CN111075844A - Inner ring for a rolling bearing and rolling bearing - Google Patents

Abstract

The invention relates to an inner ring for a rolling bearing and a rolling bearing. The rolling bearing also has a rolling body (3), the inner ring is provided with an annular stop flange for axially stopping the rolling body, wherein a radial groove (211) is arranged on the outer circumferential surface of the stop flange at the axial end side of the rolling bearing, the radial groove axially penetrates through the stop flange, and/or a flange outer diameter transition part (222; 232; 242) is formed on the stop flange at the axial end side of the rolling bearing, and/or a through hole (253) axially penetrates through the stop flange is formed on the stop flange at the axial end side of the rolling bearing, so that a lubricating medium outside the rolling bearing can enter a lubricating area in the rolling bearing; the rolling bearing comprises the inner ring.

Description

Inner ring for a rolling bearing and rolling bearing

Technical Field

The invention relates to the field of bearings. And particularly to a lubricating structure of a rolling bearing.

Background

The bearing in the wind power gearbox requires long service life and strong bearing capacity, so the requirement on the lubrication of the bearing is high. In this case, for example, a lubrication system using oil mist lubrication may be employed. A bearing lubrication system for a wind power gearbox is disclosed, for example, in chinese patent CN 206111861U. In the bearing lubrication system, an oil spray hole is provided, which is located radially between the bearing cage and the bearing outer ring and which can spray oil mist toward the rolling elements of the bearing, whereby lubrication of the bearing can be achieved.

In applications such as tapered roller bearings, however, it is sometimes necessary, depending on the overall layout of the system, to arrange the oil jet closer to the radial inside of the bearing, for example radially between the axial end faces, for example the small end faces, of the bearing cage and the inner ring. In this case, the clearance between the inside diameter of the cage of some bearings and the outside diameter of the small side flange of the inner race is small, and the effect of the lubricating oil entering the bearings is not satisfactory, thereby affecting the bearing running performance, resulting in fatigue failure of the bearings due to insufficient lubrication.

Disclosure of Invention

The object of the present invention is therefore to provide a rolling bearing which overcomes the above-mentioned disadvantages.

The above object is achieved by an inner ring for a rolling bearing, which also has rolling bodies, which inner ring is designed with a stop collar for axially stopping the rolling bodies, wherein a lubricant duct, which is additional to the prior art, is provided on the stop collar on the axial end side of the rolling bearing.

In a preferred embodiment, a radial groove is provided on the outer circumferential surface of a stop collar located on the axial end side of the rolling bearing, which radial groove extends axially through the stop collar, so that a lubricating medium, for example oil mist, on the outside of the rolling bearing can enter the lubrication region in the rolling bearing via the radial groove. In other words, the additional lubricant duct is formed as a radial groove on the outer circumferential surface of the respective stop collar, which extends axially through the respective stop collar. Here, the radial groove is recessed radially inward from the stopper flange outer circumferential surface. Preferably, the radial groove has an arc shape or a crescent shape in a cross section in the radial direction of the inner ring. Preferably, the cross-sectional area of the radial groove is designed as large as possible while ensuring that the rolling elements do not fall off. Preferably, the radial grooves are distributed uniformly at least in groups in the circumferential direction of the stop flange. Particularly preferably, the radial grooves are distributed uniformly in the circumferential direction of the stop collar. Preferably, the number of radial grooves is designed as large as possible while ensuring that the rolling elements do not fall off. By providing the radial groove, which penetrates the stop collar in the axial direction, as described above, a lubricant passage can advantageously be formed, so that even if the clearance between the cage and the inner ring at the axial end of the rolling bearing is small, the lubricant, for example oil mist, can enter the lubrication region of the rolling bearing in a sufficient amount. In an alternative or additional preferred embodiment, the flange outer diameter transition is formed on the stop flange on the axial end side of the rolling bearing in such a way that the outer diameter of the stop flange on the axial end side close to the rolling bodies is greater than the outer diameter on the axial end side remote from the rolling bodies, so that a lubricating medium, for example oil mist, outside the rolling bearing can enter the lubrication region in the rolling bearing via the flange outer diameter transition. In other words, the additional lubricant duct is designed as a flange outer diameter transition. The stop collar is formed with a substantially annular end face on the axial end side adjacent to the rolling bodies, said end face serving to stop the rolling bodies. The stop flange forms an axial end face of the rolling bearing in a radially inner region at an axial end side remote from the rolling elements. By means of such a flange outer diameter transition which is inclined overall to the rotational axis of the rolling bearing, the radial play of the cage and the stop flange of the inner ring at the axial end side of the bearing can be increased, so that the lubricating medium can easily enter into the lubricating region in the rolling bearing.

