Single row full complement cylindrical roller bearings are suitable where:
|
Cylindrical roller bearing with cage/full complement bearing, comparison of speed and load carrying capacity Cr = basic dynamic load rating nG = limiting speed |
|
Design variants
Single row full complement cylindrical roller bearings are available as:
In addition to the bearings described here, Schaeffler supplies single row full complement cylindrical roller bearings in other types, series and dimensions. These products are described in some cases in special publications. If necessary, please contact Schaeffler. Larger catalogue bearings GL 1.
Key features
Single row full complement cylindrical roller bearings are part of the group of radial roller bearings. These bearings comprise solid outer rings, inner rings and full complement rolling element sets. Due to the absence of a cage, the bearing can accommodate the largest possible number of rolling elements. 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. The series SL1923 is self-retaining. Certain sizes are also available in an increased capacity design ➤ link. These bearings have the suffix E ➤ Table.
Bearings with semi-locating bearing function
In these bearings, the outer ring has one rigid rib and the inner ring has two rigid ribs ➤ Figure. As a result, axial displacements of the shaft relative to the housing can be compensated within certain limits. The maximum axial displacement s is given in the product tables. Since the axial motion occurs without constraint in the bearing itself, this is practically free from friction with a rotating bearing. Cylindrical roller bearings of this design are used as semi-locating bearings, i. e. they can guide the shaft axially in one direction, while they act in the opposite direction as non‑locating bearings ➤ section.
The bearings are held together in handling and mounting by a transport and mounting retaining device on the outer ring ➤ Figure. This retaining device remains in the bearing even after mounting and must not be subjected to axial load.
|
Single row full complement cylindrical roller bearing – Fr = radial load Fa = axial load
|
|
Bearings with semi-locating bearing function
Cylindrical roller bearings of this design have two rigid ribs on the outer ring and a self-retaining rolling element set, while the inner ring has only one rigid rib ➤ Figure. As a result, the inner ring can be removed from the bearing. This gives easier mounting of the cylindrical roller bearings.
The bearings are used as semi-locating bearings, i. e. they can guide the shaft axially in one direction ➤ section and permit axial displacements in the bearing between the shaft and housing in one direction. The maximum axial displacement s is given in the product tables.
|
Single row full complement cylindrical roller bearing Fr = radial load Fa = axial load |
|
Many sizes are available as X-life bearings ➤ Figure. 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.
|
Single row full complement cylindrical roller bearing of X-life design
|
 |
Increased customer benefits due to X-life
These technical enhancements offer a range of advantages, such as:
Interchangeable with comparable standard bearings
Since the single row full complement 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.
Due to their special technical features, single row full complement X-life cylindrical roller bearings are highly suitable, for example, for bearing arrangements in:
X-life indicates a high product performance density and thus a particularly significant benefit to the customer.
Designed for very high radial loads
Due to the absence of a cage, the bearing can accommodate the largest possible number of rolling elements. As a result, full complement cylindrical roller bearings have very high radial load carrying capacity.
Neither wear nor material 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 axial frictional torque is reduced by up to 50%. The bearing temperature during operation is therefore significantly lower. Available bearings of toroidal crowned design ➤ Table.
|
Contact geometry of roller end face/rib face –
|
 |
Single row full complement cylindrical roller bearings with toroidal crowned roller ends available by agreement
|
Series |
from bore diameter d |
|---|---|
|
mm |
|
|
SL1818 |
460 |
|
SL1822 |
140 |
|
SL1829 |
300 |
|
SL1830 |
180 |
|
SL1923 |
90 |
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. 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 ➤ Table |
| 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, oil mist lubrication, low operating viscosity (ν ＜ 0,5 · ν1) |
7,5 |
10 |
|
Poor heat dissipation, oil sump lubrication, oil spray lubrication, low oil flow |
10 |
15 |
|
Good heat dissipation, recirculating oil lubrication (pressurised oil lubrication) |
12 |
18 |
|
Very good heat dissipation, recirculating oil lubrication with oil cooling, high operating viscosity (ν ＞ 2 · ν1) |
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.
