阅读说明：本技术 无保持架的滚动轴承 (Rolling bearing without retainer ) 是由 E·福施贝克 于 2020-03-30 设计创作，主要内容包括：本发明涉及一种无保持架的滚动轴承(1),其具有：多个滚动体(4),所述多个滚动体在内圈(2)和与内圈(2)同心布置的外圈(3)之间在周向方向上分布地布置；和压紧元件(6),该压紧元件以环形段的方式沿着周向方向布置,至少暂时地同时接触所述滚动体(4)中的至少两个,并且对被接触的滚动体(4)中的每个施加在轴向方向上定向的力。(The invention relates to a cage-free rolling bearing (1) comprising: a plurality of rolling bodies (4) which are arranged distributed in the circumferential direction between the inner ring (2) and an outer ring (3) which is arranged concentrically to the inner ring (2); and a pressing element (6) which is arranged in an annular segment manner along the circumferential direction, at least temporarily contacts at least two of the rolling bodies (4) at the same time, and applies a force oriented in the axial direction to each of the contacted rolling bodies (4).)

1. A cage-less rolling bearing (1) comprising:

-a plurality of rolling bodies (4) arranged dispersed in a circumferential direction between an inner ring (2) and an outer ring (3) arranged concentrically to the inner ring (2); and

-a pressing element (6) which:

_○arranged in circumferential direction in the manner of annular segments,

_○at least temporarily simultaneously contacting at least two of the rolling bodies (4), and

_○a force directed in the axial direction is applied to each of the contacted rolling elements (4).

2. Rolling bearing (1) without cage according to claim 1, wherein the pressing element (6) has a pressing tongue (7) which is supported in a first end region (7a), the second end region (7b) of which is designed as an unsupported end.

3. Rolling bearing without cage (1) according to claim 2, wherein the second end region (7b) of the pressing tongue (7) is designed as an unsupported end.

4. Rolling bearing without cage (1) according to claim 2 or 3, wherein the second end region (7b) of the pressing tongue (7) is fixed in an elastically bendable manner.

5. Rolling bearing without cage (1) according to any of claims 2 to 4, wherein the cross section of the pressing tongue (7) tapers from the first end region (7a) to the second end region (7 b).

6. Rolling bearing without cage (1) according to any of claims 2 to 5, wherein a chamfered starting region (7c) is formed in the first end region (7 a).

7. Rolling bearing without cage (1) according to any of claims 2 to 6, wherein a chamfered end zone (7d) is formed in the second end zone (7 b).

8. Rolling bearing without cage (1) according to any of claims 2 to 7, wherein the pressing tongue (7) is arched.

9. Rolling bearing without cage (1) according to claim 1, wherein the pressure element (6) is designed as a seesaw-shaped pressure element which is supported in a middle region and is either fixed in an elastically bendable manner or unsupported at both end regions.

10. Rolling bearing without cage (1) according to any of the preceding claims, wherein the rolling bearing (1) is closed in axial direction by an annular cover plate (5), the pressing element (6) being mounted on the cover plate (5).

11. Rolling bearing without cage (1) according to any of the preceding claims, wherein a pressing element (7) contacts at most two of the rolling bodies (4) simultaneously.

12. Rolling bearing without cage (1) according to any of claims 1 to 10, wherein a pressing element (7) contacts at most three of the rolling bodies (4) simultaneously.

13. Rolling bearing without cage (1) according to any of the preceding claims, wherein a plurality of pressing elements (6) are distributed equidistantly on the peripheral side.

14. Rolling bearing (1) without cage according to any of the preceding claims, wherein the rolling bearing (1) is an angular contact ball bearing.

Technical Field

The present invention relates to a rolling bearing without a cage.

Background

Typically, rolling bearings for applications where relatively high rotational speeds (rotational speed characteristic n x dm > 10000mm/min) are to be expected are equipped with a bearing cage in which the rolling elements (balls/balls, rollers) of the rolling bearing are accommodated. An economical service life and uniform operation can be achieved by such a bearing cage. Furthermore, the bearing cage ensures a uniform spacing of the rolling bodies from one another and prevents the rolling bodies from making a contact which is disadvantageous in terms of friction during operation of the rolling bearing.

