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Track rollers

Yoke type roller bearing track rollers, stud type roller bearing track rollers

Yoke and stud type roller bearing track rollers:

  • are ready-to-fit needle or cylindrical roller bearings of single or double row design ➤ Figure to ➤ Figure
  • are mounted on shafts or studs (yoke type track rollers) or supplied with a heavy-section roller stud with fixing thread and a mounting aid (stud type track rollers) ➤ Figure
  • have particularly thick-walled outer rings with a crowned outside surface ➤ section
  • can support high radial loads ➤ section
  • tolerate axial loads which are due to small misalignment defects, skewed running or temporary contact running impacts ➤ section
  • are available with or without an inner ring (yoke type track rollers)
  • are produced with or without axial guidance of the outer ring (stud type track rollers are always produced with axial guidance)
  • are open or sealed on both sides ➤ section
  • are not mounted in a housing bore, but are supported on a flat mating track ➤ Figure
  • can be adjusted to the mating track in the design with the eccentric collar, thus permitting, for example, larger manufacturing tolerances in the adjacent construction

Double row stud type track roller supported on a flat mating track


Mating track

Bearing design

Design variants

This range of yoke type track rollers comprises bearings:

  • with or without an inner ring (without axial guidance) ➤ Figure, ➤ Figure
  • with an inner ring (with axial guidance)
Stud type track rollers are available in the following designs:
  • Without eccentric collar
  • With eccentric collar

Yoke type track rollers (general)

The bearings have thick‑walled outer rings and are mounted on shafts or studs

Yoke type track rollers are single or double row units mounted on shafts or studs ➤ Figure to ➤ Figure. They comprise thick-walled outer rings with a profiled outside surface and needle roller and cage assemblies or full complement needle roller or cylindrical roller sets. Yoke type track rollers can support high radial loads as well as axial loads arising from slight misalignment and skewed running. The bearings are available with or without an inner ring, with or without axial guidance and in sealed or open versions.

Typical applications

Proven areas of application of these products include cam gears, bed ways, conveying equipment and linear guidance systems.

Outside surface profile of the outer ring

The outside surface is predominantly crowned

Bearings with a crowned outside surface are predominantly used in practice since skewing usually occurs relative to the mating track and edge stresses must be avoided.

Radius of curvature

The radius of curvature of the outside surface is R = 500 mm. In the case of series NNTR..-2ZL, the radius is indicated in the product table.

Optimised INA profile

Yoke type track rollers NATR..-PP, NATV..-PP, NUTR and PWTR..-2RS have an outside surface with the optimised INA profile ➤ link. In yoke type track rollers with this curvature profile:

X-life premium quality

Series PWTR is supplied as an X-life design. Due to a modified material and the optimised raceway geometry of the outer rings, the basic rating life has been increased by up to 30%. The static and dynamic load carrying capacity has also been increased. At the same time, the stress placed on the mating track has been reduced as a result of the optimised lateral surface profile and its improved surface quality.

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 yoke type track rollers include the suffix XL in the designation.

Yoke type track rollers without inner ring, without axial guidance

The raceway must be designed as a rolling bearing raceway

Yoke type track rollers RSTO and RNA22..-2RSR do not have an inner ring ➤ Figure. Depending on the design, yoke type track rollers are also available as sealed versions ➤ section. They are particularly compact but require a hardened and ground raceway on the shaft or stud. Series RSTO is not self-retaining, which means that the outer ring and the needle roller and cage assembly can be fitted independently of each other. This gives simplified mounting of the bearings.

The rolling elements are guided by the cage. These designs do not have axial guidance of the outer ring. Axial guidance of the outer ring and needle roller and cage assembly (for RSTO only) must be provided in the adjacent construction.

Yoke type track rollers without inner ring, without axial guidance, open or sealed on both sides

Fr = radial load

Fa = axial load


Open (RSTO)


Contact seals (RNA22..-2RSR)

Yoke type track rollers with inner ring, without axial guidance

Yoke type track rollers STO and NA22..-2RSR have an inner ring ➤ Figure. Depending on the design, yoke type track rollers are also available as sealed versions ➤ section. Bearings with an inner ring are used if the shaft or stud does not have a hardened and ground raceway. Series STO is not self-retaining. This means that the outer ring, needle roller and cage assembly and the inner ring can be fitted independently of each other. This gives simplified mounting of the bearings.

The rolling elements are guided by the cage. These designs do not have axial guidance of the outer ring. Axial guidance of the outer ring and needle roller and cage assembly (for STO only) must be provided in the adjacent construction.

Yoke type track rollers with inner ring, without axial guidance, open or sealed on both sides

Fr = radial load

Fa = axial load


Open (STO)


Contact seals (NA22..-2RSR)

Yoke type track rollers with inner ring, with axial guidance

Yoke type track rollers with an inner ring are used if the shaft or stud does not have a hardened and ground raceway.

Designs

The series NATR and NATR..-PP have a cage ➤ Figure. The series NATV and NATV..-PP have a full complement needle roller set, while yoke type track rollers NUTR have a full complement cylindrical roller set ➤ Figure and ➤ Figure. Yoke type track rollers PWTR..-2RS and NNTR..-2ZL have a full complement cylindrical roller set and a central rib ➤ Figure. Depending on the design, yoke type track rollers are also available as sealed versions ➤ section.

Bearings without a cage have the largest possible number of rolling elements and therefore have particularly high load carrying capacity. Due to the kinematic conditions, however, the speeds achievable with these bearings are somewhat lower than those achievable with the cage-guided yoke type track rollers.

Axial guidance of outer ring

The type of guidance is dependent on the series

In NATR and NATV, axial guidance is provided directly by contact washers, while in NATR..-PP and NATV..-PP this is provided by contact washers and plastic axial plain washers. In NUTR, the outer ring is guided by the rolling elements, in PWTR..-2RS and NNTR..-2ZL it is guided by the central rib and the rolling elements.

Corrosion protection

Corrosion protection by Corrotect

Series PWTR..-2RS-RR is protected against corrosion by the special Cr(VI)‑free coating Corrotect ➤ link. These bearings have the suffix RR.

Yoke type track rollers with cage, with axial guidance, open or sealed on both sides

Fr = radial load

Fa = axial load


Gap seals (NATR)


Plastic axial plain washers (NATR..-PP)

Yoke type track rollers with inner ring, full complement needle roller set, with axial guidance, open or sealed on both sides

Fr = radial load

Fa = axial load


Gap seals (NATV)


Plastic axial plain washers (NATV..-PP)

Yoke type track roller with inner ring, full complement cylindrical roller set, with axial guidance, sealed on both sides

Fr = radial load

Fa = axial load


Labyrinth seals (NUTR)

Yoke type track rollers with inner ring, full complement cylindrical roller set, with axial guidance, sealed on both sides

Fr = radial load

Fa = axial load


Protected lip seals (PWTR..-2RS)


Contact washers with lamellar ring (NNTR..-2ZL)

Stud type track rollers (general)

The bearings have thick‑walled outer rings and a heavy-section roller stud

Stud type track rollers are similar in their construction to single and double row yoke type track rollers with axial guidance, except that the raceway is formed by a heavy-section roller stud with a fixing thread and type-dependent mounting aid, and with a type-dependent relubrication facility. Due to the thick-walled outer ring with profiled outside surface and the rolling element set, they can support high radial loads as well as axial loads arising from slight misalignment and skewed running. The stud type track rollers are available with or without an eccentric collar ➤ Figure to ➤ Figure.