Bearing factor kB
|
Series |
kB |
|---|---|
|
SL1818 |
4,5 |
|
SL1829 |
11 |
|
SL1830 |
17 |
|
SL1822 |
20 |
|
SL1923 |
30 |
For bearings with toroidal roller ends, the permissible axial loads are 50% higher ➤ Equation.
Permissible axial load – bearings of TB design
The maximum permissible axial load Fa max ➤ Equation is calculated from the rib strength and 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 possible misalignment between the inner ring and outer ring is influenced by the internal bearing construction, the operating clearance, the forces acting on the bearing 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 values at which, based on experience, there is no significant reduction in operating life are as follows:
Scope of values
The values apply 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.
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:
Lower speed capacity than bearings with cage
Due to the kinematic conditions, however, bearings without cage do not achieve the high speeds that are possible when using bearings with cage.
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 for single row full complement cylindrical roller bearings SGI = Schaeffler Noise Index C0 = basic static load rating |
|
Limiting values
The operating temperature of the bearings is limited by:
Possible operating temperatures of single row cylindrical roller bearings ➤ Table.
|
Operating temperature |
Single row full complement cylindrical roller bearings |
|---|---|
|
|
–30 °C to +120 °C |
In the event of anticipated temperatures which lie outside the stated values, please contact Schaeffler.
Full complement cylindrical roller bearings do not have a cage for guidance and separation of the rolling elements. The cylindrical rollers are guided by the ribs on the bearing rings.
The standard is CN
Single row full complement cylindrical roller bearings are manufactured as standard with the radial internal clearance CN (normal) ➤ Table. CN is not stated in the designation.
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 single row full complement cylindrical roller bearings
|
Nominal |
Radial internal clearance |
||||||||
|---|---|---|---|---|---|---|---|---|---|
|
d |
CN (Group N) |
C3 (Group 3) |
C4 (Group 4) |
C5 (Group 5) |
|||||
|
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 |
220 |
|
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 |
|
315 |
355 |
145 |
225 |
225 |
305 |
305 |
385 |
455 |
535 |
|
355 |
400 |
190 |
280 |
280 |
370 |
370 |
460 |
510 |
600 |
|
400 |
450 |
210 |
310 |
310 |
410 |
410 |
510 |
565 |
665 |
|
450 |
500 |
220 |
330 |
330 |
440 |
440 |
550 |
625 |
735 |
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 of the cylindrical roller bearings 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 |
|
|---|---|---|
|
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 |
|
E |
Increased capacity design |
Standard, dependent on bore code and bearing series; others available by agreement |
|
TB |
Bearing with increased axial load carrying capacity |
Standard, dependent on bore code and bearing series; others available by agreement |
|
XL |
X-life bearing |
Standard, dependent on bore code and bearing series; others available by agreement |
The designation of bearings follows a set model. Example ➤ Figure. The composition of designations is subject to DIN 623-1 ➤ link.
|
Single row full complement cylindrical roller bearing (semi‑locating bearing): 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 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 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, Y | - |
Factors ➤ Table |
Factors e and Y
|
Bearing series |
Calculation factors |
|
|---|---|---|
|
e |
Y |
|
|
SL1818 |
0,2 |
0,6 |
|
SL1923, SL1822, SL1829, SL1830 |
0,3 |
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 ➤ link.
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 |
315 |
400 |
|
|
incl. |
30 |
50 |
80 |
120 |
180 |
250 |
315 |
400 |
500 |
|
|
Values in μm |
||||||||||
|
IT4 |
6 |
7 |
8 |
10 |
12 |
14 |
16 |
18 |
20 |
|
|
IT5 |
9 |
11 |
13 |
15 |
18 |
20 |
23 |
25 |
27 |
|
|
IT6 |
13 |
16 |
19 |
22 |
25 |
29 |
32 |
36 |
40 |
|
|
IT7 |
21 |
25 |
30 |
35 |
40 |
46 |
52 |
57 |
63 |
|
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 d (D) |
Recommended mean roughness value 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 ➤ dimension table 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 ➤ Figure. 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 ➤ 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.
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:
