DE102022119916A1 - Thrust bearing with curved thrust bearing disk - Google Patents

Abstract

The invention relates to a multi-row axial bearing (1) with rolling elements (5, 6, 7) and at least one axial disk (8, 9), the axial disk (8, 9) having at least one rolling raceway (10, 11, 12) for the rolling elements (5, 6, 7) is provided, and wherein first rolling bodies (5) designed as balls (13) and first rolling bodies (6) designed as rollers (14) are provided, the axial disk (8, 9) having at least one curvature (15, 16, 17, 18). The axial disk (8, 9) has at least a first rolling raceway (10) for rolling contacts with the balls (13) and a second rolling raceway (11) for contacts with the rollers (14), the first rolling raceway (10) and the second rolling raceway (11) differ geometrically from one another.

Description

Field of invention

The invention relates to an axial bearing with rolling bodies and with at least one axial disk, the axial disk being provided with at least one rolling raceway for the rolling bodies, and first rolling bodies designed as balls and second rolling bodies designed as rollers are provided, the axial disk being provided with at least one curvature is.

Background of the invention

From the US 2016/0010688 A1 an axial bearing of the genus emerges that is formed in a single row from a row of balls and needles. When using such bearings, two circumstances are taken advantage of. On the one hand, the fact is taken advantage of that rolling bearings with balls usually have low frictional resistance when operating under load compared to rolling bearings with needles. On the other hand, the fact is taken advantage of that rolling bearings with needles can absorb comparatively higher loads. Due to the curved raceways, the axial bearings carry lower loads essentially via the balls and a very small proportion of the length of the needles, which means that the bearing runs with very little friction. Under load, the axial disks deflect axially, ie the curvature is reduced and the line contact between the needles and the rolling raceways can be achieved up to the maximum. This improves the load capacity of the thrust bearing. However, there are limits to the carrying capacity.

Description of the invention

The object of the invention is to create a thrust bearing with improved function, with which the load capacity can be increased and with which the friction can nevertheless be reduced.

The task is solved with the subject matter of claim 1.

A feature of the invention provides that the thrust bearing is a multi-row thrust bearing with at least two rows arranged concentrically to a central axis. The axial disk has at least two rolling raceways that differ geometrically from one another. Each rolling track is assigned a row of rolling elements. The rolling elements are arranged in a common first radial plane. This means that the rows of rolling elements have a mutually parallel supporting effect, at least when the axial bearing is under maximum load. A key feature is that the rolling raceways differ from each other in terms of their geometry and their position relative to the central axis. It is also conceivable that the rolling raceways differ from one another with regard to their orientation to the first radial plane. For the rolling bodies, lying together in a radial plane means that the rolling body centers lie in the radial plane. For balls, the rolling body centers are the ball centers and for rollers these are the individual roller axes of symmetry. In the latter case, it is sufficient if the roller axes intersect the first radial plane. In this case the intersection points are the centers. The first radial plane is an imaginary plane penetrated perpendicularly by the central axis of the axial bearing.

The central axis of the thrust bearing is defined as axially aligned. Radial is therefore perpendicular to the roller axis. In connection with the arrangement according to the invention, radial planes are penetrated perpendicularly by the central axis.

In their basic shape, rollers are cylindrical, but also spherical or deviating from spherical rolling bodies, which rotate or roll around their own rolling axis. In this case, the term rolls also includes rolls defined as needles with a larger length-to-diameter ratio.

The central axis of the thrust bearing is a pivot axis or rotation axis about which the rows of the thrust bearing arranged concentrically to this central axis pivot with pivot angles of up to 360° or rotate with rotation angles > 360° around the central axis of the thrust bearing.

Both the front of the axial disk and its rear are directed away from the second radial plane when viewed from the second radial plane.

The advantage of the invention results from the fact that the axial bearing is designed in several rows in a parallel arrangement. Parallel arrangement means that under the highest load, the rolling elements in all rows next to each other carry the load in the direction of the load. Each row is assigned a rolling track adapted to the loads, load sequence and the special geometry of the rolling elements used for this row. This means that optimal rolling conditions can be adjusted to the operating and load conditions and the friction in the rolling bearing can be reduced - which allows the efficiency and service life of such axial bearings to be optimally designed and with a view to the reduced friction This means that less energy is used and the CO ₂ balance is improved.

One embodiment of the invention provides that the axial bearing has a third row with third rolling elements arranged in the same radial plane as the first and second rolling elements. This measure allows the thrust bearing to be adapted to particularly high loads. The latter is particularly the case if, as one embodiment of the invention provides, the third rolling elements are designed as rollers.

The third row rollers may have the same length and shape as the second row rollers and may be made of the same material, or may differ from those in these characteristics. When using the same rolls, their production is more economical because larger batch sizes can be produced and the costs for transport, handling and storage are comparatively lower than when using different rolls.

With one embodiment of the invention it is provided that the rolling elements, both the balls and the rollers, all have the same diameter. The same diameter means that the rolling elements have the same nominal size, i.e. that the diameters can differ from one another within permissible tolerances. Alternatively, the balls can have a different diameter than the needles. It is also envisaged that the needles differ in diameter from row to row or even from one another in a row. The same applies to the balls. The diameter of the rolling elements, together with the geometry of the raceways, can be used to set certain special deflection and rolling characteristics that cannot be achieved with standard axial bearings.

In view of the above, a third rolling track is provided for the third row in a further development of the previous embodiment, thereby positively providing a further option for setting an adapted rolling behavior. The geometry of this third rolling raceway can optionally differ from the first rolling raceway and/or the second rolling raceway.

As already mentioned at the beginning, the three rows are arranged in a common radial plane. This results in a further embodiment of the invention, according to which the second row adjoins the first row in the first radial plane radially on the inside towards the central axis of the axial bearing and the third row adjoins the first row in the first radial plane on the outside away from the first radial plane first row connects radially.

With a further embodiment of the invention it is provided that the first curvature, viewed in a longitudinal section along the central axis, rises above a second radial plane in an axially convex manner. The rolling raceways are formed on the outside of the convex surface of the curvature. The first rolling raceway is axially further away from this second radial plane than the second rolling raceway and/or the first rolling raceway. The first rolling raceway, which is the rolling raceway for the balls, is preferably formed at the reversal point from rising to falling of the arcuate lines of the convex contour of the axial disk that is furthest away from the second radial plane. The other two rolling raceways therefore run axially offset from the first rolling raceway in the direction of the second radial plane. The difference in the axial distances can either be compensated for by larger rolling body diameters of the second and third rolling bodies, or, as a preferred development provides, remains as an axial air gap, at least in the unloaded state of the axial rolling bearing. In the lightly loaded state, the thrust bearing only runs supported by the rolling contact of the balls with very low frictional resistance and energy consumption. With higher loads and deflection of the axial disk, the load share of the rollers will increase and the rollers ultimately support the loads within the scope of their predetermined rolling contact, so that a high load capacity is ensured by two rows of rollers and a row of balls acting in parallel.

The elasticity or the elastic behavior of the axial disk is optimally designed if the axial disk is hollowly curved on its back and at the same time elastically flexible. This allows the axial disk to deflect elastically under load, so that all rows come into play, and to spring back elastically when the load is relieved, so that only the row of balls is supported again. According to one embodiment of the invention, the axial disk is curved in an arc shape when viewed in any longitudinal section along the central axis. The first curvature of the first axial disk according to the definition of the patent claim is connected to the at least one roller raceway by a front facing away from the second radial plane and axially spaced from a second radial plane and also by a back facing away from the front and facing the second radial plane radial heights characterized in such a way that both the front and the back rise axially above the second radial plane and away from the second radial plane in a common axial direction have vex uplifting courses. The axial disk is preferably a component stamped from sheet metal, preferably sheet steel, and embossed with the rolling raceways. The wall thickness of the axial disk can be the same in any longitudinal sections or, alternatively, the axial disk can have different thicknesses. The second radial plane is an imaginary plane in which the axial disk is supported. The axial disk is preferably supported via the circular lines of a radially outer body edge of the axial disk or surface contact of a radially outer or the entire rear side of the axial disk. The latter preferably at maximum load on the axial bearing. The back is the side of the axial disk facing away from the rolling raceways, which is supported on a component.

A further embodiment of the invention provides further depressions or elevations, i.e. bulges, on the first curvature, which are locally annular, preferably in the area of the rolling raceways. Such measures can be easily integrated into the punching or embossing process in the production of the axial disk without additional or barely noticeable additional effort. By means of such a measure, further specific deflection and rolling characteristics can advantageously be adjusted. The local curvatures, which are preferably spherical circular surfaces and revolve concentrically around the central axis, can protrude from the first curvature in a spherical, convex manner when viewed in any longitudinal sections through the axial disk along the central axis, or can bulge in a spherical, concave manner into the first curvature. The latter is particularly advantageous on the rolling raceway for the balls because it creates an oscillation between the rolling raceway and the balls in the manner of a ball groove of a ball bearing, through which the surface pressure in the rolling contact is reduced and the load-bearing capacity of the row of balls is increased.

The rolling and load-bearing behavior can also be positively influenced by the fact that the axial bearing is provided with two of the axial disks. In the interest of economical batch sizes, the two axial disks are preferably designed as identical parts in terms of geometry and material technology. However, it is also conceivable to provide a further axial disk with any suitable different geometry or on rolling raceway(s) formed directly on a component.

The rolling elements of the individual rows are preferably guided in a common cage. Alternatively, it is also conceivable to use two or three cages and/or several cage segments to guide the rolling elements.

Description of the drawings

• 1 zeigt einen Ausschnitt eines längs seiner Zentralachse 19 geschnittenen Axiallagers 1.
• 2 zeigt die untere Axialscheibe 8 der beiden Axialscheiben 8 und 9 des mit 1 dargestellten Axiallagers 1 als Einzelteil in der mit der Darstellung nach 1 vergleichbaren Ansicht.

The invention is explained in more detail below using an exemplary embodiment.

• 1 shows a section of an axial bearing 1 cut along its central axis 19.
• 2 shows the lower axial disk 8 of the two axial disks 8 and 9 of the with 1 Thrust bearing 1 shown as an individual part in the illustration 1 comparable view.

1 - The axial bearing 1 is formed from a first axial disk 8, a second axial disk 9, first rolling elements 5, second rolling elements 6 and third rolling elements 7 and a cage 22. The first rolling elements 5 are designed as balls 13. The second rolling elements 6 and the third rolling elements 7 are each designed as rollers 14. The roles 14 are identical parts. The diameters D of the balls 13 and the rollers 14 are all the same.

The balls 13 are guided together in a first row 2 in the cage 22. The thrust bearing 1 has two rows 3 and 4 with the rollers 14. The rows 2, 3 and 4 or their rolling elements 5, 6 and 7 are arranged concentrically to the central axis 19. The ball centers 23 of the balls 13 and the roller axes 24 of the rollers 14 ideally lie in the first radial plane L1.

1 and 2 - The respective axial disk 8 or 9 is provided with at least the rolling raceways 10, 11 and 12 for the rolling elements 5, 6 and 7. The respective first rolling track 10 is intended for rolling contacts of the balls 13 of the first row 2 with the respective axial disk 8 or 9. The respective second rolling track 11 is intended for rolling contacts with the rollers 14 of the second row 3. The respective third rolling track 12 is assigned to rolling contacts of the rollers 14 of the third row 4 with the axial disks 8 and 9. The axial disks 8 and 9 are identical parts.

1 - In the illustration, the axial bearing 1 is not or only slightly loaded, so that only the balls 13 carry. Between the rollers 14 and the respective opposing rolling raceways 11 and 11 of the second row 3, an air gap 26 which extends around the central axis and narrows radially in the direction of the central axis or an air gap 27 which widens axially radially in the direction of the central axis 19 is formed.

The ideal case is shown in which, as already mentioned, the ball centers 23 of the balls 13 and the roller axes 24 of the rollers 14 lie in the first radial plane L1. Possible possible displacements of the rolling elements that deviate from this ideal case per 5, 6, 7 to each other or axial sags and tilting of the rolling elements 6 or 7 in the cage 22 and possibly one-sided contact of the rollers 14 without load with one of the rolling raceways 11 and 12 are conceivable in practice, so that air gaps between only one side the one rolling track 11 or 12 and the respective roller 14 can be designed to be twice as high as the two air gaps 26 and 27, while on the other hand the rollers 14 sag in one direction, for example under the effect of gravity, and in this direction rolling raceways 11 or .12 concerns.

2 - Both the first roller raceway 10 and the second roller raceway 11 as well as the first roller raceway 10 and the third roller raceway 12 as well as the second roller raceway 11 and the third roller raceway 12 differ geometrically from one another. The radius R3 of the third rolling raceway 12 is larger than the radius R1 of the first rolling raceway 10 and the radius R1 of the first rolling raceway 10 is larger than the radius R2 of the second rolling raceway 11. The axial distance A1 of the first rolling raceway 10 from the second radial plane L2 is largest of the distances A1, A2 and A3 and larger than the axial distances A2 and A3 of the second rolling raceway 11 and the third rolling raceway 12 from the second radial plane L2. The distances A2 and A3 of the second rolling raceway 11 and the third rolling raceway 12 are the same. The axial disk 8 is curved in the longitudinal section in such a way that its first curvature 15 rises convexly in a longitudinal section along a second radial plane L2 in an axially bulbous manner with the axial direction of the arrow away from this radial plane L2. The second radial plane L2 is a plane parallel to the first radial plane L1. In this radial plane L2, the axial disk 8 is supported during installation, for example against a component (not shown), with a body edge 25 running around the central axis 19. It is also shown and possible that the radially inner body edge 28 of the axial disk 8 lies or is supported in the same radial plane L2, alternatively in a further radial plane (not shown). The first curvature 15 is characterized by a front side 20 facing away from the second radial plane L2 and axially spaced from the second radial plane L2 and also by a back side 21 facing away from the front side 20 and facing the second radial plane L2 in such a way that both the front side 20 as well as the back 21 have courses that rise axially above the second radial plane L2 and run convexly away from the second radial plane L2 and are parallel to one another. The distance between the front 20 and the back 21 is defined by a constant sheet thickness of the punched and embossed axial disk 8. The front 20 has the rolling raceways 10, 11 and 12. The axial disk 8 is provided with further curvatures 16, 17 and 18, which are partially formed on the first curvature 15. The third curvature 17 is convexly bulged out of the first curvature 15 from the perspective of the radial plane L2 on the second rolling track 11. A second curvature 16 is concave on the first rolling raceway 10 as viewed from the radial plane L2 and a fourth curvature 18 on the third rolling raceway 12 is in turn designed to be convexly bulged. Due to its concave design, the second curvature 16 forms a ball groove in which the balls 13 run under rolling contact ( 1 ). Alternatively, the third curvature is convex and the second and/or fourth curvature are concave (not shown).

Reference symbols

1

Thrust bearing

2

first row

3

second row

4

third row

5

first rolling elements

6

second rolling elements

7

third rolling elements

8th

first axial disk

9

second axial disk

10

first rolling raceway

11

second rolling raceway

12

third rolling raceway

13

Bullet

14

role

15

first bulge

16

second bulge

17

third bulge

18

fourth bulge

19

Central axis of the thrust bearing

20

Front of the first axial disk

21

Back of the first axial disk

22

Cage

23

Sphere center

24

Roller axis

25

body edge

26

air gap

27

air gap

28

body edge

A1

axial distance of the first rolling raceway

A2

axial distance of the second rolling raceway

A3

axial distance of the third rolling raceway

D

diameter

L1

first radial plane

L2

second radial plane

R1

first radius

R2

first radius

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 20160010688 A1 [0002]

Claims (13)

Axial bearing (1) with rolling bodies (5, 6, 7) and at least one axial disk (8, 9), the axial disk (8, 9) having at least one rolling raceway (10, 11, 12) for the rolling bodies (5, 6, 7) is provided, and wherein first rolling bodies (5) designed as balls (13) and second rolling bodies (6) designed as rollers (14) are provided, the axial disk (8, 9) having at least one curvature (15, 16, 17, 18), characterized in that the axial bearing is a multi-row axial bearing (1) with at least two rows (2, 3, 4) arranged concentrically to a central axis (19) and the rolling elements arranged together in a first radial plane (L1). (5, 6, 7) and that the axial disk (8, 9) has at least a first rolling raceway (10) of the rolling raceways (10, 11, 12) of a first row (2) for rolling contacts with the balls (13) and a second Rolling raceway (11) of the rolling raceways (10, 11, 12) is assigned to a second row (3) for contacts with the rollers (14), the first rolling raceway (10) and the second rolling raceway (11) differing geometrically from one another. Axial bearing (1). Claim 1 , characterized in that the axial bearing (1) has a third row (4) with third rolling elements (7) arranged in the radial plane (L1). Axial bearing (1). Claim 2 , characterized in that the third rolling elements (7) are designed as rollers (14). Axial bearing after Claim 2 or 3 , characterized in that the first rolling bodies (5) and the second rolling bodies (6) and the third rolling bodies (7) have the same diameter (D). Thrust bearing (1) according to claim (2, 3 or 4), characterized in that a third rolling raceway (12) of the rolling raceways (10, 11, 12) of the third row (4) is assigned for rolling contacts with the third rolling elements (7). , wherein the third rolling raceway (12) differs geometrically from the first rolling raceway (10) and / or the second rolling raceway (11). Axial bearing after Claim 2 , 3 , 4 or 5 , characterized in that the second rolling bodies (6) and the third rolling bodies (7) are geometrically identical. Axial bearing (1) according to one of the preceding Claims 2 , 3 , 4 , 5 or 6 , characterized in that the second row (3) adjoins the central axis (19) of the axial bearing (1) in the first radial plane (L1) radially on the inside and the third row (4) adjoins the outside in the first radial plane (L1). away from the central axis (19) and radially adjoins the first row (2). Axial bearing (1) according to one of the preceding claims, characterized in that the first curvature (15), viewed in a longitudinal section along the central axis (19), rises axially convexly curved above a second radial plane (L2) and in the direction of the second radial plane ( L2) is designed to be elastically flexible, the first rolling raceway (10) being axially further away from the second radial plane (L2) than the second rolling raceway (11) and/or the first rolling raceway (10) being axially further away from the second radial plane (L2). is removed than the third rolling raceway (12). Axial bearing (1). Claim 8 , characterized in that the first curvature (15) has the at least one rolling track (10, 11, 12) and also through a front side (20) facing away from the second radial plane (L2) and axially spaced from the second radial plane (L2). a rear side (21) facing away from the front side (20) and facing the second radial plane (L2) is characterized in such a way that both the front side (20) and the back side (21) are located axially above the second radial plane (L2). elevating and convexly elevating courses away from the second radial plane (L2). Axial bearing after Claim 1 or 9 , characterized in that the first axial disk (8) is provided with further curvatures (16, 17, 18), a second curvature (16) of the curvatures (16, 17, 18) being at least on the first rolling track (10) and / or a third curvature (17) is formed on the second rolling raceway (11) and/or a fourth curvature (18) on a third rolling raceway (12). Axial bearing (1) according to one of the preceding claims, characterized in that the axial bearing (1) has the first axial disk (8) and at least one second axial disk (9), at least one row (2, 3, 4) of the rolling elements (5 , 6, 7) are arranged axially between the axially opposite axial disks (8, 9). Axial bearing (1). Claim 11 , characterized in that the first axial disk (8) and the second axial disk (9) are geometrically identical to one another. Axial bearing after Claim 2 , characterized in that all of the rolling elements (5, 6, 7) are arranged in a common cage (22).

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