DE102020103261A1 - Thrust roller bearings - Google Patents

Abstract

The invention relates to an axial rolling bearing (1), comprising a first running disk (2) and a second running disk (3), each of which is circular and spaced from one another around a common axial rolling bearing axis of rotation (4), with between the first running disk (2) and a plurality of rolling elements (5) are arranged on the second running disk (3) and roll on a first rolling element raceway (6) of the first running disk (2) and a second rolling element running path (7) of the second running disk (3), the axial roller bearing (1 ) also has a seal (9) designed as a sealing ring (8) According to the invention, the sealing ring (8) is designed in two parts and comprises a first sealing ring disk (10) and a second sealing ring disk (11), the first sealing ring disk (10) having a first running disk contact surface (12) ), on which a first solid-state lubricant (13) is arranged, and wherein the second sealing ring disk (11) has a second running disk contact surface (14 ), on which a second solid lubricant (13) is arranged, wherein the first sealing ring washer (10) and the second sealing ring washer (11) also have a common ring washer contact surface (15) which is opposite a radial plane (16) of the axial roller bearing (1) an angle (17) is inclined and a third solid lubricant (13) is arranged in the area of the annular disk contact surface (15) on the first sealing washer (10) and / or on the second sealing washer (11).

Description

Field of invention

The invention relates to an axial rolling bearing, comprising a first running disk and a second running disk, each of which is circular and spaced from one another around a common axial rolling bearing axis of rotation, with a plurality of rolling elements arranged on a first rolling element raceway between the first running disk and the second running disk of the first running disk and a second rolling element raceway of the second running disk, the axial rolling bearing also having a seal designed as a sealing ring.

Background of the invention

In general, rolling bearings with predominant axial loads are referred to as axial bearings. In the DE 90 11 029 U1 and in the DE 10 2013 225 996 A1 an exemplary axial bearing is disclosed in each case. The axial bearings usually consist of two running disks, between which rolling elements are arranged.

Agricultural applications, such as in agricultural machines or vehicles such as tractors, pose a particular challenge to such bearings. Due to the ground traveled on, such applications have very challenging load profiles for rolling bearings. At the same time, the ingress of contaminants into the bearing can damage the bearing and lead to premature functional failure.

Object of the invention

In the light of the known prior art, it is therefore the object of the invention to provide an axial roller bearing that is improved in terms of its operational reliability and service life.

Description of the invention

This object is achieved by an axial rolling bearing, comprising a first running disk and a second running disk, each of which is circular and spaced from one another around a common axial rolling bearing axis of rotation The first rolling element raceway of the first running disk and roll on a second rolling element raceway of the second running disk, the axial roller bearing also having a seal designed as a sealing ring, the sealing ring being designed in two parts and comprising a first sealing ring disk and a second sealing ring disk, the first sealing ring disk having a first running disk contact surface , on which a first solid lubricant is arranged, and wherein the second sealing ring washer has a second raceway contact surface on which a second solid lubricant is arranged, the first Sealing ring disk and the second sealing ring disk also have a common ring disk contact surface which is inclined at an angle with respect to a radial plane of the axial roller bearing and a third solid lubricant is arranged in the area of the ring disk contact surface on the first sealing ring disk and / or the second sealing ring disk.

This configuration makes it possible for the first sealing ring disk to be displaceable in the radial direction with respect to the second sealing ring disk, so that corresponding tolerances or an offset during operation of the axial roller bearing can be compensated without the contact on the running disk contact surfaces or the ring disk contact surface being canceled. In this way, the sealing effect of the seal is guaranteed even with radial clearance compensation. Furthermore, the sealing ring disks can be adjusted even if the solid lubricants wear out, so that the sealing effect is further improved here as well. This will be explained in more detail below.

First, the individual elements of the claimed subject matter of the invention are explained in the order in which they are named in the set of claims and particularly preferred embodiments of the subject matter of the invention are described below.

If the forces to be absorbed by a roller bearing do not act radially, but in the direction of the axis of rotation of a component, one speaks of axial forces. Axial roller bearings are configured, in particular, to divert axial forces and to enable a relative rotation of two components that are coupled via the axial roller position about an axis of rotation with as little friction as possible. Axial roller bearings can also have the function of preventing a component coupled to the axial roller bearing from being displaced in the axial direction, as a result of which the component, such as a shaft, can be axially fixed.

For this purpose, rolling rolling bodies are arranged between a first running disk and a second running disk of the axial roller bearing. Between these three main components, the first running disk, the second running disk and the rolling elements, mainly rolling friction usually occurs within the axial rolling bearing. Since the rolling elements on the first and second running disks can preferably roll on hardened steel surfaces with optimized lubrication, the rolling friction of such bearings is relatively low.

