Table of contents
Cylindrical roller bearings with disc cage/with spacers are suitable where:
|
Cylindrical roller bearing with full complement bearing/standard cage/disc cage, comparison of speed and load carrying capacity nG = limiting speed Cr = basic dynamic load rating SL1923 = full complement cylindrical roller bearing NJ23 = cylindrical roller bearing with standard cage LSL1923 = cylindrical roller bearing with disc cage |
 |
Design variants
These cylindrical roller bearings are available as:
LSL1923 and ZSL1923 correspond to dimension series 23
Cylindrical roller bearings with disc cage or with spacers are part of the group of radial roller bearings and correspond to dimension series 23. These single row bearings comprise radially split outer rings, removable inner rings, disc cages or spacers and cylindrical rollers. The rollers have profiled ends, i. e. they have a slight lateral curvature towards the ends. This modified line contact between the raceways and rolling elements prevents damaging edge stresses ➤ Figure. For mounting of the bearings, the inner ring can be removed.
Bearings with semi-locating bearing function
Cylindrical roller bearings LSL1923 have two rigid ribs on the outer ring and one rigid rib on the inner ring. An externally-guided flat brass disc cage prevents the rolling elements from coming into contact with each other during rolling ➤ Figure and ➤ section. The disc cage has pockets in which the rolling elements run. The rollers are guided between the ribs on the outer ring. The outer ring is axially split and held together by fasteners. Due to their design configuration, the bearings permit axial displacements of the shaft relative to the housing in one direction. In the opposite direction, they act as locating bearings. The maximum axial displacement s is given in the product tables.
|
Cylindrical roller bearing with disc cage Fr = radial load Fa = axial load
|
 |
Bearings with semi-locating bearing function
In the case of cylindrical roller bearings ZSL1923, plastic spacers prevent the rollers from coming into contact with each other during rolling ➤ Figure and ➤ section. The spacers are guided axially between the ribs on the outer ring. They are designed such that the rolling element set is self-retaining, so the outer ring with the rolling element set and the inner ring can be mounted separately from each other. Due to their design configuration, the bearings permit axial displacements of the shaft relative to the housing in one direction. In the opposite direction, they act as locating bearings. The maximum axial displacement s is given in the product tables.
|
Cylindrical roller bearing with spacers Fr = radial load Fa = axial load
|
 |
In addition to high basic dynamic load ratings Cr (and thus long rating life values), bearings for vibratory machinery must also be able to compensate or support considerable shaft tilting due to load or misalignment. The cylindrical roller bearings LSL and ZSL are therefore also available by agreement in the BIR design ➤ Table. In these bearings, the inner ring raceway is ground slightly spherical.
Many sizes of the bearings are also available as X-life bearings. These bearings exhibit considerably higher performance than comparable standard cylindrical roller bearings. This is achieved, for example, through the modified internal construction, the optimised contact geometry between the rollers and raceways, better surface quality and the optimised roller guidance and lubricant film formation.
Increased customer benefits due to X-life
These technical enhancements offer a range of advantages, such as:
Interchangeable with comparable standard bearings
Since X-life cylindrical roller bearings have the same dimensions as the corresponding standard bearings, the latter can be replaced without any problems by the higher-performance X-life bearings. The major advantages of X-life can therefore also be used for existing bearing arrangements with standard bearings.
Lower operating costs, higher machine availability
In conclusion, these advantages improve the overall cost-efficiency of the bearing position significantly and thus bring about a sustainable increase in the efficiency of the machine and equipment.
Suffix XL
X-life cylindrical roller bearings include the suffix XL in the designation ➤ section and ➤ link.
X-life indicates a high product performance density and thus a particularly significant benefit to the customer.
Designed for high radial loads
Cylindrical roller bearings LSL and ZSL are used as semi-locating bearings. These bearings can support not only high radial forces but also axial forces in one direction; i. e. they can guide the shaft axially in one direction. Furthermore, they can withstand high shock loads, vibrations and accelerations.