Rolling bearings without bearing cages are also known. These rolling bearings are also referred to as cage-free rolling bearings. The advantage of such a cage-free roller bearing is, for example, that, by eliminating the bearing cage, more rolling bodies can be present while maintaining the same size of the roller bearing, which in turn increases the load-bearing capacity of the roller bearing. Such rolling bearings are also referred to as cage-free ball bearings. However, the above-described advantages of a rolling bearing with a bearing cage are not provided in the known cage-free rolling bearings. The elimination of the bearing cage leads to problems, in particular at high rotational speeds. This may result in a change in the spacing between the individual rolling elements until contact occurs between these rolling elements. This undesired contact in turn increases the wear and shortens the service life of the rolling bearing.

Disclosure of Invention

The object of the invention is to provide a cage-free roller bearing which prevents as far as possible contact between adjacent roller bodies during operation of the roller bearing.

This object is achieved by the features of claim 1. Advantageous embodiments are described in the dependent claims.

The cage-less rolling bearing according to the invention has a plurality of rolling bodies which are arranged in a distributed manner in the circumferential direction between an inner ring and an outer ring which is arranged concentrically to the inner ring, and a pressure element. The pressing element is arranged in the circumferential direction in the manner of a ring segment, temporarily contacts at least two of the rolling bodies at the same time, and exerts a force directed in the axial direction on each of the contacted rolling bodies.

The term "axial direction" relates to the axial direction of the concentrically arranged inner and outer rings of the rolling bearing. Furthermore, the expression "force directed in the axial direction" is to be understood such that the orientation of the rolling elements exerted by the pressure element has a directional component in the axial direction; thus, not only the precise axial force falls within this definition, but also forces which, in addition to an axial direction component, for example also have a radial direction component.

During operation of the rolling bearing, the pressing elements have a compensating effect on the spacing between adjacent rolling bodies. If, for example, the distance between the preceding rolling element and the following rolling element is smaller than the theoretical distance that would be produced on the basis of an equidistant distribution of the rolling elements, the braking effect of the pressure element on the preceding rolling element is smaller. The spacing between the rolling elements increases accordingly. If, on the other hand, the distance between the preceding rolling element and the following rolling element is greater than the theoretical distance, the braking effect of the pressure element on the preceding rolling element is greater. The spacing between the rolling elements is correspondingly reduced.

The distance between the individual rolling elements is therefore set to the theoretical distance. In this way, contact between adjacent rolling bodies during operation of the rolling bearing is prevented as far as possible. The service life of the rolling bearing is correspondingly increased, and a rolling bearing without a cage is also particularly suitable for high-speed applications.

In an advantageous embodiment, the pressing element is fixed or stationary in this case. In rolling bearings, usually, the inner or outer ring is stationary, while the respective other ring rotates at the speed required according to the application. The rolling bodies roll on the respective running surfaces of the inner ring and the outer ring during operation. Furthermore, other components of the rolling bearing, such as a cover plate, for example (decksheibe), can be present, which are also usually stationary. Fixed or stationary means now that the pressure element is fixedly connected to one of the stationary elements of the rolling bearing (for example a stationary ring, a cover plate or an adjacent component). Thus causing a relative movement of the rolling bodies with respect to the pressing element. During the rotational movement of the rolling bearing, all the rolling bodies are therefore in contact with the pressing element in succession. An advantage of designing the pressing element as a stationary or stationary pressing element is that it can be controlled relatively easily from a technical point of view.

However, the pressing element can also be designed as a rotating pressing element. The pressure element is mounted on a rotating element of the rolling bearing, for example on a rotating ring. Since the rolling element groups are usually surrounded by the outer ring and the inner ring at a substantially moderate rotational speed, almost the same relative movement between the rolling element groups and the pressure elements takes place and the operating principle of the pressure elements is almost the same.

In other words, the pressure element assumes the function of adjusting the rotational-side spacing of the rolling elements in such a way that the rotational speed of the rolling elements is influenced locally by applying a specific force. This is achieved in that the pressure element is designed in terms of its elasticity and the elasticity is adjusted in such a way that different force distributions on the preceding rolling element and the following rolling element are adjusted as a function of the distance between the following rolling element and the preceding rolling element. For example, the contact force between the pressure element and the rolling elements causes a reduction in the rotational speed of the rolling elements in that the force direction is oriented axially opposite to the supporting shoulder of the inner ring or opposite to the supporting shoulder of the outer ring of the rolling bearing. The separating action is thereby achieved by increasing the contact force on the following rolling elements close to the critical distance.

The cage-free rolling bearing according to the invention has the following advantages:

in bearings without the packaging-density limitation caused by assembly, in particular in those bearings in which at least one edge is at least partially removed (e.g. angular contact ball bearings, spindle bearings, packed groove bearings …), a higher load capacity can be achieved by a greater number of rolling elements by eliminating the space requirement for the intermediate path of the cage separating the rolling elements.

Reduced friction can be achieved by eliminating the friction points between the cage pockets and the rolling bodies on the guide surfaces of the rotating cage and the hysteresis losses in the material of the cage caused by the forces.

The impact that is not reproducible in the rolling behavior of the bearing is cancelled, which is caused by the cage rotating together, which moves without restriction within its degrees of freedom of eccentricity, rotation and elasticity.

During rolling of the rolling bodies, a more favorable kinematic relationship can be produced by the compensating or reducing effect of the contact angle of the rolling bodies with the bearing outer ring and the bearing inner ring with respect to the bore-to-rolling ratio and the ball advance follow-up.

In an advantageous embodiment, the pressing element has a pressing tongue which is supported in the first end region. The bearing of the pressure tongue is advantageously realized here by a projection which acts as a bearing block, by means of which the pressure element is connected in a rotationally fixed manner to the stationary element of the rolling bearing or to its surroundings.

The second end region of the pressure tongue, which is opposite the first end region of the pressure tongue, is preferably designed as a floating/unsupported end. By means of the floating tongues (similar to bending beams), the pressure elements acquire a spring force, by means of which a variable axial force is exerted on the respectively contacting rolling bodies. In this way, the spacing between adjacent rolling bodies can be adjusted particularly precisely.

For stability reasons, however, the second end region of the pressing tongue can also be fixed in an elastically bendable manner.

The cross section of the pressure tongue is advantageously tapered, i.e. the cross section of the pressure tongue decreases from the first end region in the direction of the second end region. The second end region accordingly has a smaller cross section than the first end region. In this way, the elastic distribution or the bending resistance moment of the pressing element can be set. This in turn leads to a particularly precise adjustment of the spacing between two adjacent rolling bodies. The tapering of the cross section can be achieved here by a reduction in the thickness and/or width of the compression tongue.

Furthermore, a chamfered starting region (anal fbereich) can be formed in the first end region of the compression tongue. By means of this beveled starting region, a gentle introduction of axial forces is achieved at the beginning of the contact between the respective rolling body and the pressure element.

A chamfered end zone (Auslaufbereich) may also be formed in the second end zone. By means of this chamfered end region, a gentle interruption of the force introduction at the end of the contact between the respective rolling body and the pressure element is achieved.

In a further advantageous embodiment, the compression tongue is designed to be arched or curved. Such a curvature likewise effects the elastic pretensioning (or the elastic adjustment) of the pressing element and thus leads to a particularly precise adjustment of the distance between two adjacent rolling bodies.

In a further advantageous embodiment, the pressure element is designed as a see-saw-shaped pressure element which is supported in the middle region and is fixed in an elastically bendable manner at the two end regions or is completely cantilevered. In this way, the pressure element can act as a spring rocker and the rolling elements located in front can be accelerated more strongly when the following rolling elements are very close.

According to the invention, it is necessary to apply a force to at least two rolling bodies simultaneously in the axial direction, temporarily by means of a pressing element. However, it is also possible to apply a force to more than two rolling bodies simultaneously in the axial direction by means of the pressing element. In this way, the spacing can be adjusted over a plurality of rolling elements and over a longer period of time. This additionally reduces the possibility of undesired contact between adjacent rolling bodies.

It is also possible to arrange a plurality of pressing elements distributed on the circumferential side. This additionally reduces the possibility of undesired contact between adjacent rolling bodies.

The rolling bearing is advantageously designed as an angular contact ball bearing. If the rolling bodies are pressed by the pressure elements in the direction of the outer ring shoulder of the angular ball bearing, a specific force introduction can thus be achieved by the pressure elements in this way.

Drawings

The invention is further illustrated by way of example in the accompanying drawings. The figures show that:

fig. 1 shows a sectional view of a rolling bearing without a cage;

fig. 2 shows a front view of the rolling bearing in fig. 1, wherein the cover plate is not shown;

FIG. 3 shows one of the pressing elements of FIG. 2 in isolation;

FIG. 4 shows a side view of the hold-down element of FIG. 3;

fig. 5 shows a schematic view of a pressing element with two rolling bodies contacting the pressing element;

fig. 6 shows a further embodiment of the pressing element.

Detailed Description

Fig. 1 shows a rolling bearing 1 without a cage in a sectional view. The rolling bearing has an inner ring 2 and an outer ring 3 arranged concentrically with the inner ring 2. An annular bearing interior is formed between the inner ring 2 and the outer ring 3. The rolling bodies 4 are distributed equidistantly in the circumferential direction in the bearing inner space. The annular cover disk 5 forms an axial closure of the rolling bearing 1 on the right in fig. 1. Sealing elements, which are not shown in detail in the figures, can be arranged between the cover sheet 5 and the inner ring 2 and/or the outer ring 3.

Fig. 2 shows a front view of the rolling bearing 1 from fig. 1, wherein the cover plate 5 is not shown for the sake of clarity. In addition to the inner ring 2, the outer ring 3, the rolling bodies 4 and the cover plate 5, the rolling bearing 1 has a total of three pressure elements 6.

The pressing elements 6 are fixed on the lid 5 and are distributed equidistantly in the circumferential direction. In this case, each pressing element 6 has the basic shape of a ring segment and accordingly covers the ring segment of the bearing interior. In this case, each pressing element 6 covers such a large angular range that at least two rolling bodies 4 are temporarily simultaneously contacted by the pressing element 6. In this case, each pressing element 6 exerts a force directed in the axial direction on the rolling elements 4 in contact therewith. More precisely, the pressure element 6 exerts an axial force on the rolling bodies 4, which force is directed from right to left in fig. 1. The rolling bodies 4 are thus pressed by the pressure elements 6 in the direction of the shoulder of the outer ring 3.

Fig. 3 and 4 show the pressing element 6 from fig. 1 and 2 separately. Fig. 4 shows the pressing element 6 from the same perspective as fig. 2. Fig. 3 shows a side view of the pressing element 6.

The pressing element 6 has a pressing tongue 7 and a projection 8. A projection 8 is formed on a first end region 7a of the pressure tongue 7 and serves to fix the pressure element 6 to the lid plate 5. The pressing element 6 is therefore supported in the first end region 7 a. A second end region 7b of the pressure tongue 7 opposite the first end region 7a is designed as an unsupported/floating end. I.e. the second end region 7b is unsupported. The cross section of the pressure tongue 7 tapers from the first end region 7a in the direction of the second end region 7 b. More precisely, the thickness of the compression tongue 7 is reduced, while the width of the compression tongue 7 remains constant. A chamfered starting area 7c is formed in the first end area 7 a. A chamfered end zone 7d is formed in the second end zone 7 b. As shown in particular in fig. 4, the pressing tongue 7 is formed in a curved or arched manner.

Fig. 5 schematically shows the functional principle of the cage-free roller bearing 1. One pressure element 6 and exemplarily two rolling bodies 4a, 4b are shown. If the rolling bodies 4a and 4b are not present, the pressing element 6 assumes the position of the dashed line. The pressing element 6 is pressed into the position shown by the solid lines by the two rolling bodies 4a, 4 b. At the same time, the pressing element 6 causes a corresponding reaction force acting on the two rolling elements 4a and 4 b. This reaction force corresponds to a force in the axial direction, which the pressing element 6 exerts on the rolling bodies 4.

During operation of the rolling bearing 1 (i.e. during rotation), the rolling elements 4a are the rolling elements located in front and the rolling elements 4b are the rolling elements following behind. The rolling bodies 4a therefore first come into contact with the pressure element 6 in the region of the starting region 7c and then move from the first end region 7a in the direction of the second end region 7 b. The following rolling element 4b is in contact with the pressure element 6 relatively late in the region of the start region 7c and likewise moves from the first end region 7a in the direction of the second end region 7 b. First, the rolling bodies 4a located at the front have reached the second end region 7b and then have lost contact with the pressing element 6 via the end region 7 d. At the same time, the rolling bodies 4 following the rolling bodies 4b have already passed the starting region 7 c. Rolling element 4b then accordingly becomes the preceding rolling element relative to the new following rolling element, and so on.

If, for example, the distance between the preceding rolling element 4a and the following rolling element 4b is now smaller than the theoretical distance that would be expected on the basis of an equidistant distribution of the rolling elements 4, the braking effect of the pressure element 6 on the preceding rolling element is smaller. The spacing between the rolling elements 4a and 4b increases accordingly. On the other hand, if the distance between the preceding rolling element 4a and the following rolling element 4b is greater than the theoretical distance, the braking effect of the pressure element 6 on the preceding rolling element 4a is greater. The spacing between the rolling elements 4a and 4b is correspondingly reduced.

Therefore, the distance between the rolling elements 4a and 4b is adjusted to the theoretical distance. Therefore, contact between the adjacent rolling elements 4a and 4b during operation of the rolling bearing 1 is reliably prevented.

Fig. 6 shows a further embodiment of the pressing element. The pressure element 106 shown in fig. 6 is distinguished from the pressure element 6 shown in the preceding figures by a differently shaped pressure tongue 107. The pressing tongue 7 of the pressing element 6 has a constant width, while the pressing element 107 has a narrowing width. More precisely, the width of the pressing element 107 decreases from the first end region 107a in the direction of the second end region 107 b. The second end region 107b accordingly has a smaller cross section than the first end region 107 a. In this way, the pressing element 106 has a different elasticity profile or a different bending moment of resistance than the pressing element 6.

In the embodiment shown in the figures, the rolling elements 4 are designed as balls. The rolling bearing 1 is accordingly designed as a ball bearing, more precisely as an angular contact ball bearing. However, it is also possible to design the rolling bodies 4 as cylinders, i.e. as rollers or cylinders.

In the embodiment shown in the figures, three pressing elements 6 are arranged equidistantly. However, other numbers of pressing elements or only a single pressing element 6 can also be provided.

In the embodiment shown in the figures, the rolling bearing 1 is designed as a cage-free rolling bearing. By almost completely filling the bearing inner space with rolling bodies 4, a high load-bearing capacity is achieved. However, a less tight packing of the rolling bodies 4 can also be used.

In the embodiment shown in the figures, the pressing element 6 is connected to the cover 5. However, it is also possible to connect the pressure element 6 to another fixed or stationary part of the rolling bearing or to a holder arranged adjacent to the rolling bearing. Furthermore, it is also possible to arrange the pressure element 6 on a rotating element of the rolling bearing 1, for example on the rotating inner ring 2 or outer ring 3.

In the embodiment shown in the figures, the pressure elements 6, 106 are designed as pressure elements with pressure tongues 7 and 107, respectively. In this case, the respective second end region 7b or 107b is formed completely free of support/cantilevered. However, it is also possible to fix the second end region 7b or 107b in an elastically bendable manner.

Furthermore, one or more pressure elements can also be provided, which are designed as seesaw-shaped pressure elements, which are supported in the middle region and are fixed in an elastically bendable manner or are unsupported at the two end regions. This embodiment of the pressing elements is advantageous in particular when the pressing forces are oriented axially relative to one another.

List of reference numerals:

1 Rolling bearing without cage

2 inner ring

3 outer ring

4. 4a, 4b rolling element

5 cover sheet

6. 106 pressing element

7. 107 compression tongue

7a, 107a first end region

7b, 107b second end region

7c start region

7d end region

8 projecting part