The first running disk can in particular connect the first component to be supported by the axial roller bearing to the axial roller bearing or the roller bodies. In particular, the first component can be coupled to the end face of the first running disk facing the first component, the first rolling element raceway on which the rolling elements of the axial rolling bearing roll being arranged on the end face opposite this end face. The first running disk can in particular be designed in the shape of a circular ring. The first running disk can be formed from a metallic and / or ceramic material.

The second running disk can, in particular, connect the second component to be supported by the axial roller bearing to the axial roller bearing or the roller bodies. In particular, the second component can be coupled to the end face of the second running disk facing the second component, the second rolling element raceway on which the rolling elements of the axial rolling bearing roll being arranged on the end face opposite this end face. The second running disk can in particular be designed in the shape of a circular ring. The second running disk can be formed from a metallic and / or ceramic material.

The rolling elements have the shape of a ball or a roller, depending on the type of rolling bearing. They roll on the raceways of the rolling bearing and have the task of transmitting the force acting on the axial rolling bearing from the first running disk to the second running disk and vice versa. Roller-shaped rolling bodies are also referred to as roller-rolling bodies and spherical rolling bodies as bearing balls.

The rolling elements can roll within the axial rolling bearing, in particular on the first rolling element raceway of the first running disk. For this purpose, the surface of the first rolling element raceway can advantageously be made correspondingly wear-resistant, for example also by means of a corresponding surface treatment method and / or by applying a corresponding additional material layer.

The first rolling element raceway can be flat or profiled. A profiled configuration of the first rolling element raceway can be used, for example, to guide the rolling elements on the first rolling element raceway. By contrast, a planar formation of the first rolling element raceway can allow, for example, a certain radial displaceability of the rolling elements on the first rolling element raceway.

The rolling elements can roll within the axial rolling bearing, in particular on the second rolling element raceway of the second running disk. For this purpose, the surface of the second rolling element raceway can advantageously be made correspondingly wear-resistant, for example also by means of a corresponding surface treatment method and / or by applying a corresponding additional material layer.

The second rolling element raceway can be flat or profiled. A profiled configuration of the second rolling element raceway can be used, for example, to guide the rolling elements on the second rolling element raceway. By contrast, a planar formation of the second rolling element raceway can allow, for example, a certain radial displaceability of the rolling elements on the second rolling element raceway.

A thrust roller bearing according to the invention has a seal in order to prevent lubricant from escaping from the thrust roller bearing or the entry of dirt or moisture into the thrust roller bearing.

An axial roller bearing can have a cage, the cage guiding the rolling elements. The cage is designed in such a way that the bearing balls and / or the roller rolling elements are spaced apart from one another so that, for example, the friction and heat development of the rolling elements is kept as low as possible. Furthermore, the cage keeps the rolling element balls and / or rolling element rollers at a uniform distance from one another, as a result of which a uniform load distribution can be achieved. The cage can be made in one piece or in several pieces.

According to a preferred embodiment of the invention, it can be advantageous that the solid lubricant is a PTFE. In particular, PTFE has low coefficients of friction and good service life with a view to its use in axial roller bearings. In addition, due to the low friction, the PTFE solid-state lubricant enables a high-speed application of a correspondingly designed axial roller bearing.

It can furthermore be advantageous that the first sealing ring washer and / or the second sealing ring washer are made of a metallic material, in particular steel. As a result, the sealing ring disks can on the one hand be produced in an extremely dimensionally stable and cost-effective manner.

In a further development of the invention, it can furthermore be preferred that the angle at the annular disk contact surface with respect to the radial plane is between 0.5 and 5 degrees, preferably between 1 and 3 degrees. It has been shown that the tolerance compensation and the tightness of the sealing ring are particularly advantageous at this angular degree interval.

Furthermore, it can be advantageous for the first running disk contact surface of the first sealing ring disk and / or the second running disk contact surface of the second sealing ring disk to be formed on an inner running disk surface.

According to a further advantageous embodiment of the invention, it can be preferred that the first running disk and / or the second running disk has a shoulder protruding axially out of the running disk, on which the corresponding sealing ring disk rests in the radial direction, whereby a running disk radially into the interior of the Thrust roller bearing 1 pointing direction is held in a defined stop position.

According to a preferred embodiment of the invention, it can be advantageous that the shoulder is designed like a ramp and preferably has a ramp angle of X-Y degrees with respect to an axial bearing plane.

It can also be advantageous that the solid lubricant that forms the first rotor disk contact surface and / or the second rotor disk contact surface has a layer thickness that corresponds to 1.5 to 3 times the layer thickness of the solid lubricant that forms the annular disk contact surface. It has been shown that, on the one hand, this allows the amount of solid lubricant used to be optimized with a view to wear and tear and the service life of the solid lubricant.

In a further development of the invention, it can furthermore be preferred that the sealing ring is arranged completely within the axial roller bearing, as a result of which a particularly compact design of the axial roller bearing can be implemented.