Typical applications

Proven areas of application of these products include cam gears, bed ways, conveying equipment and linear guidance systems.

Outside surface profile of the outer ring

The outside surface is crowned

Stud type track rollers with a crowned outside surface are predominantly used since skewing usually occurs relative to the mating track and edge stresses must be avoided.

Radius of curvature

In series KR, the radius of curvature is R = 500 mm. The series KR..-PP, KRE..-PP, KRV..-PP, NUKR, NUKRE, PWKR..-2RS and PWKRE..-2RS have an outside surface with the optimised INA profile.

Optimised INA profile

In stud type track rollers with the optimised INA profile:

X-life premium quality

Stud type track rollers PWKR(E) are supplied in the X-life design. Due to a modified material and the optimised raceway geometry of the outer rings, the basic rating life has been increased by up to 30%. The static and dynamic load carrying capacity has also been increased. At the same time, the stress placed on the mating track has been reduced as a result of the optimised lateral surface profile and its improved surface quality.

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 stud type track rollers include the suffix XL in the designation.

Stud type track rollers without eccentric collar

Stud type track rollers without an eccentric collar do not have a defined adjustment facility in relation to the mating track on the adjacent construction in mounting of the bearings.

Designs

The series KR and KR..-PP have a cage, the design KRV..-PP has a full complement needle roller set. Series NUKR has a full complement cylindrical roller set, series PWKR..-2RS has a full complement cylindrical roller set and a central rib ➤ Figure to ➤ Figure.

Bearings without a cage have the largest possible number of rolling elements and therefore have particularly high load carrying capacity. Due to the kinematic conditions, however, the speeds achievable with these bearings are somewhat lower than those achievable with the cage-guided stud type track rollers.

Axial guidance of outer ring

The type of guidance is dependent on the series

In KR, axial guidance is provided directly by the contact flange and contact washer, while in KR..-PP and KRV..-PP this is provided by plastic axial plain washers, the contact flange and contact washer ➤ Figure and ➤ Figure. The outer rings of series NUKR and PWKR..-2RS are guided by the rolling elements and ribs ➤ Figure and ➤ Figure.

Relubrication facility

Stud type track rollers KR16 and KR19 with a hexagonal socket cannot be lubricated, while stud type track rollers KR16 and KR19 with a mounting slot have a relubrication facility.

Corrosion protection

Corrosion protection by Corrotect

Series PWKR(E)..-2RS-RR is protected against corrosion by the special Cr(VI)-free coating Corrotect ➤ link. These bearings have the suffix RR.

Stud type track roller without eccentric collar, with cage, sealed on both sides

Fr = radial load

Fa = axial load


Plastic axial plain washers (for KR..-PP) or gap seals (for KR)

Stud type track roller without eccentric collar, full complement needle roller set, sealed on both sides

Fr = radial load

Fa = axial load


Plastic axial plain washers (KRV..-PP)

Stud type track roller without eccentric collar, full complement cylindrical roller set, sealed on both sides

Fr = radial load

Fa = axial load


Labyrinth seals (NUKR)

Stud type track roller without eccentric collar, full complement cylindrical roller set, with central rib, sealed on both sides

Fr = radial load

Fa = axial load


Protected lip seals (PWKR..-2RS)

Stud type track rollers with eccentric collar

The bearings have a defined adjustment facility relative to the mating track

Designs with an eccentric collar can be adjusted by means of a hexagonal socket on the flanged or threaded side of the roller stud. The outer ring outside surface can thus be adjusted against the mating track. As a result, larger manufacturing tolerances can be tolerated in the adjacent construction. Furthermore, this gives improved load distribution when using several stud type track rollers and also allows preloaded linear systems to be easily realised.

Highest point of the eccentric collar

The highest point of the eccentric collar is indicated on the roller stud side, the eccentricity e is stated in the product tables. This is also the location of the radial relubrication holes, which should lie in the unloaded zone of the rolling contact.

Designs

Series KRE..-PP has a cage, NUKRE and PWKRE..-2RS have a full complement cylindrical roller set ➤ Figure to ➤ Figure.

Bearings with a full complement cylindrical roller set have the largest possible number of rolling elements and therefore have particularly high load carrying capacity. Due to the kinematic conditions, however, the speeds achievable with these bearings are somewhat lower than those achievable with the cage-guided stud type track rollers.

Axial guidance of outer ring

The type of guidance is dependent on the series

In the series KRE..-PP, axial guidance is provided by the plastic axial plain washers, contact flange and contact washers. In NUKRE, the outer ring is guided axially by the rolling elements, in PWKRE axial guidance of the outer ring is provided by the central rib and rolling elements.

Stud type track roller with eccentric collar, with cage, sealed on both sides

Fr = radial load

Fa = axial load


Plastic axial plain washers (KRE..-PP)

Stud type track roller with eccentric collar, full complement cylindrical roller set, sealed on both sides

Fr = radial load

Fa = axial load


Labyrinth seals (NUKRE)

Stud type track roller with eccentric collar, full complement cylindrical roller set, with central rib, sealed on both sides

Fr = radial load

Fa = axial load


Protected lip seals (PWKRE..‑2RS)

Optimised INA profile

Advantages

The advantages of the optimised INA profile are:

Hertzian pressure curve

Optimised INA profile, profile R = 500, cylindrical profile

The Hertzian pressure curve is more favourable for bearings with an optimised INA profile than for bearings with a cylindrical profile or with a profile where R = 500 mm (load Cr w/Pr = 5) ➤ Figure.

Hertzian pressure curve


Optimised INA profile


Profile R = 500


Cylindrical profile


Untilted running, β = 0 mrad


Tilted running, β = 3 mrad

Maximum Hertzian pressure

Reduced Hertzian pressure with optimised INA profile

The maximum Hertzian pressure is significantly lower for bearings with an optimised INA profile than for bearings with a cylindrical profile or with the profile R = 500 mm ➤ Figure.

Maximum Hertzian pressure, stud type track roller NUKR80, Fr = 13 800 N (Cr w/Pr = 5)

pH = Maximum Hertzian pressure

β = tilt angle


Optimised INA profile


Profile R = 500


Cylindrical profile

Basic rating life of mating track

Longer rating life of mating track

The rating life of the mating track is significantly longer for outer rings with an optimised INA profile than for bearings with the profile R = 500 mm ➤ Figure. Yoke type track rollers NUTR15 ➤ Figure were used as comparative bearings.

Basic rating life of the mating track, track made from 42CrMo4 V, hardness 350 HV

L = basic rating life in millions of overrolling motions

Fr = radial load


Optimised INA profile


Profile R = 500

Wear of the mating track

Reduced wear of the mating track

The mating track wears to a lesser extent with the optimised INA profile ➤ Figure: mating track made from EN-GJS-500-7, mean value derived from several test runs after 360 000 overrolling motions.

Wear of the mating track, track made from EN-GJS-500-7

sw = wear

Fr1 = low radial load

Fr2 = high radial load


Optimised INA profile


Profile R = 500


Mating track made from 58CrV4, mean value derived from several test runs after 800 000 overrolling motions ➤ Figure.

Wear of the mating track, track made from 58CrV4

sw = wear

Fr1 = low radial load

Fr2 = high radial load


Optimised INA profile


Profile R = 500

Rigidity in outer ring contact

Radial deflection

The radial deflection of the outer ring and rolling element set is smaller for bearings with an optimised INA profile than for bearings with the profile R = 500 mm ➤ Figure. Example, yoke type track roller NUTR15.