"inclined overall" here means in particular: the present invention does not limit the structure of the outer peripheral surface of the flange outer diameter transition portion. In particular, the flange outer diameter transition may be configured as a conical surface. Alternatively, the flange outer diameter transition may be configured as an axially curved surface, such as a raised surface (e.g., a portion of an annulus) or a recessed surface. Alternatively, the flange outer diameter transition may have a stepped configuration.

In a further alternative or additional preferred embodiment, a through-opening is formed in the stop collar on the axial end side of the rolling bearing, which through-opening extends axially through the stop collar, so that a lubricating medium, for example an oil mist, outside the rolling bearing can enter the lubrication region in the rolling bearing through the through-opening. In other words, the additional lubricant duct is formed as a through-hole which extends axially through the respective stop flange. Preferably, the cross-sectional area of the through-opening is designed as large as possible while ensuring that the rolling elements do not fall off. Preferably, the through-holes are distributed uniformly at least in groups in the circumferential direction of the stop collar. Particularly preferably, the through-openings are distributed uniformly in the circumferential direction of the stop collar. Preferably, the number of through-holes is designed as large as possible while ensuring that the rolling elements do not fall off. By providing a through-hole running through in the axial direction, a lubricant passage can be advantageously formed, and even if the radial clearance between the cage and the inner ring at the axial end side of the rolling bearing is small, the lubricant, such as oil mist, can smoothly enter the lubrication region of the rolling bearing.

Within the scope of the present description, the rolling bearing may also comprise an outer ring and a cage. The rolling bodies and the cage are arranged between the outer race and the inner race. The cage isolates the rolling elements and guides and retains the rolling elements within the bearing. The self-rotation axis of the rolling body and the rotation axis of the rolling bearing may intersect. The rolling bodies can be designed, for example, as tapered rollers. Alternatively, the rolling bodies can also be designed, for example, as rolling bodies of any known design. The rolling bodies can be arranged in a single row in the circumferential direction of the rolling bearing, i.e. the rolling bearing is designed as a single-row bearing. The rolling bodies can also be arranged in more than one row in the rolling bearing, for example the rolling bearing can be designed as a double row bearing, a four row bearing or the like.

Within the scope of the present description, the inner ring may be the inner ring of a single row bearing. The inner ring may also be an inner ring of a double row bearing or a four row bearing having raceways for only one row of rolling elements. The inner ring can also be an inner ring with raceways for at least one row of rolling elements in a double row bearing or a four row bearing. The one-piece inner ring is formed with a stop flange at least on one axial end side of the rolling bearing. At least one of the segmented inner rings is formed with a stop collar, such that, in the assembled state of the rolling bearing, it is formed with a stop collar on at least one axial end side of the rolling bearing. The stop collar at least partially stops the rolling bodies in the axial direction. Furthermore, the stop flange on the axial end side of the rolling bearing also partially defines a lubrication region, for example a raceway region, of the rolling bearing.

For the three preferred embodiments, the additional lubricant ducts can each be formed on a stop flange of the inner ring with a smaller diameter, i.e. on a small-side flange on the small end face side of the inner ring.

By providing an additional lubricant duct on the stop collar at the axial end of the rolling bearing, a channel for feeding lubricant, for example oil mist, axially outward of the rolling bearing into the lubrication region in the rolling bearing can additionally be formed. In particular in the case of the solution in which the oil spray openings outside the bearing must be arranged radially between the cage and the small-side flange of the inner ring, oil mist is difficult to enter the lubrication region of the bearing from the clearance between the cage and the outer ring on the axial end side, and because of the small radial clearance between the cage and the inner ring on the axial end side, it is difficult for oil mist to enter the lubrication region even if the oil spray openings face the clearance, whereas with the three preferred solutions described above, oil mist can advantageously enter the lubrication region in the rolling bearing by means of the radial recesses and/or the flange outer diameter transitions and/or the through-holes. This advantageously increases the lubrication of the rolling bearing and reduces the temperature inside the bearing, thereby increasing the life of the rolling bearing and reducing maintenance costs.

The above-mentioned technical problem can also be solved by a rolling bearing. The rolling bearing comprises an inner ring having the above-mentioned features. The rolling bearing further comprises an outer ring, a cage and at least one row of rolling bodies. For example, the rolling bearing can be designed as a tapered roller bearing. The rolling bearing can be used, for example, in a wind gearbox.

In summary, by changing the shape of the stopper flange of the inner ring on the axial end side of the rolling bearing, the radial clearance between the retainer and the stopper flange can be increased, so that the oil mist can more easily enter the lubrication region of the tapered roller bearing. Alternatively or additionally, it is possible to machine several through-openings and/or radial grooves on the stop collar of the inner ring, so that oil mist can enter the lubrication region of the rolling bearing through these through-openings and/or radial grooves. This advantageously increases the lubrication of the rolling bearing and reduces the temperature inside the bearing, which in turn increases the service life of the rolling bearing and reduces the maintenance costs. Meanwhile, the arrangement of the oil nozzle is more flexible in design, and the function of a bearing lubricating system, even the whole machine system, such as a wind power gear box, is facilitated.

Drawings

Preferred embodiments of the present invention are schematically illustrated in the following with reference to the accompanying drawings. The attached drawings are as follows:

fig. 1 is a partial view of a rolling bearing according to a first embodiment, viewed in the axial direction;

fig. 2 is a half sectional view of the rolling bearing according to the first embodiment, taken along the axial direction;

fig. 3 is a half sectional view of a rolling bearing according to a second embodiment, taken in the axial direction;

fig. 4 is a half sectional view of a rolling bearing according to a third embodiment, taken in the axial direction;

fig. 5 is a half sectional view of a rolling bearing according to a fourth embodiment, taken in the axial direction;

fig. 6 is a half sectional view of the rolling bearing according to the fifth embodiment taken in the axial direction.

Identical or functionally identical components are denoted by the same reference numerals.

Detailed Description

A number of preferred embodiments of the invention are shown below. The same aspects of the various embodiments are first described herein.

As fig. 1 to 6 show, the rolling bearing arrangement in the illustrated embodiments is designed as a single-row tapered roller bearing, which can be used, for example, in a wind turbine gearbox. The rolling bearing has an outer ring 1, inner rings 21 to 25, and a cage 4 and a row of rolling bodies 3 arranged between the outer ring 1 and the inner rings 21 to 25, wherein the cage 4 separates the rolling bodies 3 and is guided by the rolling bodies 3. The rolling bodies are designed here as tapered rollers 3, which are essentially of truncated cone shape and thus have a small end face and a large end face. The rolling bodies 3 are each stopped at their axial ends by annular stop flanges formed on the inner rings 21 to 25. The small end face of the tapered roller 3 is stopped by a stop flange having a small diameter, i.e., a small-side flange, and the large end face of the tapered roller 3 is stopped by a stop flange having a large diameter, i.e., a large-side flange. Here, an additional lubricant passage 211 is provided on the small-side flange of each inner ring 21-25, i.e. on the left-hand stop flange in fig. 2 to 6; 222, c; 232; 242; 253.

the lubricating medium passages 211 in the respective embodiments are described below; 222, c; 232; 242; 253.

fig. 1 and 2 show a partial view and a half sectional view taken in the axial direction of the rolling bearing according to the first embodiment, respectively. In this embodiment, the additional lubricant passage is configured as a radial groove 211 on the outer circumferential surface of the small-side flange of the inner ring 21, the groove cross section of the radial groove 211 being crescent-shaped. The radial groove 211 axially penetrates the small-side flange. The radial grooves 211 are evenly distributed in the circumferential direction of the inner ring 21. This increases the radial clearance of the cage 4 with respect to the outer circumferential surface of the small-side flange of the inner ring 21, particularly locally in the circumferential direction, and facilitates entry of oil mist into a lubrication area such as a raceway.

Fig. 3 shows a half sectional view of a rolling bearing according to a second embodiment, taken along the axial direction. In this embodiment, the additional lubricant passage is configured as a flange outer diameter transition 222 that makes the outer diameter of the small-side flange on the axial end side close to the tapered rollers 3 larger than the outer diameter on the axial end side away from the tapered rollers 3. As shown in fig. 3, the outer peripheral surface of the flange outer diameter transition portion 222 or the outer peripheral surface of the small-side flange in the second embodiment is configured as a conical surface. This increases the radial clearance between the cage 4 and the small-side flange of the inner ring 22, thereby facilitating entry of oil mist and improving lubrication of the tapered roller bearing.

Fig. 4 shows a half sectional view of a rolling bearing according to a third embodiment, taken in the axial direction. The third embodiment is similar to the second embodiment in that the additional lubricant passage is also configured as a flange outer diameter transition 232 that makes the outer diameter of the small-side flange on the axial end side close to the tapered rollers 3 larger than the outer diameter on the axial end side away from the tapered rollers 3. The difference is that, as shown in fig. 4, the outer peripheral surface of the flange outer diameter transition portion 232 or the outer peripheral surface of the small-side flange in the third embodiment is configured as a surface having a curvature in the axial direction, here, a bulging arc-shaped surface. This increases the radial clearance between the cage 4 and the small-side flange of the inner ring 23, thereby facilitating the entry of oil mist and improving the lubrication of the tapered roller bearing.

Fig. 5 shows a half sectional view of a rolling bearing according to a fourth embodiment, taken in the axial direction. The fourth embodiment is similar to the second embodiment in that the additional lubricant passage is also configured as a flange outer diameter transition 242 that makes the outer diameter of the small-side flange on the axial end side close to the tapered rollers 3 larger than the outer diameter on the axial end side away from the tapered rollers 3. The difference is that, as shown in fig. 5, the outer peripheral surface of the flange outer diameter transition part 242 or the outer peripheral surface of the small-side flange in the fourth embodiment has a stepped structure. This increases the radial clearance between the cage 4 and the small-side flange of the inner ring 25, thereby facilitating the entry of oil mist and improving the lubrication of the tapered roller bearing.

Fig. 6 shows a half sectional view of the rolling bearing according to the fifth embodiment, taken along the axial direction. In this embodiment, the lubricating medium passage is configured as a through hole 253 that penetrates the small-side flange in the axial direction. The through-hole 253 is configured as a circular hole, for example. The through holes 253 are arranged evenly on the small-side flange in the circumferential direction of the inner ring 25. Oil mist can thus easily enter the lubrication area in the tapered roller bearing through these through holes 253.

Although possible embodiments have been described by way of example in the above description, it should be understood that numerous embodiment variations exist, still by way of combination of all technical features and embodiments that are known and that are obvious to a person skilled in the art. It should also be appreciated that the exemplary embodiment or exemplary embodiments are only examples, and are not intended to limit the scope, applicability, or configuration of the invention in any way. From the foregoing description, one of ordinary skill in the art will more particularly provide a technical guide to convert at least one exemplary embodiment, wherein various changes may be made, particularly in matters of function and structure of the components described, without departing from the scope of the following claims.

List of reference numerals

1 outer ring

21 inner ring

211 radial groove

22 inner ring

222 flange outside diameter transition

23 inner ring

232 flange outer diameter transition

24 inner ring

242 flange outside diameter transition

25 inner ring

253 through hole

3 rolling element

4 holding rack

Claims (10)

1. Inner ring for a rolling bearing, which also has rolling bodies (3), wherein the inner ring (21) is designed with an annular stop collar for axially stopping the rolling bodies (3),

the lubrication device is characterized in that a radial groove (211) is arranged on the outer peripheral surface of the stop flange at the axial end side of the rolling bearing, and the radial groove (211) axially penetrates through the stop flange, so that a lubrication medium outside the rolling bearing can enter a lubrication area in the rolling bearing through the radial groove (211).

2. The inner ring according to claim 1, characterized in that the radial groove (211) is configured on a stop flange of the inner ring (21) having a smaller diameter.

3. Inner ring for a rolling bearing, which also has rolling bodies (3), wherein the inner ring (22; 23; 24) is designed with an annular stop collar for axially stopping the rolling bodies (3),

the method is characterized in that a flange outer diameter transition (222; 232; 242) is formed on the stop flange on the axial end side of the rolling bearing in such a way that the outer diameter of the stop flange on the axial end side close to the rolling bodies (3) is greater than the outer diameter on the axial end side remote from the rolling bodies (3), so that a lubricating medium outside the rolling bearing can enter a lubricating region inside the rolling bearing through the flange outer diameter transition (222; 232; 242).

4. The inner ring according to claim 3, characterized in that the flange outer diameter transition (222; 232; 242) is configured on a stop flange of the inner ring (21) having a smaller diameter.

5. The inner ring of claim 3, wherein the flange outer diameter transition (222) is configured as a conical surface.

6. The inner ring of claim 3, wherein the flange outer diameter transition (232) is configured as a surface having a curvature in an axial direction.

7. The inner ring of claim 3, wherein the flange outer diameter transition (242) has a stepped configuration.

8. Inner ring for a rolling bearing, which also has rolling bodies (3), wherein the inner ring (25) is designed with an annular stop collar for axially stopping the rolling bodies (3),

the rolling bearing is characterized in that a through hole (253) which penetrates through the stop flange in the axial direction is formed in the stop flange which is positioned at the axial end side of the rolling bearing, so that a lubricating medium outside the rolling bearing can enter a lubricating area in the rolling bearing through the through hole (253).

9. The inner ring according to claim 8, characterized in that the through-hole (253) is configured on a stop flange of the inner ring (21) having a smaller diameter.

10. Rolling bearing, characterized in that it comprises an inner ring (21; 22; 23; 24; 25) according to any one of claims 1-9.

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