Furthermore, it can be advantageous that the solid lubricant rests over the entire surface of the first rotor disk contact surface and / or the second rotor disk contact surface and / or the annular disk contact surface, as a result of which particularly low friction can be set.

Figure list

• 1 eine Ausführungsform des erfindungsgemäßen Axialwälzlagers in einer Querschnittsansicht,
• 2 eine Ausführungsform des erfindungsgemäßen Axialwälzlagers in einer perspektivischen Explosionsquerschnittsansicht, und
• 3 eine Detailansicht des Dichtrings in einer schematischen Querschnittsdarstellung.

The invention is explained in more detail below with reference to drawings without restricting the general inventive concept. The drawings are only of a schematic nature and are used solely for understanding the invention. The same elements are provided with the same reference symbols. The different features of the various exemplary embodiments can also be freely combined with one another within what is technically feasible. Show it:

• 1 an embodiment of the axial roller bearing according to the invention in a cross-sectional view,
• 2 an embodiment of the axial roller bearing according to the invention in a perspective exploded cross-sectional view, and
• 3 a detailed view of the sealing ring in a schematic cross-sectional illustration.

Detailed description of the drawings

the 1 shows a thrust roller bearing 1 comprising a first pulley 2 and a second pulley 3 , each of which is circular and spaced from one another around a common axis of rotation of the axial roller bearing 4th are arranged, between the first running disk 2 and the second pulley 3 a plurality of rolling elements 5 are arranged on a first rolling element raceway 6th the first pulley 2 and a second rolling element raceway 7th the second pulley 3 rolling, the axial rolling bearing 1 also one as a sealing ring 8th trained seal 9 having, the sealing ring 8th Is formed in two parts and a first sealing ring washer 10 and a second sealing ring washer 11 comprises, wherein the first sealing ring washer 10 a first pulley contact surface 12th has, on which a first solid lubricant 13th is arranged, and the second sealing ring washer 11 a second pulley contact surface 14th has on which a second solid lubricant 13th is arranged, the first sealing ring washer 10 and the second sealing ring washer 11 also a common washer contact surface 15th have opposite a radial plane 16 of the axial roller bearing 1 at an angle 17th is inclined and in the area of the washer contact surface 15th on the first sealing washer 10 and / or the second sealing ring washer 11 a third solid lubricant 13th is arranged.

the 1 also shows that the sealing ring 8th completely within the thrust roller bearing 1 is arranged.

the 2 shows that 1 known axial roller bearings in a cross-sectional exploded view. You can clearly see the first running disc again 2 and the second washer 3 , each of which is circular and spaced from one another around a common axis of rotation of the axial roller bearing 4th are arranged. Between the first pulley 2 and the second pulley 3 is a plurality of rolling elements 5 arranged on a first rolling element raceway 6th the first pulley 2 and a second rolling element raceway 7th the second pulley 3 roll over. The rolling elements 5 are in a cage 20th recorded and within the Thrust roller bearing 1 guided spaced from each other in cage pockets. The axial roller bearing 1 also has a sealing ring 8th trained seal 9 on, with the sealing ring 8th Is formed in two parts and a first sealing ring washer 10 and a second sealing ring washer 11 includes.

Based on 3 it can be seen that the first sealing ring washer 10 a first pulley contact surface 12th owns, on which a first solid lubricant 13th is arranged. The second sealing washer 11 analogous to this, has a second rotor disk contact surface 14th , on which a second solid lubricant 13th is arranged. The first sealing washer 10 and the second sealing ring washer 11 also have a common washer contact surface 15th facing a radial plane 16 of the axial roller bearing 1 at an angle 17th is inclined. In the area of the washer contact surface 15th is on the first sealing washer 10 and / or the second sealing ring washer 11 a third solid lubricant 13th arranged. This will follow in particular with the aid of 3 will be explained in more detail.

The solid lubricants 13th are formed from a PTFE in the example shown. The solid lubricants 13th are in the example shown PTFE foils, preferably self-adhesive PTFE foils.

The first sealing washer 10 and the second sealing ring washer 11 consist of a metallic material, in particular steel.

The angle 17th at the washer contact surface 15th is opposite the radial plane 16 between 0.5 and 5 degrees, preferably between 1 and 3 degrees. This can cause a radial offset of the sealing ring disks 10 , 11 be balanced to each other, as the sealing ring washers 10 , 11 on the angled washer contact surface 15th can slide along.

the 3 also shows that the first pulley contact surface 12th the first sealing washer 10 and the second pulley contact surface 14th the second sealing washer 11 is formed in each case on an inner, radially extending running disk surface.

The first running disc 2 and the second washer 3 each have a shoulder protruding in the axial direction from the respective running disk 2, 3 18th on which the respective sealing ring washer 10 , 11 is applied in the radial direction.