Rigidity in outer ring contact

δr = radial deflection

Fr = radial load


Optimised INA profile


Profile R = 500


Corrosion protection by Corrotect

A Corrotect coating is often more economical than using corrosion-resistant steels

Track rollers are often subjected to aggressive media. In such applications, corrosion protection is therefore a decisive factor in achieving a long operating life of the bearings. In principle, corrosion-resistant steels may be used here. In many applications, however, the application of a special coating using available Corrotect thin film coating technology is more cost‑effective and should therefore be queried in advance. The series PWTR..‑2RS-RR and PWKR(E)..-2RS-RR are therefore available with a Corrotect coating. These bearings have the suffix RR ➤ section. Other series are also available as a special design with high performance Corrotect systems, which are matched to the specific application.

Before Corrotect-coated units are used, compatibility with the existing media should always be checked.

Corrotect systems

Corrotect coating thicknesses

Corrotect methods are available which permit the application of an extremely thin coating and, as a result, do not need to be included in the bearing tolerance (0,5 μm to 3 μm or 2 μm to 5 μm). Increased demands on corrosion protection can be fulfilled with increasing coating thicknesses or completely different Corrotect methods. In isolated cases, dimensional changes resulting from the coating must be taken into account in a further processing step.

Cr(VI)-free coatings

The current Corrotect systems are all free from Cr(VI), protect effectively against corrosion and, as a result, extend the useful life of the Schaeffler components ➤ Figure.

Further detailed information on the modular coating tool box and on the individual coating systems can be found in Technical Product Information TPI 186 “Higher Performance Capacity through the Use of Coatings”. This publication can be requested from Schaeffler.

Fitting of Corrotect-coated bearings

Take account of larger tolerances

The tolerances are increased by the thickness of the coating. In order to reduce the press-in forces, the surface of the parts should be lightly greased for fitting.

Uncoated and coated stud type track roller in the salt spray test

Load carrying capacity

Suitable for high radial loads

The bearings can support high radial loads as well as axial loads arising from slight misalignment and skewed running.

Installation as yoke or stud type track roller

If used as a yoke and stud type track roller, the outer rings undergo elastic deformation

If the yoke and stud type track rollers are used on a flat mating track, the outer rings undergo elastic deformation. Compared with rolling bearings supported in a housing bore, yoke and stud type track rollers therefore have the following characteristics:

  • modified load distribution in the bearing. This is taken into consid­eration by the effective basic load ratings Cr w and C0r w used in the calculation of the rating life
  • bending stresses and reverse bending strengths in the outer ring. These are taken into consideration by the permissible effective radial loads Fr per and F0r per. The bending stresses and reverse bending strengths must not exceed the permissible strength values of the material

Permissible radial load under dynamic loading

Cr w is valid

For rotating bearings under dynamic load, the effective basic dynamic load rating Cr w is used. Cr w is used to calculate the basic rating life.

The permissible dynamic radial load Fr per must not be exceeded. If a value for Fr per is not given, the effective basic dynamic load rating Cr w is used as a substitute. This basic load rating must not be exceeded by the radial load present. If the basic static load rating C0r w is lower than the basic dynamic load rating Cr w, then C0r w applies.

Permissible radial load under static loading

C0r w is valid

For bearings under static load, either stationary or with only infrequent rotary motion, the effective basic static load rating C0r w applies. C0r w is used to calculate the static load safety factor S0.

The permissible basic static radial load F0r per must not be exceeded. If a value for F0r per is not given, the effective basic static load rating C0r w is used as a substitute. This basic load rating must not be exceeded by the radial load present. In addition to the permissible radial load of the bearing, the permissible radial load of the mating track must also be taken into consideration ➤ link.

Angular misalignment

Skewed running

Additional axial load under skewed running

Skewed running leads to additional axial load on the rolling bearing and axial slippage in the rolling contact between the outer ring and mating track ➤ Figure. Depending on the skewed running angle α and the lubrication, wear can occur in these cases.

A complete loss of adhesive friction between the outer ring and raceway, with correspondingly severe wear, is to be expected with a skewed running angle α ≧ 1,4 · 10-4 · pH (°) or α ≧ 2,5 · 10-3 · pH (mrad).

Skewed running

α = skewed running angle

Tilting

Cylindrical outer ring

If tilting occurs during running, increased edge stresses occur, especially in yoke and stud type track rollers with cylindrical outer rings.

Crowned outer ring

Track rollers with a crowned outer ring are less sensitive to tilting and should therefore be used in preference.

Limits for tilting

In practice, track rollers with a cylindrical outside surface and a tilting angle of β > 0,1° (1,7 mrad) and for yoke and stud type track rollers wth a crowned outside surface and a tilting angle of β > 0,25° (4,4 mrad) have proved susceptible to damage ➤ Figure.

Tilting

β = tilt angle

Lubrication

Two contact zones

Lubricate the rolling elements, rolling element raceway and mating track

Two contact zones must be lubricated and considered separately:

  • the rolling elements and rolling element raceway
  • the outside surface of the track roller and the mating track

The contact zone between the rolling elements and the rolling element raceway is covered in the section Technical Principles, Lubrication.

Lubrication of the bearing

Greased with a lubricating grease to GA08

For yoke and stud type track rollers, a lithium complex soap grease with a mineral oil base and EP additives to GA08 is used. Yoke type track rollers can be lubricated via the inner ring, stud type track rollers have a type-dependent relubrication facility via the roller stud. Greases for initial greasing are listed in the chapter Lubrication ➤ Table. For relubrication, greases in accordance with ➤ Table are suitable.

In stud type track rollers with an eccentric collar, the eccentric collar covers the radial lubrication hole in the shank. Relubrication must therefore be carried out via the end faces.

Arcanol rolling bearing greases for relubrication

Arcanol grease

Designation
to DIN 51825

Type of grease

Track roller

Load150

KP2N–20

Lithium soap grease with mineral oil base

Yoke and stud type roller bearing track rollers

Load220

KP2N–20

Lithium calcium soap grease with mineral oil base

Yoke and stud type roller bearing track rollers

Multi2

KP3K–30

Lithium soap grease with mineral oil base

Yoke and stud type ball bearing track rollers

Lubrication of mating track

Suitable lubricants

For lubrication of the mating track, all lubricants suitable for rolling bearing lubrication may be used. However, there are applications in which the mating track must not be lubricated.

If the contact point cannot be lubricated, wear must be expected, especially under high loads and at high speeds.

Oil lubrication

For oil lubrication, oils of type CLP to DIN 51517 are recommended.

Grease lubrication

For grease lubrication, lithium soap greases to DIN 51825 should be used. Relubrication intervals can only be determined under operating conditions. Relubrication must be carried out at the latest when fretting corrosion first occurs; this can be identified by a reddish discolouration of the mating track or the outer ring.

Solid lubricants and anti‑friction coatings

These substances are also suitable for lubrication. At high traverse or rotational speeds, however, they provide effective lubrication for a significantly shorter period than oil or grease lubrication.

Central lubrication system for stud type track rollers

Connection adapter with rapid-fit connection cartridge

If a central lubrication system is to be used, a patented central lubrication adapter can be used to connect the standard roller stud of stud type track rollers with hexagonal sockets on both sides ➤ Figure. This connector comprises a connection adapter with a hexagonal end and a rapid-fit connection cartridge.

