阅读说明：本技术 密封的滚动轴承和用于运行滚动轴承的方法 (Sealed rolling bearing and method for operating a rolling bearing ) 是由 托马斯·诺盖拉·达·西尔瓦 惠灵顿·阿德里亚诺·费雷拉·桑托斯 法比奥·路易斯·维埃拉 于 2018-11-09 设计创作，主要内容包括：本发明涉及滚动轴承(1),其具有密封件(6),该密封件包括紧固在第一轴承圈(2)上的金属的止推盘(7)和紧固在第二轴承圈(3)上的密封盘(10),密封盘具有金属的加固圈(12)和至少有一个密封唇(13、14)。止推盘(7)以及加固圈(12)具有以金属对金属接触的形式与负荷有关地彼此协同作用的隆起部(17、19)。(The invention relates to a rolling bearing (1) having a seal (6) which comprises a metallic thrust disk (7) fastened to a first bearing ring (2) and a sealing disk (10) fastened to a second bearing ring (3), said sealing disk having a metallic reinforcing ring (12) and at least one sealing lip (13, 14). The thrust disk (7) and the reinforcing ring (12) have elevations (17, 19) which cooperate with one another in a load-dependent manner in the form of a metal-to-metal contact.)

1. Rolling bearing (1) having a seal (6) comprising a metallic thrust disk (7) fastened to a first bearing ring (2) and a sealing disk (10) fastened to a second bearing ring (3), which sealing disk has a metallic reinforcing ring (12) and at least one sealing lip (13, 14), characterized in that the thrust disk (7) and the reinforcing ring (12) have elevations (17, 19) which cooperate with one another in load-dependent manner in the form of a metal-to-metal contact.

2. Rolling bearing (1) according to claim 1, characterized in that the elevations (17, 19) are configured as granular protrusions.

3. Rolling bearing (1) according to claim 1 or 2, wherein at least twelve ridges (17, 19) are distributed on the circumference of the thrust disc (7) and of the reinforcing ring (12), respectively.

4. Rolling bearing (1) according to any of claims 1 to 3, characterized in that the seal (6) is configured in such a way that the thrust disk (7) is completely spaced apart from the reinforcing ring (12) in the unloaded state.

5. Rolling bearing (1) according to any of claims 1 to 4, characterized in that said thrust disc (7) is located on the inside of said seal (6).

6. Rolling bearing (1) according to claim 5, wherein the sealing disc (10) has two sealing lips (13, 14), wherein at least in the state of mechanical load establishing metal-to-metal contact between the thrust disc (7) and the reinforcing ring (12), one of the sealing lips (14) is in contact with the thrust disc (7) and the second sealing lip (13) is in contact only with the bearing ring (2).

7. Rolling bearing (1) according to any of claims 1 to 6, characterized in that said reinforcing ring (12) has a smaller wall thickness (W2) than said thrust disc (7).

8. Rolling bearing (1) according to any of claims 1 to 7, characterized in that it is configured as a double row ball bearing.

9. Method for operating a rolling bearing (1) having two bearing rings (2, 3) between which a seal (6) acts, wherein a metallic thrust disk (7) is held on a first bearing ring (2) and a sealing disk (10) having a metallic reinforcing ring (12) is held on a second bearing ring (3), having the following features:

-in an operating state of the rolling bearing (1) with low mechanical load, the bearing rings (2, 3) rotate relative to each other, wherein the thrust disk (7) does not contact the reinforcing ring (12),

-in an operating state with high mechanical load, the fixing ring (12) contacts the thrust disk (7) in such a way that an oscillating relative movement is generated between the fixing ring (12) and the thrust disk (7) by the shape of the fixing ring (12) and the thrust disk (7), the frequency of the oscillating relative movement being higher than the rotational speed of the rolling bearing (1).

10. Method according to claim 9, characterized in that the oscillations forcibly generated in the rolling bearing (1) by the contact between the thrust disk (7) and the reinforcing ring (12) are mainly oriented in the axial direction of the rolling bearing (1).

Technical Field

The invention relates to a rolling bearing having at least one seal according to the preamble of claim 1. The invention also relates to a method for operating a sealed rolling bearing.

Background

Rolling bearings of this type are known, for example, from DE 102014208691 a 1. The seal of the rolling bearing comprises a race, also commonly referred to as a thrust disk, which is retained on one of the bearing rings of the rolling bearing. Furthermore, the seal comprises a sealing ring which is fastened to a further bearing ring of the rolling bearing. The sealing ring, i.e. the sealing disk, has a metallic carrier ring and a plurality of sealing lips made of an elastomer material.

In principle, the design of seals is also known as box seals. In this connection, reference is made, by way of example, to documents DE 102012207688A 1, DE 102012204620A 1, WO 2015/120831A1 and EP 1963697B 1.

A sealed bearing arrangement for an agricultural implement is disclosed, for example, in DE 102012207848 a 1. In this case, the bearing element is designed as a two-row ball bearing.

Disclosure of Invention

The object of the invention is to improve the bearing component in relation to the prior art described above, which is particularly suitable for use in agricultural implements.