Higher basic dynamic load ratings lead to an increase in basic rating life
Due to the internal construction, the bearings can acommodate more rolling elements than conventional cylindrical roller bearings. As a result, there is a significant increase in the basic dynamic and static load rating and thus the basic rating life compared with conventional cylindrical roller bearings. ➤ Figure shows a comparison of the basic dynamic load rating Cr between a cylindrical roller bearing NJ2324 with a conventional cage, a bearing with a disc cage and a bearing with spacers. The advantage in basic dynamic load rating of approx. 14% gives an increase in the basic load rating of approx. 55% ➤ Figure.
|
Comparison of basic dynamic load ratings – |
 |
|
Comparison of basic percentage rating life – |
 |
Neither wear nor fatigue occurs on the rib contact running and roller end faces
In the case of cylindrical roller bearings with toroidal crowned rollers (TB design), the axial load carrying capacity has been significantly improved with the aid of new calculation and manufacturing methods. A special curvature of the roller end faces facilitates optimum contact conditions between the rollers and ribs ➤ Figure. As a result, the axial contact pressures on the rib are significantly minimised and a lubricant film capable of supporting higher loads is formed. Under standard operating conditions, this completely eliminates wear and fatigue at the rib contact running and roller end faces. In addition, the frictional torque is reduced by up to 50%. The bearing temperature during operation is therefore significantly lower. Bearings of the toroidal crowned design are available for a bore diameter of, or larger than, d = 90 mm ➤ dimension table.
|
Contact geometry of roller end face/rib face –
|
 |
Ratio Fa/Fr ≦ 0,4 or 0,6
The bearings can support axial loads on one side by means of the ribs on the inner and outer ring ➤ Figure. In order to ensure problem-free running (tilting of the rollers is prevented), they must always be subjected to radial load at the same time as axial load. The ratio Fa/Fr must not exceed the value 0,4. For bearings with toroidal roller ends (TB design), values up to 0,6 are permissible.
Continuous axial loading without simultaneous radial loading is not permissible.
Influencing factors on the axial load carrying capacity
Axial loads are supported by the bearing ribs and the roller end faces ➤ Figure and ➤ Figure. The axial load carrying capacity of the bearing is therefore essentially dependent on:
|
Force flow under axial load – |
 |
Bearings with standard roller ends
The permissible axial load Fa per can be calculated from the hydrodynamic load carrying capacity of the contact ➤ Equation.
Permissible axial load – bearings of standard design
Legend
| Fa per | N |
Permissible continuous axial load. In order to prevent unacceptably high temperatures in the bearing, Fa per must not be exceeded |
| Fa max | N |
Maximum continuous axial load in relation to rib fracture. In order to prevent unacceptably high pressures at the contact surfaces, Fa max must not be exceeded |
| kS | - |
Factor as a function of lubrication method ➤ Table. The factor takes into consideration the lubrication method used for the bearing. The better the lubrication and in particular the heat dissipation, the higher the permissible axial load |
| kB | - |
Factor as a function of the bearing series, kB = 28 |
| dM | mm |
Mean bearing diameter dM = (D + d)/2 ➤ link |
| n | min-1 |
Operating speed |
Factor kS
|
Lubrication method |
Factor kS |
|
|---|---|---|
|
from |
up to |
|
|
Minimal heat dissipation, drip feed oil lubrication, |
7,5 |
10 |
|
Poor heat dissipation, oil sump lubrication, |
10 |
15 |
|
Good heat dissipation, recirculating oil lubrication |
12 |
18 |
|
Very good heat dissipation, recirculating oil lubrication |
16 |
24 |
The precondition for these kS values is an operating viscosity of the lubricant of at least the reference viscosity ν1 in accordance with DIN ISO 281:2010.
Doped lubricating oils should be used, such as CLP (DIN 51517) and HLP (DIN 51524) of ISO-VG-grades 32 to 460 and ATF oils (DIN 51502) and transmission oils (DIN 51512) of SAE viscosity grades 75W to 140W.
