Angular contact roller bearing and method and device for the assembly thereof

Abstract

Angular contact roller bearings include an inner bearing ring with an inner raceway, which is arranged on the outer shell surface of the inner bearing ring so as to be inclined with respect to the bearing axis of rotation. An outer bearing ring has an outer raceway, which is arranged on the inner shell surface of the outer bearing ring so as to be inclined with respect to the bearing axis of rotation. An integrally formed rim delimits each, and a multiplicity of roller-type rolling bodies are arranged between the bearing rings and roll on the raceways of the bearing rings and are held with uniform spacings to one another in a circumferential direction by a bearing cage.

Claims

1. An angular contact roller bearing comprising: an inner bearing ring with an inner raceway, which is arranged on an outer shell surface of said inner bearing ring so as to be inclined with respect to a bearing axis of rotation, said inner bearing ring having an integrally formed inner rim which delimits said inner raceway at its smallest diameter; an outer bearing ring with an outer raceway, which is arranged on an inner shell surface of said outer bearing ring so as to be inclined with respect to the bearing axis of rotation, said outer bearing ring having an integrally formed outer rim which delimits said outer raceway at its greatest diameter; and a multiplicity of roller-type rolling bodies, each having a maximum diameter, which are arranged between the bearing rings and which roll on the raceways of said bearing rings and which are held with uniform spacings to one another in a circumferential direction by a bearing cage; and wherein the inner rim and the outer rim each have a height of 18% to 22% of the maximum diameter; wherein the roller-type rolling bodies are formed as tapered rollers which have a taper angle in the range from 1 to 4, and which roll with an envelope circle angle of between 3 and 7 on their raceways.

2. The angular contact roller bearing as claimed in claim 1, wherein a gap between the outer shell surface of the inner bearing ring and the inner shell surface of the outer bearing ring is dimensioned such that two times the dimension of said gap is greater than the maximum diameter of the roller-type rolling bodies.

3. The angular contact roller bearing as claimed in claim 1, wherein the bearing cage is formed by a comb-type cage which is insertable into the angular contact roller bearing after installation of the roller-type rolling bodies and which is composed of a cage ring and of a multiplicity of axial cage webs.

4. The angular contact roller bearing as claimed in claim 3, wherein the bearing cage has, on its cage webs, multiple uniformly circumferentially distributed detent webs which run so as to be inclined with respect to the bearing axis of rotation and by which the bearing cage is axially fixable in position on an inner surface of the outer rim.

5. The angular contact roller bearing as claimed in claim 1, wherein said angular contact roller bearing is sealed off against contamination from the outside, and against the escape of lubricant that has possibly been introduced into a bearing interior space, by two elastomer sealing disks which are inserted, axially on both sides of the roller-type rolling bodies, into encircling fastening grooves in the inner shell surface of the outer bearing ring and which have metal reinforcement.

6. A method for assembling an angular contact roller bearing comprising: in a first step, placing an inner bearing ring onto a horizontal assembly plane with a convex sickle-shaped auxiliary ramp, said inner bearing ring having an inner raceway, which is arranged on an outer shell surface of said inner bearing ring so as to be inclined with respect to a bearing axis of rotation, said inner bearing ring having an inner rim which delimits said inner raceway at its smallest diameter, in such a way that said inner bearing ring bears with its rim against an inner diameter side of the auxiliary ramp; in a second step, arranging an outer bearing ring eccentrically with the inner ring, said outer ring having an outer raceway, which is arranged on an inner shell surface of said outer bearing ring so as to be inclined with respect to the bearing axis of rotation, said outer bearing ring having an outer rim which delimits said outer raceway at its greatest diameter, a face side having the rim facing away from the horizontal assembly plane; and in a third step, filling a sickle-shaped free space formed between the outer bearing ring and the inner bearing ring with roller-type rolling bodies in the form of tapered rollers such that relatively small face sides of said roller-type rolling bodies lie on an oblique side of the auxiliary ramp.

7. The method as claimed in claim 6, wherein, in a fourth step, the outer bearing ring is clamped such that the outer bearing ring is slightly ovalized within its elasticity limit.

8. The method as claimed in claim 7, wherein, in a fifth step, the inner bearing ring is displaced into a coaxial position with respect to the outer bearing ring, and the roller-type rolling bodies are uniformly circumferentially distributed in their raceways in the bearing rings, with the ovalization of the outer bearing ring being eliminated.

9. A method for assembling an angular contact roller bearing comprising: in a first step, placing an outer bearing ring onto a horizontal assembly plane with a convex sickle-shaped auxiliary ramp, said outer bearing ring having an outer raceway, which is arranged on an inner shell surface of said outer bearing ring so as to be inclined with respect to a bearing axis of rotation (AL), said outer bearing ring having an outer rim which delimits said outer raceway at its greatest diameter, in such a way that said outer bearing ring bears with its rim against an outer diameter side of the auxiliary ramp in a second step, arranging an inner bearing ring eccentrically with respect to the outer bearing ring, said inner bearing ring having an inner raceway, which is arranged on an outer shell surface of said inner bearing ring so as to be inclined with respect to the bearing axis of rotation, said inner bearing ring having an inner rim which delimits said inner raceway at its smallest diameter, such that, at one side, the auxiliary ramp is arranged between the bearing rings and, at the other side, offset 180 with respect to the center of the auxiliary ramp, the bearing rings bear against one another in a third step, filling a sickle-shaped free space formed between the outer bearing ring and the inner bearing ring with roller-type rolling bodies in the form of tapered rollers such that relatively large face sides of said roller-type rolling bodies lie on an oblique side of the auxiliary ramp.

10. The method as claimed in claim 9, wherein, in a fourth step, the outer bearing ring is clamped such that the outer bearing ring is slightly ovalized within its elasticity limit.

11. The method as claimed in claim 10, wherein, in a fifth step, the inner bearing ring is displaced into a coaxial position with respect to the outer bearing ring, and the roller-type rolling bodies are uniformly circumferentially distributed in their raceways in the bearing rings, with the ovalization of the outer bearing ring being eliminated.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) An embodiment of the angular contact roller bearing designed according to the disclosure and two alternative variants of the method for the assembly thereof and two associated devices for carrying out said method variants will be discussed in more detail below with reference to the appended drawings, in which:

(2) FIG. 1 shows an enlarged illustration of a cross section through an angular contact roller bearing designed according to the disclosure;

(3) FIGS. 2a, 2b show an illustration of the first step of the first variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(4) FIGS. 3a, 3b show an illustration of the second step of the first variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(5) FIGS. 4a, 4b show an illustration of the third step of the first variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(6) FIGS. 5a, 5b show an illustration of the first step of the second variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(7) FIGS. 6a, 6b show an illustration of the second step of the second variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(8) FIGS. 7a, 7b show an illustration of the third step of the second variant of the assembly method according to the disclosure in a plan view and in a sectional view;

(9) FIGS. 8a, 8b show an illustration of the fifth step of both variants of the assembly method according to the disclosure in a plan view and in a sectional view;

(10) FIGS. 9a, 9b show an illustration of the sixth step of both variants of the assembly method according to the disclosure in a plan view and in a sectional view;

(11) FIGS. 10a, 10b show an illustration of the auxiliary ramp for carrying out the first variant of the assembly method according to the disclosure in a plan view and in a sectional view; and

(12) FIGS. 11a, 11b show an illustration of the auxiliary ramp for carrying out the second variant of the assembly method according to the disclosure in a plan view and in a sectional view.

DETAILED DESCRIPTION

(13) FIG. 1 illustrates a cross section through a single-row angular contact roller bearing which is suitable for example as a replacement for the previously used deep-groove ball bearing for the mounting of the crankshaft in motor vehicle internal combustion engines. As can be clearly seen, said angular contact roller bearing 1 is composed of an inner bearing ring 2 with an inner raceway 4, which is arranged on the outer shell surface 3 of said inner bearing ring so as to be inclined with respect to the bearing axis of rotation AL and which is delimited at its smallest diameter by a rim 5, and of an outer bearing ring 6 with an outer raceway 8, which is arranged on the inner shell surface 7 of said outer bearing ring likewise so as to be inclined with respect to the bearing axis of rotation AL and which is delimited at its greatest diameter by a rim 9. Furthermore, between the bearing rings 2, 6, there is arranged a multiplicity of roller-type rolling bodies 10 which roll on the raceways 4, 8 of said bearing rings and which are held with uniform spacings to one another in a circumferential direction by a bearing cage 11.

(14) It can furthermore be seen in FIG. 1 that the outer shell surface 3 of the inner bearing ring 2 and the inner shell surface 7 of the outer bearing ring 6 are, in each case outside the raceways 4, 8, of cylindrical form so as to run coaxially with respect to the bearing axis of rotation AL, and the raceways 4, 8 of the two bearing rings 2, 6 are each formed in conical fashion into the cylindrical shell surfaces 3, 7. The rims 5, 9 which are thus formed and which delimit the raceways 4, 8 in each case on one side are thus each formed integrally with the bearing rings 2, 6.

(15) It can likewise be seen in FIG. 1 that the roller-type rolling bodies 10 are formed as tapered rollers which have a taper angle preferably of 2 and which roll with an envelope circle angle preferably of 6 on their raceways 4, 8. Furthermore, the gap S between the outer shell surface 3 of the inner bearing ring 2 and the inner shell surface 7 of the outer bearing ring 6 is dimensioned such that two times the dimension of said gap is greater than the greatest diameter DW of the roller-type rolling bodies 10, in order to permit the insertion of the roller-type rolling bodies 10 into the radial rolling bearing 1 in accordance with the assembly method described in more detail below. Furthermore, both the rim 5 which delimits the raceway 4 in the inner bearing ring 2 and the rim 9 which delimits the raceway 8 in the outer bearing ring 6 have an equal minimum height h.sub.BI, h.sub.BA of approximately 20%, of the greatest diameter DW of the roller-type rolling bodies 10, in order to enable high axial forces in one direction that arise during bearing operation to be accommodated with the least possible rim friction.

(16) It can also be seen in FIG. 1 that the bearing cage 11 is preferably formed by a comb-type cage which is insertable into the radial rolling bearing 1 after the installation of the roller-type rolling bodies 10. Here, the bearing cage 11, which is composed of a cage ring 12 and of a multiplicity of axial cage webs 13, has, on its cage webs 13 (obscured in the illustration), multiple uniformly circumferentially distributed detent webs 14 (likewise obscured in the illustration), which run so as to be inclined with respect to the bearing axis of rotation AL and by which the bearing cage 11 is axially fixable in position on the inner surface 15 of the rim 9 on the outer bearing ring 6.

(17) Finally, it can also be seen in FIG. 1 that the radial rolling bearing 1 is sealed off against contamination from the outside, and against the escape of lubricant that has possibly been introduced into the bearing interior space 20, by two elastomer sealing disks 18, 19 which are inserted, axially on both sides of the roller-type rolling bodies 10, into encircling fastening grooves 16, 17 in the inner shell surface 7 of the outer bearing ring 6 and which have metal reinforcement. This design which is known per se in other rolling bearing types is possible in the case of the radial rolling bearing 1 according to the disclosure, by contrast to known angular contact roller bearings, only because said radial rolling bearing 1 according to the disclosure, by the radially planar form of the outer shell surface 3 of the inner bearing ring 2 and of the inner shell surface 7 of the outer bearing ring 6, has suitable fastening surfaces and suitable sealing surfaces for such elastomer sealing disks 18, 19.

(18) FIGS. 2a, 2b, 3a, 3b and 4a, 4b furthermore schematically illustrate the first steps of a first variant of an assembly method for the angular contact roller bearing 1 according to the disclosure. Said assembly method is substantially a modified eccentric assembly method known per se as an assembly method for deep-groove ball bearings, in the case of which, as can be seen in FIGS. 2a and 2b, in a first step, the inner bearing ring 2 is placed, with its face side formed with the rim 5, onto a horizontal assembly plane 21 with a convex sickle-shaped auxiliary ramp 22 in such a way that said inner bearing ring bears with its rim 5 against the inner diameter side 24 of the auxiliary ramp 22.

(19) Subsequently, in a second step, the outer bearing ring 6 is arranged, with its face side formed with the rim 9 upward, eccentrically with respect to the inner bearing ring 2 such that, as can be clearly seen in FIGS. 3a and 3b, at one side, the auxiliary ramp 22 is arranged between the bearing rings 2, 6 and, at the other side, offset 180 with respect to the center of the auxiliary ramp 22, the bearing rings 2, 6 bear against one another.

(20) In a third step illustrated in FIGS. 4a and 4b, the sickle-shaped free space formed between the outer bearing ring 6 and the inner bearing ring 2 is filled with the roller-type rolling bodies 10 in the form of tapered rollers such that the relatively small face sides of said roller-type rolling bodies lie on the oblique side 26 of the auxiliary ramp 22.

(21) The second variant, illustrated in FIGS. 5a, 5b, 6a, 6b and 7a, 7b, of the assembly method for the angular contact roller bearing according to the disclosure is likewise a modified eccentric assembly method and differs from the first variant in that, in the first step shown in FIGS. 5a and 5b, in this case the outer bearing ring 6 is placed, with its face side formed with the rim 9, onto a horizontal assembly plane 21 with a convex sickle-shaped auxiliary ramp 23 in such a way that said outer bearing ring bears with its rim 9 against the outer diameter side 25 of the auxiliary ramp 23.

(22) Similarly to the first variant, it is then the case in a second step that the inner bearing ring 2 is arranged, with its face side formed with the rim 5 upward, eccentrically with respect to the outer bearing ring 6 such that, as can be seen in FIGS. 6a and 6b, at one side, the auxiliary ramp 23 is arranged between the bearing rings 2, 6 and, at the other side, offset 180 with respect to the center of the auxiliary ramp 23, the bearing rings 2, 6 bear against one another.

(23) Then, in a third step illustrated in FIGS. 7a and 7b, it is the case here too that the sickle-shaped free space formed between the inner bearing ring 2 and the outer bearing ring 6 is filled with the roller-type rolling bodies 10 in the form of tapered rollers, but with the difference that, here, the relatively large face sides of said roller-type rolling bodies 10 lie on the oblique side 27 of the auxiliary ramp 23.

(24) Independently of the two variants of the eccentric assembly method, it is then the case in a fourth step which is not illustrated in any more detail in the drawings that the outer bearing ring 3 is clamped, at the level of the contact point with the inner bearing ring 2 and at the level of a point on the outer shell surface of said outer bearing ring which is offset 180 with respect to the contact point, such that the outer bearing ring 3 is slightly ovalized within its elasticity limit. Subsequently, as can be seen from FIGS. 8a and 8b, in a fifth step, the inner bearing ring 2 is displaced into a coaxial position with respect to the outer bearing ring 3, and the roller-type rolling bodies 10 are uniformly circumferentially distributed in their raceways 4, 8 in the bearing rings 2, 6, with the ovalization of the outer bearing ring 3 being eliminated.

(25) In the case of the first variant of the eccentric assembly method according to the disclosure being implemented, it is then the case in a sixth step, which for the sake of simplicity is however not illustrated in the drawings, that the bearing cage 11 in the form of a comb-type cage is inserted with its cage webs 13 between the roller-type rolling bodies 10 from the side with the relatively small face sides of said roller-type rolling bodies, and said bearing cage is engaged with its detent lugs with detent action against the inner surface of the rim 5 on the inner bearing ring 2. In the case of the second variant of the eccentric assembly method according to the disclosure being implemented, it is by contrast the case in a sixth step that the bearing cage 11 in the form of a comb-type cage is, as shown in FIGS. 9a and 9b, inserted with its cage webs 13 between the roller-type rolling bodies 10 from the side with the relatively large face sides of said roller-type rolling bodies, and, as shown in FIG. 1, said bearing cage is engaged with its detent webs 14 with detent action against the inner surface 15 of the rim 9 on the outer bearing ring 6. Finally, it is then also the case that the bearing interior space 20 is filled with lubricant, and the two elastomer sealing disks 18, 19 are inserted into the encircling fastening grooves 16, 17 in the inner shell surface 7 of the outer bearing ring 6 in the manner likewise illustrated in FIG. 1.

(26) Finally, FIGS. 10a, 10b and 11a, 11b illustrate the auxiliary ramps 22 and 23 for carrying out the two variants of the eccentric assembly method according to the disclosure. Here, the auxiliary ramp 22 used for the first method variant is distinguished by the fact that it bears with its inner diameter side 24 against the inner bearing ring 6 and, as can be clearly seen in FIGS. 10a and 10b, has an oblique side 26, which tapers toward the outer bearing ring 3 with the angle of inclination of the raceway 4 in the inner bearing ring 2, and a maximum ramp height h.sub.R which corresponds to the rim height h.sub.BI on the inner bearing ring 2.

(27) By contrast, the auxiliary ramp 23 used for the second method variant is distinguished by the fact that it bears with its outer diameter side 25 against the outer bearing ring 6 and, as can be seen in FIGS. 11a and 11b, has an oblique side 27, which tapers toward the inner bearing ring 2 with the angle of inclination of the raceway 8 in the outer bearing ring 6, and a maximum ramp height h.sub.R which corresponds to the rim height h.sub.BA on the outer bearing ring 6.

LIST OF REFERENCE DESIGNATIONS

(28) 1 Radial rolling bearing 2 Inner bearing ring 3 Outer shell surface of 2 4 Inner raceway in 2 5 Rim on 4 6 Outer bearing ring 7 Inner shell surface of 6 8 Outer raceway in 6 9 Rim on 8 10 Roller-type rolling body 11 Bearing cage 12 Cage ring of 11 13 Cage webs on 12 14 Detent webs on 13 15 Inner surface of 9 16 Fastening groove in 7 17 Fastening groove in 7 18 Elastomer sealing disk 19 Elastomer sealing disk 20 Bearing interior space 21 Assembly plane 22 Auxiliary ramp 23 Auxiliary ramp 24 Inner diameter side of 22 25 Outer diameter side of 23 26 Oblique side on 22 27 Oblique side on 23 AL Bearing axis of rotation Taper angle Envelope circle angle S Gap between 3 and 7 DW Greatest diameter of 10 h.sub.BI Rim height on 2 h.sub.BA Rim height on 6 h.sub.R Ramp height