The connection adapter is connected to the roller stud on one end of the stud type track roller by replacing the funnel type lubrication nipple with the fitting cylinder. The hexagonal end prevents rotation of the adapter. The other end of the stud type track roller is closed off using the supplied funnel type lubrication nipple ➤ Figure.

Central lubrication adapter and funnel type lubrication nipple


Connection adapter with M10×1 internal thread


Rapid-fit connection cartridge


Fitting cylinder


Funnel type lubrication nipple


Hard PA pipes should be used in preference

The connection adapter has an M10×1 internal thread. This is used for screw mounting and sealing of the rapid-fit connection cartridge. The cartridge gives firm retention and sealing of the plastic tube. It is therefore not necessary to screw the pipe and adapter onto each other. Hard PA pipes should be used in preference. In this instance, the operating limits according to DIN 73378 and the manufacturer's guidance must be observed. The maximum excess pressure for pipes made from PA11 or PA12 is as follows at +23 °C: 31 bar to 62 bar. The maximum excess pressure when using other screw-in connectors is 80 bar.

Dimensions

For dimensions of the adapters ➤ Table and ➤ Figure.

Dimensions of adapter

Central
lubrication adapter

Dimensions

W

L

l1

l2

l3

For polyamide pipe to DIN 73378

Designation

max.

approx.

d1×snom

AP8 8 27 16 22 4

4×0,75

AP10 10 27 15 22 5

4×0,75

AP14 14 25 8 20 6

4×0,75

Dimensions of central lubrication adapters

Calculation of relubrication intervals

Simplified determination of lubrication impulses

The relubrication quantities for central lubrication using flowable grease and their conversion to the number of relubrication impulses for conventional metering nipple sizes are given in the table ➤ Table. The data are valid for EP additives, for a lithium soap flowable grease with a mineral oil base ISO VG 100 to ISO VG 220 or NLGI 00 or NLGI 000.

Relubrication quantities for stud type track rollers

Series1)

Outside diameter

Central lubrication adapter

Relubri­cation quantity2)

Relubrication impulses
for metering nipple of size

D

Designation

30 mm3

50 mm3

mm

g

from

up to

NUKR, NUKRE

35

40

AP8

1,1

40

24

47

52

AP10

2,4

89

53

62

90

AP14

7,3

271

163

KR, KRE

35

40

AP8

1,2

44

27

47

52

AP10

1,6

60

36

62

90

AP14

6

222

133

KRV, KRVE

35

40

AP8

0,7

26

16

47

52

AP10

1

37

22

62

90

AP14

3,2

120

72

  1. For stud type track rollers with hexagonal socket on both sides.
  2. Relubrication quantity and relubrication intervals for central lubrication using flowable grease for the majority of applications. Note the quantity required to fill the feed lines.

Relubrication periods

Approximate definition

The approximate definition of the relubrication periods for single shift operation and the majority of load applications is shown in ➤ Table and ➤ Table. The data are valid for single shift operation; the relubrication quantity and relubrication intervals are valid for the majority of applications. They are based on approximate calculation of the relubri­cation interval tfR. For definition of the relubrication interval see chapter Relubrication ➤ section. Within these periods, the number of relubrication intervals determined in accordance with ➤ Table should be evenly distributed.

Relubrication period for calculating the relubrication intervals

Load ratio

C0r w/Pr

Maximum operating speed

nmax in % of nD G

10

25

50

100

5 >C0r w/Pr ≧ 3

1/2 yearly

10 >C0r w/Pr ≧ 5

yearly

4 months

monthly

C0r w/Pr ≧ 10

yearly

8 months

2 months

14 days

Periods in single shift operation

Months

Weeks

Working days

Working hours

1/2

2

10

80

1

4

20

160

2

8

40

320

4

16

80

640

6

24

120

960

8

32

160

1 280

12

48

240

1 920


Fitting of central lubrication adapter

Mount the stud type track roller first

The stud type track roller must be mounted before fitting the adapter. The unused relubrication hole in the roller stud must be closed off using the funnel type lubrication nipple supplied. Only the lubrication nipples supplied should be used.

Guidelines for mounting of the adapter

The central lubrication adapter should preferably be pressed in using a manual lever press under low, uniform pressure or carefully driven into the unused hexagonal socket of the roller stud by means of light blows with a plastic hammer; pay attention to the press-in depth l3 and the position of the hexagon ➤ Figure and ➤ Table.

Fitting of the polyamide pipe

The plastic pipe must be cut off straight across and inserted into the cartridge until it stops. Only polyamide pipes to DIN 73378 should be used. Check the seating of the pipe. Note maximum pressures, maximum temperatures and minimum bending radius. The maximum pipe length up to the distributor is 1 m.

Sealing

Yoke type track rollers

Available in open or sealed designs

Yoke type track rollers are available in open designs and with non-contact or contact type seals ➤ Table.

Seals used in yoke type track rollers

Yoke type track roller

Seal

STO

Open

RSTO

Open

RNA22..-2RSR

Lip seal on both sides

NA22..-2RSR

Lip seal on both sides

PWTR..-2RS

Protected lip seal on both sides

continued ▼

Seals used in yoke type track rollers

Yoke type track roller

Seal

NATR..-PP

Three-stage sealing by plastic axial plain washers

NATV..-PP

Three-stage sealing by plastic axial plain washers

NATR

Gap seal on both sides

NATV

Gap seal on both sides

NUTR

Labyrinth seal on both sides

NNTR..-2ZL

Contact washer with lamellar ring on both sides

continued ▲

Stud type track rollers

Available with seals on both sides

Stud type track rollers are sealed on both sides. Depending on the series, non-contact or contact types seals are used. A three-stage seal, comprising plastic axial plain washers with formed seal lips on both sides of the bearings, is also used ➤ Table.

Seals used in stud type track rollers

Stud type track roller

Seal

KR

Gap seal on both sides

KR..-PP

Three-stage sealing by plastic axial plain washers

KRE..-PP

Three-stage sealing by plastic axial plain washers

KRV..-PP

Three-stage sealing by plastic axial plain washers

NUKR

Labyrinth seal on both sides

NUKRE

Labyrinth seal on both sides

PWKR..-2RS

Protected lip seal on both sides

PWKRE..-2RS

Protected lip seal on both sides

Three-stage seal

Seal design

In the three-stage concept, there is a gap seal between the plastic axial plain washer and the outer ring, as well as a labyrinth seal between the formed seal lip and an undercut in the outer ring. The disc spring shape of the axial plain washer gives a preloaded contact seal as the third stage. It also provides axial sliding contact between the outer ring and contact washers, thus reducing wear and grease consumption.

Speeds

Speeds nD G

The maximum possible speed is essentially determined by the permissible operating temperature of the yoke and stud type track rollers. The temperature thus depends on the type of bearing, the load, the lubrication conditions and the cooling conditions.

Speeds with lip seals

The speed of track rollers with lip seals is additionally restricted by the permissible sliding speed at the seal lip.

Speed during continuous operation

Criteria for guide values

The speeds nD G in the product tables are guide values. They were determined for:

  • grease lubrication
  • loads during continuous operation of < 0,05 · C0r w
  • skewed running angles of α < 0,03° (< 0,5 mrad)
  • an ambient temperature of +20 °C
  • outer ring temperatures of +70 °C
  • lubricated mating tracks
  • no external axial load

Reducing the speed

The speeds must be reduced under the following conditions:

  • loads > 0,05 · C0r w
  • additional axial forces (skewed running)
  • insufficient heat dissipation

Higher speeds

Higher speeds can be achieved with intermittent operation and oil impulse lubrication.

