84,7 58,9 186 183 16,1 6 700 5 300 22309-E1-T41A 1,3950 50 110 40 2 6,5 92,6 63 228 224 20,3 6 000 4 950 22310-E1-T41A 1,9
55 55 120 43 2 6,5 101,4 68,9 265 260 23,9 5 600 4 650 22311-E1-T41A 2,2760 60 130 46 2,1 6,5 110,1 74,8 310 310 28 5 000 4 300 22312-E1-T41A 2,8965 65 140 48 2,1 9,5 119,3 83,2 355 365 32,5 4 800 3 950 22313-E1-T41A 3,57
70 70 150 51 2,1 9,5 128 86,7 390 390 36,5 4 500 3 850 22314-E1-T41A 4,2175 75 160 55 2,1 9,5 136,3 92,4 440 450 40,5 4 300 3 650 22315-E1-T41A 5,1880 80 170 58 2,1 9,5 145,1 98,3 500 510 45 4 300 3 450 22316-E1-T41A 6,27
85 85 180 60 3 9,5 154,2 104,4 540 560 50 4 000 3 300 22317-E1-T41D 7,0690 90 190 64 3 12,2 162,5 110,2 610 630 55 3 600 3 100 22318-E1-T41D 8,5195 95 200 67 3 12,2 171,2 116 670 695 60 3 000 2 900 22319-E1-T41D 9,69
100 100 215 73 3 12,2 183,3 124,2 815 915 75 3 000 2 550 22320-E1-T41D 12,8110 110 240 80 3 15 204,9 143,1 950 1 060 91 2 600 2 250 22322-E1-T41D 17,7120 120 260 86 3 15 222,4 150,8 1 080 1 160 103 2 600 2 080 22324-E1-T41A 22,5
130 130 280 93 4 17,7 240 162,2 1 250 1 370 117 2 400 1 870 22326-E1-T41A 28140 140 300 102 4 17,7 255,7 173,5 1 460 1 630 132 2 200 1 700 22328-E1-T41A 35,1150 150 320 108 4 17,7 273,2 185,3 1 630 1 860 147 2 000 1 550 22330-E1-T41A 42,2
All spherical roller bearings of series 223..-E1-T41A(D) are X-life designs.
Referencespeed
Limitingspeed
Fatigue limitload
FAG special spherical roller bearings for vibratory machineryWith cylindrical bore, series 223..-A-MA-T41A
24
Dd
B
ns
r
r
D1
Shaft Dimensions Basic load Designation Massratings
d D B r ns D1 dyn. stat. nG nB Bearing ≈min ≈ Cr C0r Cur
mm kN kN min-1 FAG kg
FAG special spherical roller bearings for vibratory machinery, with cylindrical bore, series 223..-A-MA-T41A
160 160 340 114 4 17,7 289 1 430 1 900 136 2 000 1 490 22332-A-MA-T41A 52,7170 170 360 120 4 17,7 305 1 600 2 120 144 1 800 1 380 22334-A-MA-T41A 59,5180 180 380 126 4 23,5 324 1 700 2 240 229 1 500 1 280 22336-A-MA-T41A 72,2
190 190 400 132 5 23,5 339 1 860 2 500 173 1 500 1 220 22338-A-MA-T41A 81200 200 420 138 5 23,5 359 2 080 2 800 189 1 400 1 130 22340-A-MA-T41A 93,5220 220 460 145 5 23,5 392 2 320 3 350 217 1 300 980 22344-A-MA-T41A 120
97/0
5/07
Pri
nted
in G
erm
any
byD
ruck
haus
WEP
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bH
Every care has been taken to ensure the
correctness of the information but no
liability can be assumed for any incorrect
or incomplete data. We reserve the right
to make technical changes.
© Schaeffler KG · 2007, May
Reproduction in whole or in part without
our authorisation is prohibited.
WL 21 100/5 EA
Schaeffler KG
Georg-Schäfer-Strasse 30
97421 Schweinfurt (Germany)
Internet www.fag.com
E-mail [email protected]
Phone +49 9721 91-0
Fax +49 9721 91-3435