Higher axial loads possible
For bearings with toroidal roller ends, the permissible axial loads are 50% higher ➤ Equation.
Permissible axial load – bearings of TB design
For bearings with rollers of the standard or TB design, the maximum permissible axial load Fa max ➤ Equation is calculated from the rib strength and the security against wear. This must not be exceeded, even if Fa per gives higher values ➤ Equation.
Maximum axial load – bearings of standard and TB design
Permissible axial load
Permissible axial load under shaft deflection of up to 2′
Under considerable shaft deflection, the shaft shoulder presses against the inner ring rib. In combination with the active axial load, this can lead to high alternating loading of the inner ring ribs. Under a shaft deflection of up to 2′, the permissible axial load can be estimated ➤ Equation.
If more severe tilting is present, a separate strength analysis is required. In this case, please contact Schaeffler.
Axial load under misalignment
Legend
| Fas | N |
Permissible axial load under misalignment |
Angular deviations are misalignments between the inner and outer ring
The permissible misalignment between the inner ring and outer ring is influenced by the internal bearing construction, the operating clearance, the forces acting on the bearings etc. Due to these complex relationships, it is not possible to give generally valid absolute values here. However, misalignments (angular deviations) between the inner ring and outer ring always have an effect on the running noise and the operating life of the bearings.
Permissible tilting
The permissible guide value at which, based on experience, there is no significant reduction in operating life is 3′.
Scope of value
The value applies to:
Checking by means of the calculation program BEARINX is recommended in all cases. If there is any uncertainty regarding possible misalignment, please consult Schaeffler.
Oil or grease lubrication is possible
The cylindrical roller bearings are not greased. They must be lubricated with oil or grease.
Pay attention to the compatibility of the lubricant with plastic
When using bearings with plastic spacers, compatibility between the lubricant and the cage material must be ensured if synthetic oils, lubricating greases with a synthetic oil base or lubricants containing a high proportion of EP additives are used.
If there is any uncertainty regarding the suitability of the selected lubricant for the application, please consult Schaeffler or the lubricant manufacturer.
Observe oil change intervals
Aged oil and additives in the oil can impair the operating life of plastics at high temperatures. As a result, stipulated oil change intervals must be strictly observed.
Providing additional seals in the adjacent construction
The bearings are not sealed; i. e. sealing of the bearing position must be carried out in the adjacent construction. This must reliably prevent:
Limiting speeds and reference speeds in the product tables
The product tables give two speeds for most bearings:
The limiting speed nG is the kinematically permissible speed of the bearing. Even under favourable mounting and operating conditions, this value should not be exceeded without prior consultation with Schaeffler ➤ link.
nϑr is used to calculate nϑ
The thermal speed rating nϑr is not an application-oriented speed limit, but is a calculated ancillary value for determining the thermally safe operating speed nϑ ➤ link.
The Schaeffler Noise Index (SGI) has been developed as a new feature for comparing the noise level of different bearing types and series. As a result, a noise evaluation of rolling bearings can now be carried out for the first time.
The SGI value is based on the maximum permissible noise level of a bearing in accordance with internal standards, which is calculated on the basis of ISO 15242. In order that different bearing types and series can be compared, the SGI value is plotted against the basic static load rating C0.
This permits direct comparisons between bearings with the same load carrying capacity. The upper limit value is given in each of the diagrams. This means that the average noise level of the bearings is lower than illustrated in the diagram.
The Schaeffler Noise Index is an additional performance characteristic in the selection of bearings for noise-sensitive applications. The specific suitability of a bearing for an application in terms of installation space, load carrying capacity or speed limit for example, must be checked independently of this.
|
Schaeffler Noise Index SGI = Schaeffler Noise Index C0 = basic static load rating |
 |
Limiting values
The operating temperature of the bearings is limited by:
Possible operating temperatures of bearings ➤ Table.
Permissible temperature ranges
|
Operating temperature |
Cylindrical roller bearings with disc cage or with spacers |
|---|---|
|
|
–30 °C to +120 °C |
In the event of anticipated temperatures which lie outside the stated values, please contact Schaeffler.