Noise

Schaeffler Noise Index

The Schaeffler Noise Index (SGI) is not yet available for this bearing type ➤ link. The data for these bearing series will be introduced and updated in stages.

Temperature range

Limiting values

The operating temperature of the yoke and stud type track rollers is limited by:

  • the dimensional stability of the bearing rings and rolling elements
  • the cage
  • the lubricant
  • the seals

Permissible temperature ranges

Operating tempera­ture

Yoke and stud type track rollers

Open or with
gap seal or labyrinth seal

With
lip seal

With
plastic cage

With
three-stage seal

2RS, 2RSR

TV

PP

from

to

from

to

from

to

from

to

°C

–30

+140

–30

+120

–30

+120

–30

+100

Note the information on the operating temperature range in Technical Principles, Lubrication.

In the event of anticipated temperatures which lie outside the stated values, please contact Schaeffler.

Cages

Yoke type track rollers

Yoke type track rollers without inner ring

With cage

Yoke type track rollers RSTO and RNA22..-2RSR have a sheet steel cage as standard. Yoke type track rollers RSTO up to D = 24 mm have a plastic cage made from polyamide PA66 (suffix TV). Series RSTO does not have axial guidance of the needle roller and cage assembly and of the outer ring. As a result, lateral guidance is required.

Yoke type track rollers with inner ring

With cage, with full comp­lement needle roller or cylindrical roller set

The series STO, NA22..-2RSR, NATR and NATR..-PP have a sheet steel cage as standard. Yoke type track rollers STO up to D = 24 mm have a plastic cage made from polyamide PA66 (suffix TV). The series NATV and NATV..-PP have a full complement needle roller set, while yoke type track rollers NUTR, PWTR..-2RS and NNTR..-2ZL have a full complement cylindrical roller set. Series STO does not have axial guidance of the needle roller and cage assembly and of the outer ring. As a result, lateral guidance is required.

Stud type track rollers

Stud type track rollers without eccentric collar

With cage, with full comp­lement needle roller or cylindrical roller set

Stud type track rollers KR and KR..-PP have a sheet steel cage, the design KRV..-PP has a full complement needle roller set. The series NUKR and PWKR..-2RS have a full complement cylindrical roller set.

Axial guidance of outer ring

In KR, axial guidance is provided directly by the contact flange and contact washer, while in KR..-PP and KRV..-PP this is provided by plastic axial plain washers, the contact flange and contact washer. In NUKR, the outer ring is guided axially by the rolling elements, in PWKR, axial guidance of the outer ring is provided by the central rib and rolling elements.

Stud type track rollers with eccentric collar

With cage or full comp­lement cylindrical roller set

Series KRE..-PP has a sheet steel cage, NUKRE and PWKRE..-2RS have a full complement cylindrical roller set.

Axial guidance of outer ring

In KRE..-PP, axial guidance is provided by the plastic axial plain washers, contact flange and contact washer. In NUKRE, the outer ring is guided axially by the rolling elements, in PWKRE, axial guidance of the outer ring is provided by the central rib and rolling elements.

Internal clearance

Radial internal clearance

Standard corresponds approximately to C2 or CN

The radial internal bearing clearance of yoke and stud type track rollers corresponds approximately to tolerance class C2 (Group 2) and, in the case of STO and NA22..-2RSR, to tolerance class CN (Group N). Values ➤ Table.

The values for radial internal clearance correspond to DIN 620-4:2004 (ISO 5753-1:2009). These are valid for bearings which are free from load and measurement forces (without elastic deformation).

Radial internal clearance for yoke and stud type track rollers

Nominal
bore diameter

Radial internal clearance

d

C2
(Group 2)

CN
(Group N)

C3
(Group 3)

C4
(Group 4)

mm

μm

μm

μm

μm

over

incl.

min.

max.

min.

max.

min.

max.

min.

max.

24

0

25

20

45

35

60

50

75

24

30

0

25

20

45

35

60

50

75

30

40

5

30

25

50

45

70

60

85

40

50

5

35

30

60

50

80

70

100

50

65

10

40

40

70

60

90

80

110

65

80

10

45

40

75

65

100

90

125

80

100

15

50

50

85

75

110

105

140

100

120

15

55

50

90

85

125

125

165

120

140

15

60

60

105

100

145

145

190

Dimensions, tolerances

Tolerances

The dimensional and running tolerances correspond to the tolerance class Normal in accordance with ISO 492, for KR, KRE and KRV to ISO 7063.

Deviations from ISO 492

The following deviations from ISO 492 apply:

  • the diameter deviations of the profiled outside surface 0/–0,05 mm
  • for NNTR, the diameter tolerance class h10
  • for NATR, NATV, NUTR, PWTR..-2RS, the tolerance class h12 for width B
  • for NATR, NATV, the roundness of the inner ring
  • for stud type track rollers, the tolerance class of the shank diameter h7 and the eccentric collar diameter h9

Tolerances for Corrotect-coated bearings

For PWTR..-2RS-RR and PWKR..-2RS-RR , the tolerances are increased by the thickness of the Corrotect special coating.

Enveloping circle

Yoke type track rollers without inner ring

For yoke type track rollers without an inner ring, RSTO and RNA22..-2RSR, the needle enveloping circle Fw is in the tolerance class F6. The enveloping circle is the inner inscribed circle of the needle rollers in clearance-free contact with the adjacent construction.

Suffixes

For a description of the suffixes used in this chapter ➤ Table and medias interchange http://www.schaeffler.de/std/1B69.

Suffixes and corresponding descriptions

Suffix

Description of suffix

PP

Plastic axial plain washer with formed seal lip on both sides of the bearing, giving a three-stage seal

Standard

RR

Protected against corrosion by Corrotect special coating in the case of PWTR..-2RS and PWKR(E)..-2RS

Standard

SK

Hexagonal socket only on the flange-side end face, no relubrication facility

Standard

TV

Plastic cage

Standard

XL

X-life design

Standard

2RS

Protected lip seal on both sides

Standard

2RSR

Radial contact lip seal on both sides

Standard

2ZL

Contact washer with lamellar ring on both sides

Standard

Structure of bearing designation

Examples of composition of bearing designation

The designation of bearings follows a set model. Examples ➤ Figure to ➤ Figure.

Yoke type track roller, single row, without inner ring, without seal, without axial guidance, open design, plastic cage, R = 500: designation structure

Yoke type track roller, double row, with inner ring, sealed, optimised INA profile: designation structure

Needle roller stud type track roller, full complement needle roller set, with axial guidance, three-stage seal, optimised INA profile: designation structure

Cylindrical roller stud type track roller, full complement needle roller set, with axial guidance, X-life design, optimised INA profile: designation structure

Dimensioning

Calculation of the rating life

The methods for calculating the rating life are:

  • the basic rating life to DIN ISO 281
  • the adjusted basic rating life to DIN ISO 281
  • the expanded calculation of the adjusted reference rating life to DIN ISO 281-4

Use effective basic dynamic/static load ratings

These methods are described in the chapter Load carrying capacity and life. For yoke and stud type track rollers, use the following values (values ➤ link):

  • for Cr, the effective basic dynamic load rating Cr w
  • for C0r, the effective basic static load rating C0r w
  • for Cur, the effective fatigue limit load Cur w

Other rating life equations

Other equations for calculating the rating life ➤ Equation, ➤ Equation and ➤ Equation.

Basic rating life

Basic rating life in oscillating operation

Basic rating life

Legend

Ls 105 m

Basic rating life in 105 m

Lh h

Basic rating life in operating hours

Cr w N

Effective basic dynamic load rating. Cr w is that load of constant magnitude and direction which a sufficiently large group of apparently identical track rollers can endure for a basic rating life of one million revolutions

Pr N

Equivalent dynamic bearing load (radial load)

p -

Life exponent:
p = 3 for yoke or stud type track rollers based on balls
p = 10/3 for yoke and stud type track rollers based on needle or cylindrical rollers

n min–1

Operating speed

D mm

Outside diameter of track roller

H m

Single stroke length for oscillating motion

nosc min–1

Number of return strokes per minute

m/min

Mean travel velocity

Operating life

Life actually achieved

The operating life is defined as the life actually achieved by a yoke type track roller, stud type track roller or ball bearing track roller. This can deviate significantly from the calculated basic rating life.

Cause of deviations

Possible causes of a deviation between the basic rating life and the operating life are wear or fatigue as a result of:

  • deviations in the operating data
  • misalignment between the track roller and mating track
  • insufficient or excessive operating clearance
  • contamination of the track roller
  • inadequate lubrication
  • excessive operating temperature
  • oscillating bearing motion with very small swivel angles, leading to false brinelling
  • wear between the outer ring outside surface and mating track
  • high vibration and false brinelling
  • very high shock loads, static overloading
  • prior damage during mounting

Due to the variety of mounting and operating conditions, the operating life cannot be precisely calculated in advance. The most reliable way of arriving at a close estimate is by comparison with similar applications.

Static load safety factor

S0 = C0r w/F0r

In addition to the basic rating life L, it is also always necessary to check the static load safety factor S0 ➤ Equation.

Static load safety factor

Legend

S0 -

Static load safety factor

C0r w N

Effective radial basic static load rating in accordance with product table

F0r N

Maximum static radial load on track roller

Track rollers are regarded as heavily loaded at a static load safety factor of S0 < 8. Static load safety factors of S0 < 1 cause plastic deformation of the rolling elements and the raceways, which can impair smooth running. This is only permissible for bearings with small rotary motions or in secondary applications.

If an application has a static load safety factor of S0 < 2, please consult Schaeffler.

Frictional torque

Calculation only possible in approximate terms

The frictional torque MR of a yoke type, stud type or ball bearing track roller depends on many influencing factors such as load, speed and type, as well as the lubrication conditions and seal friction. Due to the wide range of these influencing factors, the frictional torque can only be calculated approximately.

For designs without contact seals, the frictional torque can be calculated under normal operating conditions and moderate speed range in accordance with ➤ Equation.

Frictional torque

Legend

MR Nmm

Frictional torque of track roller

f -

Coefficient of friction ➤ Table and ➤ Table

Fr N

Radial load

dM mm

Mean bearing diameter of track roller (d + D)/2


Coefficient of friction for yoke and stud type track rollers

Type

Coefficient of friction

f

Cylindrical roller bearing, full complement

0,002

to 0,003

Needle roller bearing, with cage

0,003

to 0,004

Needle roller bearing, full complement

0,005

to 0,007


Coefficient of friction for track rollers

Type

Coefficient of friction

f

Ball bearing, single row

0,0015

to 0,002

Ball bearing, double row

0,002

to 0,003


Validity of coefficients of friction

The stated factors f are valid for yoke type, stud type and ball bearing track rollers, which are unsealed or have a contact seal and are subjected to radial load. If sealed designs are used, higher coefficients of friction must be expected.

Influence of additional axial forces

Additional axial forces, such as those occurring under large skewed running angles, can lead to a substantial increase in the values, especially in the case of track rollers based on needle rollers. Track rollers based on ball bearings can support axial loads without a significant change in friction.

Displacement resistance

When an outer ring rolls on a track, it must overcome not only the friction within the bearing but also the rolling friction between the outer ring and the mating track. The displacement resistance is determined from the rolling friction and the frictional torque MR in accordance with ➤ Equation.

Displacement resistance

Legend

Fv N

Displacement resistance

fR mm

Coefficient of rolling friction for tracks made from hardened steel:
fR = 0,05 mm

Fr N

Radial load

MR Nmm

Frictional torque

D mm

Outside diameter of track roller

Minimum load

Minimum load C0r w/Fr < 60

In order to ensure that the outer ring is driven, that no slippage occurs and that the track roller does not lift from the mating track, the track roller must be subjected to a minimum load in dynamic operation. In general, the minimum load is calculated using the ratio C0r w/Fr < 60.

Design of bearing arrangements

Adjacent construction for yoke type track rollers

Yoke type track rollers without inner ring, raceway design

For yoke type track rollers without an inner ring, the rolling element raceway on the shaft or stud must be hardened and ground ➤ Table. The surface hardness must be 670 HV to 840 HV, the hardening depths CHD or SHD must be sufficiently large.

Tolerances and surface design

Diameter tolerance of shafts or studs

Roughness

Roundness tolerance

Parallelism tolerance

Without inner ring

With inner ring

max.

max.

k5 Ⓔ

g6 Ⓔ
(with point load)

Ramax 0,4 (Rzmax 2)

25% of diameter tolerance

50% of diameter tolerance

Location of yoke type track rollers without axial guidance

For yoke type track rollers without axial guidance, the outer ring and needle roller and cage assembly must be laterally guided ➤ Figure. The axial contact surfaces for the outer rings must be precision machined (Ramax 2 recommended), wear-resistant and lubricated.

Bearing parts must not be interchanged with parts from other bearings during fitting

Yoke type track rollers without axial guidance are not self-retaining. The outer ring and the needle roller and cage assembly are matched to each other and must not be interchanged during mounting with components from other bearings of the same size. The inner rings are matched to the enveloping circle class F6 and can be interchanged within their accuracy class (used in different combinations).

Lateral guidance of outer ring and needle roller and cage assembly


RSTO

Location of yoke type track rollers with axial guidance

Observe dimension d2

Yoke type track rollers with axial guidance must be axially clamped in place. The thrust washers must be axially supported if axial loads occur. The dimension d2 in the product tables must be observed ➤ Figure.

Location by snap ring

Yoke type track rollers NATR and NATV can be located using conventional fasteners such as snap rings ➤ Figure.

Location by snap ring

d2 = abutment diameter


NATR


Snap ring


Firmly locate inner ring and thrust ring axially

For yoke type track rollers NNTR..-2ZL, NUTR and PWTR..-2RS, the inner ring and thrust ring must be located axially ➤ Figure.

Clamping of inner ring and thrust washer


PWTR..-2RS

Adjacent construction for stud type track rollers

Bore tolerance H7

The bore tolerance H7 produces a clearance fit since the stud tolerance is h7 for studs without eccentric collar and h9 for studs with eccentric collar.

Design of locating surfaces

The locating surfaces for stud type track rollers must be flat, perpendicular and of sufficient height. The strength of the nut locating surface must be sufficiently high. The dimension must not be less than the dimension d2 in the product tables.

Lead chamfer

The lead chamfer on the locating bore must not be more than 0,5×45°.

Axial location

Stud type track rollers must be axially secured using a hexagon nut. The nuts of grade 8 to ISO 4032 (M6, M8), ISO 8673, are not included in the delivery and must be ordered separately.

If heavy vibration occurs, the stud type track rollers can be located using self-locking nuts in accordance with DIN 985 or special locking washers.

For self-locking nuts, a higher tightening torque must be observed; the advice given by the nut manufacturer must be followed.

Position of lubrication hole

Ensure that the lubrication hole is positioned correctly

The position of the radial lubrication hole is indicated on the flanged side of the roller stud ➤ Figure. This must not be positioned in the loaded zone.

Position of lubrication hole


NUKR


Marking (position of radial lubrication hole)

Design of mating track

Take account of Hertzian pressure

In the design of the mating track (material and strength, heat treatment, surface), the Hertzian pressure pH must be taken into consideration. This is dependent on the load, the contact geometry (point contact or line contact) and the modulus of elasticity of the materials.

Nomogram for determining the Hertzian pressure

The Hertzian pressure can be read from the nomogram and calculated ➤ Figure. The nomogram is valid for mating tracks made from steel. For other materials, the correction factor k must be taken into consideration ➤ Table.

Additional conditions

Other conditions:

  • point contact
  • radius of curvature R = 500. For radii R > 500 and the optimised INA profile, correction values must be calculated ➤ Equation
  • mating track flat in the direction of the track roller axis
  • signs according to ➤ Figure

Raceway radii and signs

D = outside diameter of track roller

rL = raceway radius

Example

NUKR35

  • stud type track roller NUKR35 with optimised INA profile
  • D = 35 mm
  • outer ring width C = 18 mm
  • radial load Fr = 2  500 N
  • cam plate, radius rL = 80 mm

Curvature sum

Calculating the curvature sum

The curvature sum is calculated from the raceway radius rL and the diameter D of the track roller ➤ Equation.

Curvature sum



PH500 = 1 250 N/mm2


Hertzian pressure

= 1 250 N/mm2 · 0,85
= 1 063 N/mm2
(1 025 N/mm2 from calculation program BEARINX, kpH ➤ Table)

Nomogram for determining Hertzian pressure, calculation example (purple)


Track rollers with optimised INA profile

For an outer ring with the optimised INA profile, the following calculation provides sufficiently precise values ➤ Equation and ➤ Table.

Optimised INA profile

Pressure factor kpH

Outer ring width

Pressure factor

C

kpH

mm

10 ≦ C ≦ 15

1

15 < C ≦ 20

0,85

20 < C ≦ 30

0,83

30 < C ≦ 35

0,8

Radius of curvature R > 500 mm

If the outer ring has a radius of curvature of R > 500 mm, ➤ Equation.

R > 500 mm

Materials for mating track

High load on the mating track

The mating track is subjected to high load during overrolling. This produces high Hertzian contact pressures. The strength and surface hardness of the material must be matched to this load.

Correction factors

For raceways subjected to high loads, through hardened steels, case hardened steels and steels for flame or induction hardening are recommended. For raceways subjected to low loads, construction steels and cast steel or cast iron materials can be used ➤ Equation ➤ Table.

Correction for mating track material


Correction factor k

Material

Material no.

Correction factor for mating track with

k

for point contact

for line contact

EN-GJL-200

0.6020

0,74

0,8

EN-GJL-300

0.6030

0,81

0,85

GG-40

0,85

0,88

EN-GJS-400-15

0.7040

0,92

0,94

EN-GJS-600-3

0.7060

0,94

0,96

EN-GJS-800-2

0.7080

0,96

0,97

Guide values for permissible Hertzian pressure

Selection by material

The table ➤ Table gives a selection of materials with the associated values. The values were determined on steel test specimens; loadings of 107 were achieved.

On a similar basis to the calculation of the load carrying capacity of rolling bearings, this gives:

  • pH stat for predominantly static load
  • pH dyn for predominantly dynamic load

Materials and guide values for permissible Hertzian pressure (selection)

Material

Material designation

Material no.

Hertzian pressure

Proof stress of material

new

old:

pH stat

pH dyn

Rp0,2

N/mm2

N/mm2

N/mm2

Flake graphite cast iron

EN-GJL-150

GG-15

EN-JL1020

0.6015

850

340

120

EN-GJL-200

GG-20

EN-JL1030

0.6020

1 050

420

150

EN-GJL-250

GG-25

EN-JL1040

0.6025

1 200

480

190

EN-GJL-300

GG-30

EN-JL1050

0.6030

1 350

540

220

EN-GJL-350

GG-35

EN-JL1060

0.6035

1 450

580

250

GG-40 1 500 600 280
Spheroidal graphite cast iron

EN-GJS-400-15

GGG-40

EN-JS1030

0.7040

1 000

490

250

EN-GJS-500-7

GGG-50

EN-JS1050

0.7050

1 150

560

320

EN-GJS-600-3

GGG-60

EN-JS1060

0.7060

1 400

680

380

EN-GJS-700-2

GGG-70

EN-JS1070

0.7070

1 550

750

440

EN-GJS-800-2

GGG-80

EN-JS1080

0.7080

1 650

800

500

Cast steel

GE200

GS-38

1.0420

780

380

200

GE240

GS-45

1.0446

920

450

230

GS-52

1.0552

1 050

510

260

GE300 GS-60 1.0558 1 250 600 300
GS-62 1 300 630 350
GS-70 1 450 700 420
Construction steel

S235JR

St 37-2

1.0037

690

340

235

S275JR

St 44-2

1.0044

860

420

275

S355J2G3+N

St 52-3

1.0570

980

480

355

Quenched and tempered steel

C45 V

1.0503

1 400

670

500

Cf53 V

1.1213

1 450

710

520

Cf56 V 1 550 760 550

C60 V

1.0601

1 600

780

580

46Cr2 V

1.7006

1 750

850

650

42CrMo4 V

1.7225

2 000

980

900

50CrV4 V

1.8159

2 000

980

900

Hardened steel and with tempering at low temperatures

100Cr6 H

1.3505

4 000

1 500

1900

16MnCr51)

1.7131

4 000

1 500

7703)

Cf532)

1.1213

4 000

1 500

7303)

Cf562)

4 000

1 500

7603)

  1. Case hardened.
  2. Induction surface layer hardening.
  3. Proof stress of the core.

Hardenable materials

Suitable steels

The following materials with a purity level corresponding to that of alloyed construction steels may be used:

  • through hardening steels to ISO 683-17, such as 100Cr6. In special cases, surface hardening is possible
  • case hardening steels to ISO 683-17 such as 17MnCr5, or in accordance with EN 10084, such as 16MnCr5. Both the hardenability and the core strength must be taken into consideration. For case hardening, a fine grained hardening structure and a case hardening depth CHD in accordance with ➤ Equation is necessary
  • steels for flame or induction hardening to ISO 683-17, such as C56E2, or to DIN 17212, such as Cf53. For flame or induction hardening, only the parts of the machine component used as raceways must be hardened. The material should be quenched and tempered before hardening. The surface hardening depth SHD is determined in accordance with ➤ Equation

Heat treatment of the mating track

Specifications for heat treatment

The following apply for hardened mating tracks:

  • a surface hardness of 670 HV to 840 HV
  • CHD and SHD according to ➤ Equation and ➤ Equation – in accordance with DIN 50190, the depth of the hardened surface zone at which there is still a hardness of 550 HV
  • hardness curves according to ➤ Figure and ➤ Figure
  • a hardening depth of ≧ 0,3 mm

The equations are based on the hardness curves normally achieved with skilled heat treatment.

Case hardening

Case hardening depth

Flame and induction hardening

Surface hardening depth

Legend

pH N/mm2

Max. Hertzian pressure

CHD mm

Case hardening depth

SHD mm

Surface hardening depth

D mm

Outside diameter of track roller

Rp0,2 N/mm2

Proof stress of mating track material ➤ Table

rL mm

Radius of mating track – the raceway must be flat in the direction of the yoke type track roller axis ➤ Figure

Case hardening depth CHD, hardness curve

CHD = case hardening depth with hardness 550 HV

HV = hardness

z = distance from surface


Required hardness


Case hardening

Surface hardening depth SHD, hardness curve

SHD = surface hardening depth

HV = hardness

z = distance from surface


Required hardness


Flame or induction hardening

Schaeffler guideways as mating tracks

Ready-to-fit units

The Schaeffler guideways are ready-to-fit units from the Schaeffler linear range. They are to the appropriate grade Q20 for yoke and stud type track rollers and correspond to the dimensions of standard profiles:

  • parallelism 20 μm/m
  • surface quality Ramax 0,8
  • hardness 58 HRC to 62 HRC
  • angular misalignment between the raceways max. 1 mrad (1 μm/mm)
  • deviations of the guideway cross-section +0,05/+0,015
  • length tolerance of the individual guideway +1/0 mm/m

Protection of mating track

The mating track must be protected against contamination. Where necessary, covers and wipers, for instance made from felt, should be placed ahead of the track roller ➤ Figure.

Protection of mating track against contamination


Covers

Mounting and dismounting

Mounting

Track rollers must be handled with care before and during assembly. Their trouble-free operation depends largely on the care taken during mounting.

Guidelines for mounting

The products must be protected against dust, contaminants and moisture. Contaminants have a detrimental influence on the running and operating life of rolling bearings.

Do not cool the bearings excessively. Moisture due to condensation can lead to corrosion in the bearings and bearing seats.

Yoke type track rollers RSTO and STO are not self-retaining. The outer ring and the needle roller and cage assembly are matched to each other and must not be interchanged during mounting with components from other bearings of the same size.

The assembly area must be kept clean and free from dust.

Check the seat of the axis for dimensional and geometrical accuracy and cleanliness.

The seating surfaces of the bearing rings must be lightly oiled or rubbed with solid lubricant.

After mounting, the bearings must be supplied with lubricant. Finally, the correct functioning of the bearing arrangement must be checked.

Mounting tools

Depending on the application, the following are suitable:

  • induction heaters; note the manufacturer’s guidance on grease and seals
  • heating cupboard; heating up to +80 °C
  • mechanical or hydraulic presses; use mounting sleeves that cover the whole circumference of the bearing ring end faces
  • hammer and mounting sleeves; blows should only be applied concentrically to the sleeve

Mounting forces must never be directed through the rolling elements. Avoid direct blows on the bearing rings in all cases. Ensure that the seals are not damaged.

Guidelines for dismounting

Mounting should be taken into consideration in the original design of the bearing position. If the bearing is to be reused:

  • avoid direct blows on the bearing rings
  • dismounting forces should not be applied through the rolling elements
  • carefully clean the bearings after dismounting
  • do not use a concentrated or “hard” flame

Mounting and dismounting of yoke type track rollers (needle and cylindrical roller types)

Use a mounting press

If the tolerances are unfavourable, the yoke type track roller should be pressed onto the shaft or stud using a mounting press ➤ Figure. The inner ring must be mounted such that the pressing-in force is distributed uniformly over the end face of the inner ring.

Lubrication hole

The bearings must be mounted such that the lubrication hole is positioned in the unloaded zone. For yoke type track rollers PWTR and NNTR, defined positioning of the lubrication hole is not required.

Mounting of yoke type track roller using a mounting press

NUTR


Mounting press


Axial location

Yoke type track rollers NUTR, PWTR and NNTR must be axially clamped in place ➤ Figure.

Axial location

PWTR..-2RS


Hexagon nut

Mounting and dismounting of stud type track rollers (needle and cylindrical roller types)

Use a mounting press

Stud type track rollers should be mounted using a mounting press if possible ➤ Figure.

Blows on the flange of the roller stud must be avoided. The position of the lubrication hole is indicated on the flanged side of the roller stud. It must not be positioned in the loaded zone ➤ Figure.

Drive fit lubrication nipples for stud type track rollers

Fit the lubrication nipples before mounting the bearings

Stud type track rollers are supplied with loose drive fit lubrication nipples that must be pressed in correctly before mounting of the bearings ➤ Figure. For lubrication of stud type track rollers using the central lubrication adapter ➤ Figure.

Only the lubrication nipples supplied may be used ➤ Table. If relubrication is to be carried out via the locating bore, the axial lubrication holes in the stud type track roller must be closed off using the lubrication nipples before mounting ➤ Figure.

Stud type track roller with drive fit lubrication nipple and dimensions for pressing mandrel

KR..-PP


Drive fit lubrication nipples

Lubrication nipple

Dimensions

Suitable for outside diameter

D

D

d

L

h

dS

LS

±0,1

mm

mm

mm

mm

mm

mm

NIPA1

6

4

6

1,51)

16 and

19

NIPA1×4,5

4,7

4

4,5

1

4,5

5

22 to

32

NIPA2×7,5

7,5

6

7,5

2

7,5

6

35 to

52

NIPA3×9,5

9,5

8

9,5

3

10

9

62 to

90

  1. Projection of lubrication nipple, see product tables

Axial location of stud type track rollers

Secure bearings axially

Stud type track rollers must be axially secured using a hexagon nut. The slot or hexagonal socket on the end of the roller stud can be used to hold the bearing by means of a key while tightening the fixing nut and to adjust the eccentric collar ➤ Figure. If heavy vibration occurs, self-locking nuts to DIN 985 or special locking washers can be used.

The tightening torque for the fixing nuts stated in the product tables must be observed. It is only in this way that the permissible radial load can be ensured. If this cannot be adhered to, an interference fit is required. For self-locking nuts, a higher tightening torque must be observed; the advice given by the nut manufacturer must be followed.

Holding the bearing using an Allen key


Allen key

Stud type track rollers with eccentric collar

Highest point on the eccentric collar

The highest point on the eccentric collar is indicated on the roller stud side, which also gives the position of the radial lubrication hole.

Commissioning and relubrication

Position of the relubrication holes

Stud type track rollers have a lubrication hole for relubrication:

  • on the flange side of the roller stud
  • on the thread-side end face for outside diameters from 22 mm
  • on the shank of the roller stud, for outside diameters from 30 mm with an additional lubrication groove

Stud type track rollers with an eccentric collar cannot be relubricated via the stud. The eccentric collar covers the lubrication hole.

For lubrication, only grease guns with needle point nozzles may be used that have an opening angle ≦ 60° ➤ Figure.

Before commissioning, the lubrication holes and feed pipes must be filled with grease in order to ensure protection against corrosion; lubrication can be carried out at the same time.

Lubrication will be more difficult if a rolling element is located over the radial lubrication hole. Relubrication should therefore be carried out with the bearing still warm from operation and rotating if safe to do so, before the bearing comes to rest if safe to do so and before extended breaks in operation.

The grease used for relubrication should be the same as that used for initial greasing. If this is not possible, the miscibility and compatibility of the greases must be checked. Relubrication should continue until a fresh collar of grease appears at the seal gaps. The old grease must be able to leave the bearing unhindered.

Relubrication using a grease gun


Needle-point nozzle, opening angle ≦ 60°

Schaeffler Mounting Handbook

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.

Legal notice regarding data freshness

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.

Further information

In addition to the data in this chapter, the following chapters in Technical principles must also be observed in the design of bearing arrangements: