EP1725782A1

EP1725782A1 - Pin-cage for a twin-row self-aligning roller bearing

Info

Publication number: EP1725782A1
Application number: EP05715090A
Authority: EP
Inventors: Rainer Schröder; Martin Grehn
Original assignee: Schaeffler KG
Current assignee: IHO Holding GmbH and Co KG
Priority date: 2004-03-19
Filing date: 2005-03-18
Publication date: 2006-11-29
Also published as: WO2005090804A1; DE102004013542A1; JP2007529702A; US20070189652A1

Abstract

The invention relates to a pin-cage (12), for a twin-row self-aligning roller bearing (1), essentially comprising an inner ring (2), an outer ring (3) and several rollers (10), running adjacently between the above, in two rows (4, 5) on the running tracks (6, 7, 8, 9) of the inner ring (2) and the outer ring (3). A pin cage (12) is arranged between the roller rows (4, 5) embodied with pins (11) on the axial faces thereof at even spaces with a stepped offset. The rollers (10) of both roller rows (4, 5) each comprise an axial through drilling (13), by means of which the above are rotatably mounted on the pins (11) of the pin-cage (12). According to the invention, the pin-cage (12) is embodied as a pre-assembled component without a lateral disc made up of a one-piece closed annular disc (14) and pins (11) freely extending axially from the above, the length of which is less than the length of the through drillings (13) in the rollers (10), whereby lubrication of the rollers (10) is achieved by centrifugal force from the free front face (15) thereof through the outer opening (16) of the through drilling (13) thereof.

Description

Name of the invention

Bolt cage for a double row spherical roller bearing

description

Field of the invention

The invention relates to a pin cage for a double row spherical roller bearing according to the preamble forming features of claim 1.

Background of the invention

From DE 28 363 09 A1 discloses a generic type of cage for a double-row spherical roller bearing is known, which consists essentially of an inner bearing ring and an outer bearing ring and a plurality of these running in two rows next to each other on their careers roles. Between these two rows of rollers formed at its axial sides with equally spaced and staggered to each other fastened bolts bolt pin cage is arranged, wherein the roles of both rows of rollers each have an axial through hole through which they are rotatably mounted on a respective bolt of the pin cage. The pin cage consists in concrete execution of a right and a left inner ring, which are separated by a gap from each other and in turn by a respective one composed of two semicircle segments main ring and each one of two semicircular segments together set auxiliary ring are formed. The bolts of the bolt cage are respectively screwed at one, threaded end into threaded holes of the respective associated inner ring and at their other ends in corresponding openings each of a right and a left outer side tenscheibe attached, each at the outer end faces of the rollers disposed adjacent between the inner and the outer bearing ring. The assembly of this pin cage takes place during assembly of the spherical roller bearing such that first the semicircular segments of the main ring of an inner ring around the pivoted out of the outer bearing ring inner bearing ring around and then the semi-circular segments of the auxiliary ring offset with their abutment surfaces to the abutting surfaces of the main ring on this and be pre-assembled by auxiliary screws on this. Subsequently, each carrying a roller bolt of an inner ring are screwed into the threaded holes in the main ring to further connect the main ring and the auxiliary ring together. After complete attachment of all bolts on the inner ring, the other ends of the bolts are inserted into the corresponding openings of the associated outer side window and firmly connected thereto by a respective weld. Thereafter, the spherical roller bearing is then turned by 180 ° and mounted the other inner ring of the pin cage in the same way.

A disadvantage of this known pin cage, however, is that it is very expensive due to its two-part design and the necessary number of individual parts on the one hand in production and on the other hand requires a very complex and complex assembly of its individual segments and roles and thus increases the cost of a trained with such a pin cage bearing disadvantageously. Furthermore, the two outer side windows of the known pin cage have proved to be particularly disadvantageous in that they are arranged directly in front of the openings of the through holes in the rollers and thus largely prevent sufficient supply of lubricant to the bearings of the rollers in the through holes. This can lead to a lack of lubricant between the pins of the pin cage and the rollers, which leads to increased wear on the pin cage and / or on the rollers and ultimately has a reduction in the life of the bearing result. This effect is further enhanced by the fact that the outer side windows of the bolt cage are welded to the ends of the bolts, so that even during assembly of the bearing a large part of the lubricant burns in the through holes of the rollers by the high temperatures occurring during welding. Another disadvantage of the two outer side windows of the known pin cage, it is beyond that the axial installation dimension of the bearing must not be exceeded by them, so that necessaryΛeise the length of the rollers must be reduced and the rollers thus no longer on the entire possible width of the Run track of the outer bearing ring can roll. The reduction of the roll length has the consequence that the raceways on the inner and outer bearing ring in a complex manner of the changed geometry of the roles must be adjusted and the camp identifies a reduced overall load.

Object of the invention

The invention is therefore based on the object to design a structurally simple trained bolt cage for a double-row spherical roller bearing, which is characterized by a low manufacturing and assembly costs and low manufacturing costs and guaranteed by the always adequate lubrication of the bearings of the roles and the use of reduced-length roles is avoided.

Description of the invention

According to the invention this object is achieved in a pin cage according to the preamble of claim 1 such that the pin cage is formed as seitenscheiben- loose pre-assembled component consisting of a one-piece, closed annular disc and axially projecting from this annular disc pin whose length is smaller than the length of the through holes in the rollers is. The lubrication of the rollers takes place according to the invention. Measured by centrifugal force of the now free end side through the outer opening of its through hole and the free through the shortened pin cavity of these through holes is also formed as an additional lubricant reservoir.

In an expedient development of the inventively embodied pin cage, the annular disc of the pin cage preferably has a rhomboid-shaped profile cross-section, in which, starting from a vertical axis of symmetry, the opposing angles between the two upper side surfaces and the two lower side surfaces are cut off at right angles to the axis of symmetry and thus form a straight outer surface and a parallel inner surface on the annular disc.

Such a profile cross-section has proved to be particularly advantageous because the lower side surfaces of the washer can thereby be formed as a further feature of the inventively designed pin cage with holes machined perpendicularly in these side surfaces for fastening the bolt of the pin cage, wherein the angular arrangement of the lower side surfaces to each other at the same time the required axial inclination of the bolt of the Bolts cage to the raceways of the rollers on the inner and outer ring of the spherical roller bearing can be produced. In addition, the lower side surfaces of the annular disc of the pin cage are also provided as inner Axialfüh- rungsflächen for the rollers of the spherical roller bearing, while the outer axial guidance of the rollers is done by a known ring board on the outside of each track on the inner ring of the spherical roller bearing.

If the inner openings of the through holes in the rollers of the spherical roller bearing in the context of the inventively designed pin cage each funnel-shaped widened by a radius, it is another advantage of rhomboidförmigen profile cross section of the annular disc of the pin cage that its upper side surfaces together with the radius of the through hole each Roll each have a defined discharge channel for emerging from the through holes lubricant bil- the. As a result of the inclination of the rollers and by the centrifugal force acting on the lubricant during operation of the spherical roller bearing a conveying effect of the lubricant along the bolt through the through holes in the rollers through, thus, the lubricant from a known manner between two outer Fettstauscheiben and the rollers located outer lubricant reservoir or from the additional lubricant reservoir within the through holes of the roller over the thus formed discharge channel into an inner, above the annular disc of the pin cage formed lubricant reservoir are removed and compensate for the consumed from this inner lubricant reservoir amount of lubricant at least partially.

The fastening of the bolts of the bolt cage is then carried out in a further embodiment of the inventively designed pin cage preferably by welding or screwing one of its ends in the holes on the lower side surfaces of the annular disc, wherein the welding of the bolt by saving corresponding threads on the bolt and in the Holes of the washer has been found to be the least expensive. Further cost advantages can still be achieved if the holes in the annular disc are saved and the bolts are butt welded to the lower side surfaces of the annular disc. In order to achieve a sufficient stability and at the same time a required for the assembly of the rollers elasticity of the pin cage despite the omission of the outer side windows on the pin cage, are used in the inventively designed pin cage shortened bolts whose remaining after attachment to the washer free length only about 50% - 70% of the length of the through holes in the rollers of the spherical roller bearing corresponds. The rollers are mounted on the pin cage, for example, in such a way that the bolt cage preassembled with the pin is inserted between the inner ring and the outer ring of the spherical roller bearing and then a first roller with the inner opening of its through hole on the free end of a pin is put on. Thereafter, by pressing the roller in the direction of the annular disk, the roller is pushed axially onto the bolt, wherein the radius at the inner opening of the through hole of the roller and the elasticity of the pin cage make it possible in total that the roller sliding with its lateral surface over the annular flange on the raceway of the inner ring can be slid so far into the bolt in the tilted position until it engages in the raceway of the inner ring. In the same way, then the assembly of the remaining roles of the first row of rollers and after turning the spherical roller bearing and the rollers of the second row of rollers.