Bearings with a disc cage or spacers are suitable for applications with high dynamic inertia forces
In addition to the actual task of a cage, which is to hold rolling elements apart from each other, a cage designed for vibrations (e. g. for use in vibratory machinery) must be able to support, on a fatigue-resistant basis, principally the inertia forces that act on the cage due to its own mass, as well as the inertia forces of the rolling elements that act directly on the cage pockets. Since these applications also call for very high basic load ratings, conventional cages can only support this requirement under very limited conditions. As a result, bearings with a brass disc cage or plastic spacers have been developed, which constitute a transition from full complement bearings to conventional cage bearings.
Rolling elements are held by the cage
This cage is designed as a flat disc ➤ Figure. Facing towards the inside diameter are rolling element pockets that support the rolling elements. The cage inside diameter is extended downwards to below the pitch circle line. This gives retention of the rolling elements, i. e. the inner ring can be mounted separately from the rest of the bearing. Facing the outside diameter, the disc cage is seated concentrically between the ribs in a slot in the outer ring.
|
Rollers and solid brass disc cage |
 |
Lower bearing frictional torque due to the geometry of the spacers
The plastic spacers were developed specially for the series ZSL1923 ➤ Figure. They are designed such that the rolling element set is self-retaining, i. e. the bearing and inner ring can be mounted separately from each other.
|
Rollers and plastic spacers |
 |
The standard is CN
As standard, cylindrical roller bearings with disc cage or with spacers have the radial internal clearance CN (normal) ➤ Table. CN is not stated in the designation.
When used in vibratory machinery, both bearing rings have a tight fit. As a result, and due to the temperature differential between the inner ring and outer ring, the internal clearance C4 is generally necessary. As standard, bearings for vibratory machinery therefore have this internal clearance group.
Certain sizes are also available by agreement with the larger internal clearance C3, C4 and C5 ➤ Table.
The values for radial internal clearance correspond to DIN 620-4:2004 (ISO 5753-1:2009) ➤ Table. They are valid for bearings which are free from load and measurement forces (without elastic deformation).
Radial internal clearance of cylindrical roller bearings with disc cage or with spacers
|
Nominal |
Radial internal clearance |
||||||||
|---|---|---|---|---|---|---|---|---|---|
|
d |
CN |
C3 |
C4 |
C5 |
|||||
|
mm |
μm |
μm |
μm |
μm |
|||||
|
over |
incl. |
min. |
max. |
min. |
max. |
min. |
max. |
min. |
max. |
|
‒ |
24 |
20 |
45 |
35 |
60 |
50 |
75 |
65 |
90 |
|
24 |
30 |
20 |
45 |
35 |
60 |
50 |
75 |
70 |
95 |
|
30 |
40 |
25 |
50 |
45 |
70 |
60 |
85 |
80 |
105 |
|
40 |
50 |
30 |
60 |
50 |
80 |
70 |
100 |
95 |
125 |
|
50 |
65 |
40 |
70 |
60 |
90 |
80 |
110 |
110 |
140 |
|
65 |
80 |
40 |
75 |
65 |
100 |
90 |
125 |
130 |
165 |
|
80 |
100 |
50 |
85 |
75 |
110 |
105 |
140 |
155 |
190 |
|
100 |
120 |
50 |
90 |
85 |
125 |
125 |
165 |
180 |
200 |
|
120 |
140 |
60 |
105 |
100 |
145 |
145 |
190 |
200 |
245 |
|
140 |
160 |
70 |
120 |
115 |
165 |
165 |
215 |
225 |
275 |
|
160 |
180 |
75 |
125 |
120 |
170 |
170 |
220 |
250 |
300 |
|
180 |
200 |
90 |
145 |
140 |
195 |
195 |
250 |
275 |
330 |
|
200 |
225 |
105 |
165 |
160 |
220 |
220 |
280 |
305 |
365 |
|
225 |
250 |
110 |
175 |
170 |
235 |
235 |
300 |
330 |
395 |
|
250 |
280 |
125 |
195 |
190 |
260 |
260 |
330 |
370 |
440 |
|
280 |
315 |
130 |
205 |
200 |
275 |
275 |
350 |
410 |
485 |
The main dimensions of cylindrical roller bearings correspond to ISO 15:2017 (DIN 616:2000 and DIN 5412-1:2005).