That shoulder 18th is designed like a ramp and has a ramp angle 19th from 35 to 55 angular degrees, preferably 45 angular degrees, based on an axial bearing plane, which is indicated by the dash-dot line.

The solid lubricant 13th , which is the first contact surface of the raceway 12th and second race contact surface 14th is formed, in particular has a layer thickness that is 1.5 to 3 times the layer thickness of the solid lubricant 13th corresponds to that of the washer contact surface 15th trains. The solid lubricant 13th lies over the entire surface of the first contact surface of the pulley 12th and the second pulley contact surface 14th and the washer pad 15th on.

The one from the sealing washers 10 , 11 formed sealing ring 8th is completely within the thrust roller bearing 1 arranged.

The invention is not limited to the embodiments shown in the figures. The above description is therefore not to be regarded as restrictive, but rather as explanatory. The following patent claims are to be understood in such a way that a named feature is present in at least one embodiment of the invention. This does not exclude the presence of further features. If the patent claims and the above description define “first” and “second” features, this designation serves to distinguish between two similar features without defining an order of precedence.

List of reference symbols

1

Thrust roller bearings

2

first running disc

3

second washer

4th

Axial roller bearing axis of rotation

5

Rolling elements

6th

first rolling element career

7th

second rolling element raceway

8th

Sealing ring

9

poetry

10

first sealing washer

11

second sealing washer

12th

first race contact surface

13th

Solid lubricant

14th

second pulley contact surface

15th

Washer contact surface

16

Radial plane

17th

angle

18th

shoulder

19th

Ramp angle

20th

Cage

QUOTES INCLUDED IN THE DESCRIPTION

This list of the 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.

Patent literature cited

• DE 9011029 U1 [0002]
• DE 102013225996 A1 [0002]

Claims (10)

Axial roller bearing (1), comprising a first running disk (2) and a second running disk (3), each of which is circular and spaced apart from one another around a common axial rolling bearing axis of rotation (4), wherein between the first running disk (2) and the second running disk ( 3) a plurality of rolling elements (5) are arranged, which roll on a first rolling element raceway (6) of the first running disk (2) and on a second rolling element running path (7) of the second running disk (3), the axial roller bearing (1) also having a has a seal (9) designed as a sealing ring (8), characterized in that the sealing ring (8) is designed in two parts and comprises a first sealing ring disk (10) and a second sealing ring disk (11), the first sealing ring disk (10) having a first running disk contact surface (12) on which a first solid lubricant (13) is arranged, and wherein the second sealing ring disk (11) has a second running disk contact surface (14) eist, on which a second solid lubricant (13) is arranged, the first sealing ring washer (10) and the second sealing ring washer (11) also have a common ring washer contact surface (15) which is around a radial plane (16) of the axial roller bearing (1) Angle (17) is inclined and a third solid lubricant (13) is arranged in the area of the annular disk contact surface (15) on the first sealing ring washer (10) and / or on the second sealing ring washer (11). Axial roller bearings, according to Claim 1 , characterized in that the solid lubricant (13) is a PTFE. Axial roller bearing according to one of the preceding claims, characterized in that the first sealing ring washer (10) and / or the second sealing ring washer (11) are made of a metallic material, in particular steel. Axial roller bearing according to one of the preceding claims, characterized in that the angle (17) on the annular disk contact surface (15) with respect to the radial plane (16) is between 0.5 and 5 degrees, preferably between 1 and 3 degrees. Axial roller bearing according to one of the preceding claims, characterized in that the first running disk contact surface (12) of the first sealing ring disk (10) and / or the second running disk contact surface (14) of the second sealing ring disk (11) is formed on an inner running disk surface. Axial roller bearing according to one of the preceding claims, characterized in that the first running disk (2) and / or the second running disk (3) has a shoulder (18) which protrudes axially out of the running disk and on which the corresponding sealing ring disk (10, 11 ) is applied in the radial direction. Axial roller bearings, according to Claim 6 , characterized in that the shoulder (18) is designed like a ramp and preferably has a ramp angle (19) of 35 to 55 angular degrees, preferably 46 angular degrees, based on an axial bearing plane. Axial roller bearing according to one of the preceding claims, characterized in that the solid lubricant (13) which forms the first rotor disk contact surface (12) and / or the second rotor disk contact surface (14) has a layer thickness which is 1.5 to 3 times the layer thickness of the solid lubricant (13) ) corresponds to which forms the annular disk contact surface (15). Axial roller bearing according to one of the preceding claims, characterized in that the sealing ring (8) is arranged completely within the axial roller bearing (1). Axial roller bearing according to one of the preceding claims, characterized in that the solid-state lubricant (13) is in full contact with the first rotor disk contact surface (12) and / or the second rotor disk contact surface (14) and / or the annular disk contact surface (15).

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