According to the invention, this object is achieved by a rolling bearing having the features of claim 1. This object is also achieved by a method for operating a rolling bearing according to claim 9. In the following, the embodiments and advantages of the invention explained in connection with the operating method are also applicable to the device, that is to say the rolling bearing, in a meaningful manner, and vice versa.

In a basic concept known per se, a rolling bearing has at least one seal which comprises a thrust disk made of metal fastened to a first bearing ring and a sealing disk fastened to a second bearing ring of the rolling bearing, wherein the sealing disk has a metallic reinforcement and at least one sealing lip made of an elastomer material. According to the invention, the thrust disk and the reinforcement have ridges which cooperate with one another in a metal-to-metal contact in a manner dependent on the mechanical loads to which the rolling bearing is subjected. In particular, in operating phases with high mechanical loads, with respect to a specific load direction, there is at least a temporary contact between the thrust disk and the reinforcement, while in other operating phases the thrust disk is completely spaced apart from the reinforcement. The contact between the thrust disk and the reinforcement which occurs under these defined operating conditions leads in particular to intentional vibrations occurring in these operating phases. Due to these forced vibrations, dirt is deposited and loosened, so that dirt cannot enter the inner space of the rolling bearing and the function of the seal is maintained without restriction. In a typical application, the total duration of those operating phases in which the thrust disk contacts the reinforcing member is significantly shorter than the operating time in which there is no contact between the thrust disk and the reinforcing member. The forced metal-to-metal contact between the thrust disk and the reinforcement therefore has at most a secondary influence on the friction of the rolling bearing.

According to a possible embodiment, both the thrust disk and the elevations of the reinforcement are embodied as granular projections. The granular projections of a ring are preferably oriented in the direction of the other ring. This means that in the event of contact between the thrust disk and the reinforcing member, the elevations of the thrust disk, which are configured as granular projections, come into contact with the elevations of the reinforcing member, which are likewise configured as granular projections. Preferably, at least twelve ridges are distributed on the circumference of the thrust disk and the circumference of the reinforcing member, respectively.

The seal of the rolling bearing is preferably designed in such a way that the thrust disk is completely spaced apart from the reinforcement in the unloaded state. Thus, in this state, there is no metal-to-metal contact between the two relatively moving parts of the seal. In addition, the seal is preferably a touch seal.

In a preferred embodiment, the thrust disk is located on the inner side of the seal, i.e. on the side of the seal facing the rolling bodies. The sealing disk preferably has two sealing lips, wherein, at least in some of the possible operating states, in particular under mechanical load, one of the sealing lips contacts the thrust disk, while the other sealing lip contacts only one of the bearing rings.

Both the thrust disk and the reinforcement can be manufactured reasonably as sheet metal. In this case, the elevations, in particular in the form of granular projections, can be produced in a single method step together with the shaping of the respective annular component, that is to say of the thrust disk or of the reinforcing element. In a preferred embodiment, the wall thickness of the reinforcement element is smaller than the wall thickness of the thrust disk.

The rolling bearing can have any desired shape of the rolling elements, for example rollers, needles or balls, and any desired number of rows of rolling elements. The rolling bearing is, for example, a double-row ball bearing. In a preferred embodiment, the rolling bearing is provided primarily for transmitting radial forces.

Regardless of the type and arrangement of the rolling elements, the rolling bearing can be used in the following operating states:

in an operating state of the rolling bearing with low mechanical loading, the bearing rings rotate relative to one another, wherein the thrust disk does not touch the reinforcement,

in an operating state with increased mechanical load, the reinforcement element is in contact with the thrust disk in such a way that, due to the shape of the reinforcement element and the thrust disk, an oscillating relative movement is produced between the reinforcement element and the thrust disk, the frequency of the oscillating relative movement being higher than the rotational speed of the rolling bearing.

If the rolling bearing is a radial bearing, the oscillations which are forced in the rolling bearing by the contact between the thrust disk and the reinforcement are preferably oriented predominantly in the axial direction of the rolling bearing. The operating state in which the contact of the reinforcing ring with the thrust disk takes place can be generated in this case by axial forces between the bearing rings.

Rolling bearings are particularly suitable for use in agricultural machinery. The agricultural machine may be a mobile machine or a stationary machine. Rolling bearings can also be used in industrial installations, in particular in areas with high levels of contamination.

Drawings

Embodiments of the present invention are explained in more detail below with reference to the accompanying drawings. Wherein:

figure 1 shows a rolling bearing in a sectional view;

fig. 2 and 3 show details of the rolling bearing in different operating states;

fig. 4 shows the rolling bearing in an exploded view;

fig. 5 shows the rolling bearing in a perspective view;

figures 6 to 8 show the thrust disk of the seal of the rolling bearing;

fig. 9 shows a schematic sectional illustration of a thrust disk of a seal of a rolling bearing and a reinforcement in sections.

Detailed Description

The rolling bearing, which is designated as a whole by reference numeral 1, is a double-row ball bearing. The ball bearing 1 comprises two bearing rings 2, 3, i.e. an inner ring 2 and an outer ring 3, between which balls 4 roll and which are guided in a cage 5. Furthermore, the rolling bearing 1 also comprises a seal 6, which will be discussed in more detail below. In the exemplary embodiment, the seal 6 is located on exactly one end face of the rolling bearing 1. Likewise, a correspondingly designed seal 6 can be located on the second end side.

The seal 6 comprises a thrust disk 7 which is retained on the inner ring 2. The thrust disk 2 is made of sheet metal and has, in its cross section, a bent shape, as is evident in particular from fig. 2 and 3. The disk section 8 of the thrust disk 7 lies substantially in a plane which is oriented perpendicularly to the central axis of the rolling bearing 1. Adjoining the inner edge of the disk section 8 is a rib 9, which is described as cylindrical in shape. The rib 9 rests against an annularly encircling shoulder 16 of the inner ring 2. The shoulder 16 borders an annular groove 18, the width of which, measured in the axial direction, is smaller than the width of the rib 9, measured in the same direction. The collar 9 rests on the outer circumferential surface of the inner ring 2 outside the annular groove 18. The disc segment 8 adjoining the rib 9 extends over the majority of the annular gap formed between the outer circumferential surface of the inner ring 2 and the inner circumferential surface of the outer ring 3, but does not come into contact with the outer ring 3 in any operating state.

The thrust disk 7 is located on the inner side of the seal 6, that is to say on the side of the seal 6 facing the rolling bodies 4. The sealing disk 10 held in the groove 15 in the outer ring 3 serves as the outer part of the seal 6, i.e. the part facing the end faces of the bearing rings 2, 3. In contrast to the thrust disk 7, the seal disk 10 is a member including a plurality of materials. The carrier ring 12 of the sealing disk 10, also referred to as reinforcement, is made of a metal sheet material, as is the thrust disk 7. The reinforcement 12 is firmly connected to the elastomer ring 11 with the two sealing lips 13, 14.

The cooperation between the thrust disk 7 on the one hand and the sealing disk 10 on the other hand depends on the degree of axial force acting between the bearing rings 2, 3. Such axial forces are clearly indicated by arrows in fig. 2. Axial forces which may occur during operation of the roller bearing 1, which is designed primarily as a radial bearing, cause the thrust disk 7 to contact the reinforcement 12. Here, the granular protrusions 17 distributed over the circumference of the disc segments 8 are in contact with the granular protrusions 19 distributed over the circumference of the reinforcement 12 in a similar manner. The different granular projections 17, 19 are here directed towards each other so that in the case of contact of the thrust disk 7 with the reinforcement 12, the two convex profiles formed by the granular projections 17, 19 collide with each other. In the embodiment, the thrust disk 7 has a total of thirty granular protrusions 17. The stiffener 12 has thirty granular projections 19 in a similar design. The granular projections 17, 19 are therefore spaced apart from one another at an angle of 12 ° on the thrust disk 7 or on the reinforcement 12, respectively. The granular projections 20 are visible on the elastomer ring 11, the shape of which matches the shape of the granular projections 19.

In the operating state according to fig. 2, the sealing lip 13 contacts only the inner ring 2, while the sealing lip 14 contacts the inner ring 2 and the thrust disk 7. A total of sixty granular protrusions 17, 19 of the thrust disk 7 and of the reinforcement 12 ensure that rotation of the inner ring 2 relative to the outer ring 3 results in a rapidly oscillating axial movement between the bearing rings 2, 3. The frequency of this rapid oscillating axial movement is many times higher than the rotational speed of the roller bearing 1, in Hz in each case. If dirt is carried on the seal 6, the forced oscillation will clean it from the seal 6. Therefore, the possibility of dirt intruding into the inner space of the rolling bearing 1 or damaging the seal 6 is greatly reduced compared to conventionally constructed seals.

Details of the thrust disk 7 and the reinforcement 12 can be taken from fig. 9. The tangential direction in which the thrust disk 7 moves relative to the reinforcement member 12 is here denoted TR. The wall thickness of the thrust disk 7, designated by W1, is greater than the wall thickness of the reinforcement 12, designated by W2, and the operating state of the rolling bearing 1 according to fig. 9 corresponds to the state shown in fig. 3. In this case, the reinforcement element 12 is completely lifted off the thrust disk 7, so that no vibrations are generated by the sealing element 6. This operating state is assumed for the most part of the total operating time of the rolling bearing 1.

List of reference numerals

Rolling bearing and ball bearing

2 inner ring

3 outer ring

4 rolling element, ball

5 holding rack

6 sealing element

7 metal disc, thrust disc

8 disc segment

9 Flange

10 sealing disc

11 elastic body ring

12 bearing ring and reinforcing ring

13 sealing lip

14 sealing lip

15 groove

16 convex shoulder

17 raised part, granular protrusion

18 ring groove

19 raised part and granular protrusion

20 raised part

Direction of tangent of TR

W1, W2 wall thickness