Finally, it is still a last feature of the inventively designed pin cage, that its bolts have a cylindrical profile cross-section over their entire free length, wherein the diameter of which is slightly smaller than the diameter of the through holes in the rollers. Such bolts are simple and inexpensive to produce and have optimum guiding properties for the rollers of the spherical roller bearing. However, since the diameter difference between the bolts of the pin cage and the through-hole of the rollers can lead to entanglement of the rollers or tilting of the rollers relative to the axes of the bolts during operation of the bearing, a cylindrical profile cross-section of the bolts may result, that the rollers have only punctiform contacts to the bolts and thus the bolts are subject to increased wear at these contact points. To avoid such an effect, it may therefore be advantageous to design the bolts over their entire free length, on both sides of a transverse axis corresponding to the longitudinal center of the rollers, with a conical profile cross section, so that the bolts have their greatest diameter at the level of the longitudinal center of the rollers and then taper to their ends. This ensures that with entanglements of the rollers or when tilting the rollers, a low-wear linear contact between the rollers and the bolts is always maintained, whereby a two-sided cone angle corresponding to the average setting angle of the rollers of the spherical roller bearing on the bolt of each has been found to be sufficient by about 1 °.

The inventively designed bolt cage for a double row pendulum roller lenlager thus has over the known from the prior art pin cages the advantage that it is structurally simple designed as a closed annular disk with freely projecting bolt and thus consists of a minimum of individual parts that are inexpensive to produce. Furthermore, the pin cage according to the invention can be used as a preassembled component in the spherical roller bearing and enables a simple and quick mounting of the rollers on the pin cage, so that the manufacturing costs for a spherical roller bearing formed with the pin cage according to the invention are reduced to a minimum. By eliminating the two otherwise common outer side windows on the bolt cage, it is also ensured that on the outer openings of the through holes in the rollers at any time sufficient lubricant can reach the bearings between the bolts of the pin cage and the rollers. In addition, by the absence of the two outer side windows already filled in the bearing lubricant no longer burn by final welding work on the cage during assembly of the bearing, so that characterized and resulting from the shortened pin additional lubricant reservoir in the free cavity of the through holes in the rollers an increased supply of lubricant is formed, which contributes to a significant increase in the life of the spherical roller bearing. Likewise, it is possible by eliminating the two outer side windows to use such rollers for the spherical roller bearings, which roll on the entire possible width of the raceways of the outer ring of the spherical roller bearing, so that equipped with a pin cage invention spherical roller bearings can be designed for higher overall loads ,

Brief description of the drawings

A preferred embodiment of the inventively designed bolt zenkäfigs will be explained in more detail with reference to the accompanying drawings. Showing:

Figure 1 is a perspective view of a partially cut double row Spherical roller bearing with inventively designed pin cage;

Figure 2 is an enlarged view of a cross section through a two-row spherical roller bearing with inventively designed pin cage;

Figure 3 is a perspective view of the inventively designed pin cage as a preassembled component;

Figure 4 is an enlarged view of a cross section through the inventively designed pin cage;

5 shows an enlarged view of an alternative Bolzenausfüh- tion for inventively designed pin cage.

Detailed description of the drawings

FIG. 1 clearly shows a double-row spherical roller bearing 1 which essentially consists of an inner ring 2 and an outer ring 3 and a plurality of two rows 4, 5 side by side on the raceways 6, 7, 8 and 9 of the inner ring 2 and the outer ring 3 running rollers 10 consists. Clearly visible is between the two rows of rollers 4, 5 arranged at its axial sides with equally spaced and staggered to each other fastened pin 11 trained pin cage 12, wherein the rollers 10 of both rows of rollers 4, 5 each have an axial through hole 13 through which they are rotatably mounted on a respective bolt 11 of the pin cage 12.

In Figures 2 and 3 is also seen that the pin cage 12 is formed according to the invention without outer side windows as preassembled component and consists of a one-piece, closed annular disc 14 and axially free of this projecting pin 11 whose length is smaller than the length of Through holes 13 in the rollers 10 is. Of the occurring in known spherical roller bearings lack of lubricant between the pin 11 and the rollers 10 is thereby repaired in this pin cage 12 that the lubrication of the rollers 10 according to the invention from the free end 15 ago from an unspecified, between two not shown Fettstauscheiben and the rollers 10th arranged outer lubricant reservoir through the outer opening 16 of their through holes 13 through, wherein the remaining through the shortened pin 11 of the pin cage 12 free cavity 17 of the through holes 13 at the same time forms an additional lubricant reservoir.

By the cross-sectional views in Figures 2 and 4, it is further clear that the annular disc 14 of the pin cage 12 has a rhomboid profile cross-section, in which, starting from a vertical axis of symmetry, the opposing angle between the two upper side surfaces 18, 19 and the two lower side surfaces 20, 21 are cut perpendicular to the axis of symmetry and thus each form a straight outer and inner surfaces of the annular disc 14. In the lower side surfaces 20, 21 of the annular disc 14 of the pin cage 12 are arranged perpendicular to these side surfaces 20, 21 arranged holes 22, which serve to fasten the bolt 11 to the washer 14, wherein the angular arrangement of the lower side surfaces 20 , 21 to each other at the same time the required axial inclination of the pin 11 of the pin cage 12 to the raceways 6, 7, 8, 9 of the rollers 10 on the inner ring 2 and the outer ring 3 of the spherical roller bearing 1 is produced. In addition, the lower side surfaces 20, 21 of the annular disc 14 of the pin cage 12 are provided as inner Axialführungsf laugh for the rollers 10 of the spherical roller bearing 1, while the outer axial guidance of the rollers 10 by the visible in Figure 2, unspecified ring rims on the outsides the raceways 8, 9 takes place on the inner ring 2 of the spherical roller bearing 1.

In addition, it can be seen in Figure 2 that the inner openings 23 of the through holes 13 in the rollers 10 of the spherical roller bearing 1 are each formed by a funnel-shaped widened, so that the inner Opening 23 together with the upper side surfaces 18, 19 of the annular disc 14 of the pin cage 12 forms a defined discharge channel 24 for emerging from the through holes 13 of the rollers 10 lubricant. As a result, the lubricant from the aforementioned outer lubricant reservoir of the spherical roller bearing 1 or from the additional lubricant reservoir in the free cavity 17 of the through holes 13 of the rollers 10 through the thus formed discharge channel 24 unhindered in an inner, unspecified lubricant reservoir above the annular disc 14 of the pin cage 12th be dissipated.

The attachment of the bolt 11 of the pin cage 12 then takes place, as also shown in Figure 2, by screwing one of its ends 25 in the holes 22 on the lower side surfaces 20, 21 of the annular disc 14, wherein the ends 25 of the pin 11 and the holes 22 of the annular disc 14 are each formed with corresponding, unspecified threads. In order to give the bolt cage 12 sufficient stability and at the same time required for the assembly of the rollers 10 elasticity, the bolts 11 are formed so shortened that their remaining after attachment to the washer 14 free length only about 50% - 70% of Length of the through holes 13 in the rollers 10 of the spherical roller bearing 1 corresponds.

Finally, FIGS. 1 to 4 show that the bolts 11 of the pin cage 12 have a cylindrical profile cross section over their entire free length, the diameter of which being slightly smaller than the diameter of the through holes 13 in the rollers 10. However, in order to exclude the disadvantageous effects occurring in the case of bolts 11 with such a profile cross-section in the case of entanglements of the rollers 10 occurring during operation of the spherical roller bearing 1, the bolts 11 can also optionally be formed in the alternative form shown in FIG. In this embodiment, the pins 11 clearly visible on their entire free length, on either side of one of the longitudinal center of the rollers 10 corresponding transverse axis, a tapered profile cross-section, so that the bolts 11 at the level of the longitudinal center of the rollers 10 have their largest diameter and then co- run out to their ends. Such a profile cross-section of the pin 11 causes the tilting of the rollers 10 during operation of the spherical roller bearing always a linear contact between the rollers 10 and the pin 11 is maintained, with a the average Schränkwinkel of the rollers 10 of the spherical roller bearing 1 corresponding bilateral cone angle α, ß has proved to the bolt 11 of each about 1 ° as sufficient.

LIST OF REFERENCE NUMBERS

1 spherical roller bearing

2 inner ring

3 outer ring

4 rows of rollers

5 rows of rollers

6 career

7 career

8 career

9 career

10 rolls

11 bolts

12 bolt cage

13 through hole

14 annular disc

15 front side

16 outer opening

17 cavity

18 upper side surface

19 upper side surface

20 lower side surface

21 lower side surface

22 bore

23 inner opening

24 discharge channel

25 ends α cone angle ß cone angle

Claims

claims

1. Bolt cage for a double-row spherical roller bearing, with the following features:

■ the spherical roller bearing (1) has an inner ring (2) and an outer ring (3) and several rollers (10) running side by side in two rows (4, 5) on their raceways (6, 7, 8, 9), ■ between the rows of rollers (4, 5) is arranged on its axial sides with equally spaced and stepped staggered to each other bolts (11) formed bolt cage (12),

^■ the rollers (10) of the two rows of rollers (4, 5) each have an axial through bore (13), about which they are rotatable on a respective pin (11) of the bolt retainer mounted (12), characterized in that ■ the pin cage ( 12) is formed as a side windowless preassembled component consisting of a one-piece, closed annular disc (14) and axially free of this projecting pin (11) whose length is smaller than the length of the through holes (13) in the rollers (10) , Wherein the lubrication of the rollers (10) by centrifugal force from the free end face (15) forth through the outer opening (16) of its through hole (13) passes through and the free cavity (17) of these through holes (13) formed as an additional lubricant reservoir is.

2. Bolt cage according to claim 1, characterized in that the ring Disc (11) of the pin cage (12) preferably has a rhomboid profile cross-section, in which, starting from a vertical axis of symmetry, the opposing angles between the two upper side surfaces (18, 19) and the two lower side surfaces (20, 21) right are cut off at an angle to the axis of symmetry.

3. Bolt cage according to claim 2, characterized in that the lower side surfaces (20, 21) of the annular disc (11) of the pin cage (12) preferably perpendicular in these side surfaces (20, 21) incorporated holes (22) for fixing the bolt (11 ) and are formed as inner axial guide surfaces of the rollers (10) of the spherical roller bearing (1).

4. Bolt cage according to claim 2, characterized in that the inner openings (23) of the through holes (13) in the rollers (10) of the spherical roller bearing (1) are each formed widened by a radius and together with the upper side surfaces (18 , 19) of the annular disc (14) of the pin cage (12) form a defined discharge channel (24) for lubricant emerging from the through bores (13) of the rollers (10).

5. Bolt cage according to claim 3, characterized in that the fastening of the bolt (11) of the pin cage (12) preferably by welding or screwing one of its ends (25) in the bores (22) on the lower side surfaces (20, 21) of the Ring disc (14) takes place and the free length of the bolts (11) approximately 50% to 70% of the length of the Durchgangsboh- ments (13) in the rollers (10) of the spherical roller bearing (1) corresponds.

6. Bolt cage according to claim 5, characterized in that the bolts (11) of the pin cage (12) over its entire free length optionally either a cylindrical profile cross-section or, both sides of one of the longitudinal center of the rollers len (10) corresponding transverse axis, a tapered profile cross-section have, wherein the cone angles (α, ß) on both sides preferably the Schränkwinkel the rollers (10) of the spherical roller bearing (1) of about 1 °.