The limiting dimensions for chamfer dimensions correspond to DIN 620‑6:2004. Overview and limiting values ➤ section. Nominal value of chamfer dimension ➤ link.
The dimensional and running tolerances correspond to the tolerance class Normal in accordance with ISO 492:2014. Tolerance values in accordance with ISO 492 ➤ link.
For a description of the suffixes used in this chapter ➤ Table and medias interchange http://www.schaeffler.de/std/1B69.
|
Suffix |
Description of suffix |
|
|---|---|---|
|
BIR |
Inner ring raceway ground slightly spherical |
Available by agreement |
|
BR |
Black oxide coated |
Available by agreement |
|
C3 |
Radial internal clearance C3 (larger than normal) |
Available by agreement |
|
C4 |
Radial internal clearance C4 (larger than C3) |
Available by agreement |
|
C5 |
Radial internal clearance C5 (larger than C4) |
Available by agreement |
|
TB |
Bearing with increased axial load carrying capacity |
Standard dependent on bearing size |
|
XL |
X-life bearing |
Standard dependent on bearing size |
Examples of composition of bearing designation
The designation of bearings follows a set model. Examples ➤ Figure and ➤ Figure. The composition of designations is subject to DIN 623‑1 ➤ link.
|
Cylindrical roller bearing with disc cage: designation structure |
 |
|
Cylindrical roller bearings with spacers, internal clearance C3: designation structure |
 |
P = Fr under purely radial load of constant magnitude and direction
The basic rating life equation L = (Cr/P)p used in the dimensioning of bearings under dynamic load assumes a load of constant magnitude and direction. In radial bearings, this is a purely radial load Fr. If this condition is met, the bearing load Fr is used in the rating life equation for P (P = Fr).
P = Fr
Non-locating bearings can only support radial loads. For these bearings ➤ Equation.
Equivalent dynamic load
P is a substitute force for combined load and various load cases
If the condition described above is not met, i. e. if in addition to the radial force Fr there is also an axial force Fa, a constant radial force must first be determined for the rating life calculation that (in relation to the rating life) represents an equivalent load. This force is known as the equivalent dynamic bearing load P.
Fa/Fr ≦ e or Fa/Fr ＞ e
The calculation of P is dependent on the load ratio Fa/Fr and the calculation factors e and Y ➤ Equation and ➤ Equation.
Equivalent dynamic load
Equivalent dynamic load
Legend
| P | N |
Equivalent dynamic bearing load |
| Fr | N |
Radial load |
| Fa | N |
Axial load |
| e | - |
Factor, e = 0,3 |
| Y | - |
Factor, Y = 0,4 |
P0 = F0r
For cylindrical roller bearings subjected to static load ➤ Equation.
Equivalent static load
Legend
| P0 | N |
Equivalent static bearing load |
| F0r | N |
Largest radial load present (maximum load) |
S0 = C0/P0
In addition to the basic rating life L (L10h), it is also always necessary to check the static load safety factor S0 ➤ Equation.
Static load safety factor
Legend
| S0 | - |
Static load safety factor |
| C0 | N |
Basic static load rating |
| P0 | N |
Equivalent static bearing load |
In order to prevent slippage damage, a minimum radial load of P ＞ C0r/60 is necessary during continuous operation
In order that no slippage occurs between the contact partners, the cylindrical roller bearings must be constantly subjected to a sufficiently high radial load. For continuous operation, experience shows that a minimum radial load of the order of P ＞ C0r/60 is necessary. In most cases, however, the radial load is already higher than the requisite minimum load due to the weight of the supported parts and the external forces.
If the minimum radial load is lower than indicated above, please consult Schaeffler.
Support bearing rings over their entire circumference and width
In order to allow full utilisation of the load carrying capacity of the bearings and thus also achieve the requisite rating life, the bearing rings must be rigidly and uniformly supported by means of contact surfaces over their entire circumference and over the entire width of the raceway. Support can be provided by means of a cylindrical seating surface. The seating and contact surfaces should not be interrupted by grooves, holes or other recesses. The accuracy of mating parts must meet specific requirements ➤ Table to ➤ Table.
For secure radial location, tight fits are necessary
In addition to supporting the rings adequately, the bearings must also be securely located in a radial direction, to prevent creep of the bearing rings on the mating parts under load. This is generally achieved by means of tight fits between the bearing rings and the mating parts. If the rings are not secured adequately or correctly, this can cause severe damage to the bearings and adjacent machine parts. Influencing factors, such as the conditions of rotation, magnitude of the load, internal clearance, temperature conditions, design of the mating parts and the mounting and dismounting options must be taken into consideration in the selection of fits.
If shock type loads occur, tight fits (transition fit or interference fit) are required to prevent the rings from coming loose at any point. Clearance, transition or interference fits ➤ Table.
The following information provided in Technical principles must be taken into consideration in the design of bearing arrangements:
The bearings must also be securely located in an axial direction
As a tight fit alone is not normally sufficient to also locate the bearing rings securely on the shaft and in the housing bore in an axial direction, this must usually be achieved by means of an additional axial location or retention method. The axial location of the bearing rings must be matched to the type of bearing arrangement. Shaft and housing shoulders, housing covers, nuts, spacer rings, retaining rings, adapter and withdrawal sleeves etc. are generally suitable; example ➤ Figure.
A minimum of IT6 should be provided for the shaft seat and a minimum of IT7 for the housing seat
The accuracy of the cylindrical bearing seat on the shaft and in the housing should correspond to the accuracy of the bearing used. For cylindrical roller bearings with the tolerance class Normal, the shaft seat should correspond to a minimum of standard tolerance grade IT6 and the housing seat to a minimum of IT7. Guide values for the geometrical and positional tolerances of the bearing seating surfaces ➤ Table, tolerances t1 to t3 in accordance with ➤ Figure. Numerical values for IT grades ➤ Table.
Guide values for the geometrical and positional tolerances of bearing seating surfaces
|
Bearing |
Bearing seating surface |
Standard tolerance grades to ISO 286-1 |
||||
|---|---|---|---|---|---|---|
|
to ISO 492 |
to DIN 620 |
Diameter tolerance |
Roundness tolerance |
Parallelism tolerance |
Total axial runout tolerance of abutment shoulder |
|
|
t1 |
t2 |
t3 |
||||
|
Normal |
PN (P0) |
Shaft |
IT6 (IT5) |
Circumferential load IT4/2 |
Circumferential load IT4/2 |
IT4 |
| Shaft | IT6 (IT5) |
Point load IT5/2 |
Point load IT5/2 |
IT4 | ||
|
Housing |
IT7 (IT6) |
Circumferential load IT5/2 |
Circumferential load IT5/2 |
IT5 |
||
| Housing | IT7 (IT6) |
Point load IT6/2 |
Point load IT6/2 |
IT5 | ||
Numerical values for ISO standard tolerances (IT grades) to ISO 286-1:2010
|
IT grade |
Nominal dimension in mm |
|||||||
|---|---|---|---|---|---|---|---|---|
|
over |
18 |
30 |
50 |
80 |
120 |
180 |
250 |
|
|
incl. |
30 |
50 |
80 |
120 |
180 |
250 |
315 |
|
|
Values in μm |
||||||||
|
IT4 |
6 |
7 |
8 |
10 |
12 |
14 |
16 |
|
|
IT5 |
9 |
11 |
13 |
15 |
18 |
20 |
23 |
|
|
IT6 |
13 |
16 |
19 |
22 |
25 |
29 |
32 |
|
|
IT7 |
21 |
25 |
30 |
35 |
40 |
46 |
52 |
|
Ra must not be too high
The roughness of the bearing seats must be matched to the tolerance class of the bearings. The mean roughness value Ra must not be too high, in order to maintain the interference loss within limits. The shafts must be ground, while the bores must be precision turned. Guide values as a function of the IT grade of bearing seating surfaces ➤ Table.
Roughness values for cylindrical bearing seating surfaces – guide values
|
Nominal diameter of the bearing seat d (D) |
Recommended mean roughness value for ground bearing seats Ramax |
||||
|---|---|---|---|---|---|
|
mm |
μm |
||||
|
Diameter tolerance (IT grade) |
|||||
|
over |
incl. |
IT7 |
IT6 |
IT5 |
IT4 |
|
‒ |
80 |
1,6 |
0,8 |
0,4 |
0,2 |
|
80 |
500 |
1,6 |
1,6 |
0,8 |
0,4 |
The contact surfaces for the rings must be of sufficient height
The mounting dimensions of the shaft and housing shoulders, and spacer rings etc., must ensure that the contact surfaces for the bearing rings are of sufficient height. The transition from the bearing seat to the abutment shoulder must be designed with rounding to DIN 5418:1993 or an undercut to DIN 509:2006. Proven mounting dimensions for the radii and diameters of abutment shoulders are given in the product tables ➤ link and ➤ Figure. These dimensions are limiting dimensions (maximum or minimum dimensions); the actual values should not be higher or lower than specified.
Rib support in axially loaded bearings
Ribs under axial load must be supported over their entire height and entire circumference. The size and axial runout accuracy of the contact surfaces on the inner ring rib must be observed especially in the case of cylindrical roller bearings subjected to high loads, since these factors also influence the uniformity of the rib load and the running accuracy of the shaft. This means that the ribs may be subjected to damaging alternating stresses even in the case of very small misalignments. If the mounting dimensions indicated in the product tables are observed, the problems described can be reliably avoided ➤ Figure and ➤ link.
Support in semi-locating bearings
In semi-locating bearings, it is sufficient to support the bearing rings on one side, on the rib supporting the axial load ➤ Figure.
|
Support of the inner ring rib – dc = recommended height of shaft shoulder with axially loaded rib Arrow = force flow |
 |
The mounting and dismounting options for cylindrical roller bearings, by thermal, hydraulic or mechanical methods, must be taken into consideration in the design of the bearing position.
As the bearings are not self-retaining, they are easy to mount
The cylindrical roller bearings LSL 1923 and ZSL 1923 are not self-retaining. As a result, the bearing parts can be mounted separately from each other ➤ section. This gives simplified mounting of the bearings, especially when the two bearing rings have a tight fit.
Rolling bearings must be handled with great care
Rolling bearings are well-proven precision machine elements for the design of economical and reliable bearing arrangements, which offer high operational security. In order that these products can function correctly and achieve the envisaged operating life without detrimental effect, they must be handled with care.
The Schaeffler Mounting Handbook MH 1 gives comprehensive information about the correct storage, mounting, dismounting and maintenance of rotary rolling bearings http://www.schaeffler.de/std/1B68. It also provides information which should be observed by the designer, in relation to the mounting, dismounting and maintenance of bearings, in the original design of the bearing position. This book is available from Schaeffler on request.
The further development of products may also result in technical changes to catalogue products
Of central interest to Schaeffler is the further development and optimisation of its products and the satisfaction of its customers. In order that you, as the customer, can keep yourself optimally informed about the progress that is being made here and with regard to the current technical status of the products, we publish any product changes which differ from the printed version in our electronic product catalogue.
We therefore reserve the right to make changes to the data and illustrations in this catalogue. This catalogue reflects the status at the time of printing. More recent publications released by us (as printed or digital media) will automatically precede this catalogue if they involve the same subject. Therefore, please always use our electronic product catalogue to check whether more up-to-date information or modification notices exist for your desired product.
In addition to the data in this chapter, the following chapters in Technical principles must also be observed in the design of bearing arrangements:
