JPH11264420A - Rolling bearing - Google Patents

Abstract

(57) [Problem] To provide a rolling bearing capable of smoothly supplying a lubricant to the inside of the bearing while preventing deterioration of the bearing even when a radial load is mainly applied to the rolling bearing. SOLUTION: In a rolling bearing having a lubricant supply hole for supplying a lubricant to a rolling element in a raceway of either an inner ring or an outer ring, the lubricant supply hole is moved from a center of a non-load zone where a radial load is not applied. Provided at multiple locations within a range of ± 60 ゜.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing mainly receiving a radial load, and more particularly to a technique for stably supplying a lubricant while preventing deterioration of the rolling bearing.

[0002]

2. Description of the Related Art There is a rolling bearing in which a small hole communicating with the inside of a bearing is provided in a race of a rolling bearing in order to supply a lubricant to the rolling bearing satisfactorily, and the small hole is used as a lubricant supply hole. Such a rolling bearing, for example, in a case where a lubricant supply hole is provided in an outer ring, has a configuration in which lubricant is supplied into the bearing through a small hole penetrating from the outer peripheral side to the inner peripheral side of the race. . The lubricant supply hole is, for example, as shown in FIG.
Are often provided for double-row rolling bearings shown in FIG. The lubricant supply hole 51 is provided on the lubricant supply hole 51 by a roller.
In order to prevent the rolling of the rollers 52a and 52b, the rollers 52a and 52b are provided so as to avoid the rolling tracks.

Some needle roller bearings shown in FIG. 6 are provided with a lubricant supply hole even in a single row. Conventionally, this kind of lubricant supply hole is provided at one place on the circumference of the bearing ring of the bearing or at a plurality of symmetrical positions on the circumference. For example, in the needle roller bearing shown in FIG. 6, lubricant supply holes 62a, 62b, 62c, 62d communicating from the outer peripheral side to the inner peripheral side of the outer ring 61, which is a raceway ring, are provided at every 90 ° in circumferential angle. Are provided at a total of four locations.

[0004]

However, in the rolling bearing having the above-mentioned structure, the following problem occurs. First, when the lubricant supply hole is formed at only one location on the bearing ring, when the amount of the lubricant to be supplied is large, a larger supply pressure is required for supplying the lubricant. For this reason, there is a possibility that the lubricant may not be sufficiently supplied by the supply method that is generally used, and a higher-pressure lubricant supply device is required. Further, since the lubricant is supplied to the inside of the bearing from a single point, it is difficult to uniformly diffuse the lubricant throughout the rolling elements.

On the other hand, as shown in FIG.
When a, 62b, 62c, and 62d are formed at a plurality of locations symmetrically with respect to the center of the bearing, the rolling element 63 loaded with a large radial load has the lubricant supply hole 62 opened on the raceway surface of the outer ring 61.
Rolling on c may not be avoided due to its structure.
This means that, for example, if lubricant supply holes 62a, 62b, 62c, 62d are arranged on the raceway surface of the outer ring 61 at every 90 ° circumferential angle, when a large radial load Fr is applied to the rolling bearing,
One of the lubricant supply holes (62c in the figure) is arranged near the load direction of the radial load Fr at which the load becomes maximum.

Then, at the position of the lubricant supply hole 62c, the rolling element 63 rolls on the lubricant supply hole 62c opened on the raceway surface while receiving a large radial force Fr. Stress concentration occurs at the edge of 62c, and large edge stress occurs. This is the same as the case where the rolling element is spherical and the case where the rolling element is cylindrical. The edge stress generated at this time promotes abrasion and peeling of the bearing, vibration and noise are likely to occur, and there is a possibility that the life of the bearing is shortened.

[0007] For the above reasons, for a single row of rolling bearings, the rolling element rolls on the lubricant supply hole provided on the raceway surface. It was difficult to adopt a supply system. The present invention has been made in view of such conventional problems,
An object of the present invention is to provide a rolling bearing capable of smoothly supplying a lubricant while preventing deterioration of the bearing even when a large radial load is applied to the rolling bearing.

[0008]

In order to achieve the above object,
The present invention relates to a rolling bearing in which a lubricant supply hole for supplying a lubricant to the inside of a bearing is provided in one of the raceways of an inner ring and an outer ring. The bearing ring is provided at a plurality of locations within a range of ± 60 ° from the center of the non-load zone where the radial load of the bearing ring is not applied. According to the above configuration,
Since there is no lubricant supply hole on the raceway surface on the load zone that receives the radial load, the rolling elements roll smoothly, while the lubricant supply hole does not exist on the raceway surface on the non-load zone that does not receive the radial load. Since there are a plurality of lubricants, the lubricant can be stably supplied into the bearing at a relatively low supply pressure.

Here, it is preferable to make a mark on the end face of the bearing ring at the center in the circumferential direction of the plurality of lubricant supply holes of the rolling bearing. This mark may be a pin hole or a keyway which prevents rotation of the non-rotating wheel due to creep. The presence of the mark makes it easy to recognize the position of the lubricant supply hole on the bearing circumference when the bearing is assembled.

[0010]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment according to the present invention will be described below with reference to FIGS. FIG. 1 is a diagram schematically showing a cross section of a cylindrical roller bearing. First, the schematic contents of the present invention will be described with reference to FIG. Radial rolling bearings mainly receiving a radial load are usually used with an internal clearance (play inside the bearing) in order to prevent a temperature rise or seizure. For example, when a load Fr in the radial direction (radial direction) is applied to a cylindrical roller bearing having an internal clearance, the inner ring 1 and the outer ring 2 approach in the direction in which the load is received, and the roller group on one side of the load contacts the inner and outer rings. Then, a load Qi (i = 1 to 5) acts between the roller 3 and the outer ring 2. On the other hand, the roller group that is in contact with the roller group on the opposite side to the load application direction does not contact both the inner and outer rings 2 and 3 because the bearing has an internal clearance. Therefore, no load is applied to the inner and outer rings 2 and 3 from the roller group. Here, the range in which the load Qi due to the radial load Fr is received is referred to as a load zone, and the range in which the load Qi is not received is referred to as a non-load zone.

Considering the case where the outer ring 2 is fixed and the inner ring 1 is rotated, as the inner ring 1 and 3 rotate, the inner ring 1 bears a load between the rollers 3 at all the raceway positions in the circumferential direction. However, the outer ring 2 receives a load from the rollers 3 only on the raceway surface at the load zone position. In other words, at the non-load zone position of the stationary wheel, that is, the outer ring 2 that is the fixed wheel, no force other than the centrifugal force occurs between the roller 3 existing at the non-load zone position and the outer ring raceway surface. Under normal operating conditions for rolling bearings, the load generated between the outer ring 2 and 3 due to gravity or rotational centrifugal force is extremely small.Therefore, the lubricant supply hole is provided within the non-load zone on the fixed wheel side. For example, even when a relatively large radial load is applied, the above-described problems such as abrasion and peeling do not occur.

The range of the load zone varies depending on the radial clearance of the bearing and the magnitude of the radial load Fr. However, when no load is applied and all the rollers come into contact with the inner and outer rings of the bearing. When there is no clearance, the range of the load zone is 180 ° below the bearing, and when there is even a small clearance in the radial direction, the load zone is always smaller than ± 90 ° from the load direction. Becomes

Normally, the internal clearance of a radial rolling bearing is set within a predetermined range according to the dimensions of the bearing and the like, so that the lubricant supply hole may be provided within a range of 180 ° in the non-load zone. . However, when an axial load or a moment load is applied to the bearing in addition to the radial load,
Taking into account the fact that the load zone expands slightly, and the presence of mounting errors in the load direction of the bearing and slight fluctuations in the load load direction, the load may be applied within the 180 ゜is there. Therefore, the non-load area is narrowed to the safe side, and the total of ± 60mm
It is preferable to arrange a lubricant supply hole within a range of 120 °. Further, in order to sufficiently supply the lubricant into the bearing without increasing the supply pressure of the lubricant, a plurality of lubricant supply holes may be provided at different positions in the non-load zone. In this case, it is preferable that the arrangement pitch of the lubricant supply holes is equal, but for example, it is more appropriate to set densely near the center of the non-load zone, and coarsely as the distance from the center increases. May be changed as appropriate so that the lubricant can be supplied.

Next, a first embodiment in which the arrangement of the lubricant supply holes is applied to a single-row cylindrical roller bearing will be described. The configuration of the cylindrical roller bearing according to the present embodiment is shown in FIGS.
FIG. 2 (a) is a side view of the cylindrical roller bearing, and FIG. 2 (b) is FIG. 2 (a).
3 is a cross-sectional view taken along line AA of FIG. According to FIG. 2 (a), the cylindrical roller bearing 2
An annular groove 22 is formed on the outer peripheral surface of the outer race 21 of the 0 at the center in the axial direction over the entire outer peripheral surface. An outer ring raceway surface 21a where the outer ring 21 is in rolling contact with the rollers 23 from the bottom surface of the annular groove 22.
A total of three lubricant supply holes are formed so that the circumferential angle from the center of the bearing with respect to the lubricant supply hole 24b is 60 °. Further, a side surface portion of the outer ring 21 as a fixed ring, which is indicated by an arrow B, that is, three lubricant supply holes 24a, 24
As shown in FIG. 3, a mark 25 serving as a mark for aligning the lubricant supply hole at the time of assembling the bearing is attached to the position of the lubricant supply hole 24b located at the center of b, 24c. I have.
FIG. 3 is a view in the direction of arrow B in FIG. The mark 25 may be provided not only on one end face of the outer ring but also on both end faces. Accordingly, it is not necessary to confirm whether or not the bearing is on the mark side when mounting the bearing, and the mounting process is further simplified and the workability is improved.

Further, the outer ring 21 as a fixed ring is provided with a pin hole (not shown) used to prevent relative rotation with the bearing box due to creep when the bearing is used. The pin hole serves as a stopper for the outer ring and may be a keyway. Needless to say, pin holes and key grooves can be used as marks. Thus, the lubricant supply holes 24a, 24
As described with reference to FIG. 1, b and 24c are provided within a range of an arc having a circumferential angle of 120 ° or less of the outer ring 21 as a fixed ring. A mark 25 is provided on the side surface of the outer ring 21 at the center of the lubricant supply hole 24b, and the other lubricant supply holes 24a and 24c are respectively disposed at positions of a circumferential angle ± 60 ° around the mark 25. ing. In addition, although the mark 25 is provided at the center position of the non-load zone, it may be provided at a position to be the center of the load zone (the position on the opposite side of the former). In any case, it is sufficient if the circumferential position of the lubricant supply hole is provided at a position where it can be easily recognized.

Here, the dimensions of the cylindrical roller bearing of this embodiment are, for example, those having an inner diameter of 100 mm, an outer diameter of 215 mm, a width of 73 mm, a width of the annular groove 22 of 10 mm, and a diameter of the lubricant supply hole of 6 mm. However, it is needless to say that the lubricant supply hole may be provided in the same manner even if the dimensions are other than those exemplified here.

As described above, by arranging the lubricant supply hole within a range of ± 60 ° from the center position of the non-load area of the load, the lubricant supply hole provided in the non-load area is provided with the lubricant supply hole. Can be supplied stably to the inside of the bearing, and even when a radial load is applied, since there is no lubricant supply hole in the load zone, the rolling operation of the rollers is performed smoothly, And vibration can be suppressed. Also,
Pin holes (not shown) provided in the outer ring, which is a fixed ring, can prevent relative rotation with the bearing box due to creep during use.

By attaching the mark 25 to the side surface of the fixed wheel, the position of the lubricant supply hole of the rolling bearing can be easily recognized. Therefore, when assembling the rolling bearing, the position of the lubricant supply hole can be easily and reliably adjusted to a position where no radial load is applied or a position where the load is small even if it is applied, and the bearing is assembled. The work can be further simplified. Further, since a plurality of lubricant supply holes are provided within a predetermined range of the non-load zone, a larger amount of lubricant is supplied at a relatively low supply pressure as compared with a case where the lubricant is supplied from one lubricant supply hole. With this, it becomes possible to introduce into the bearing. Therefore, a smooth rotation operation of the bearing can be more reliably obtained with a simple configuration without requiring a high-pressure supply device.

In the present embodiment, the case where the outer race 21 is stationary and the inner race 26 is rotated has been described as an example.
When the outer ring 21 is rotated while the outer ring 21 is stationary, a similar effect can be obtained by providing the lubricant supply hole in the non-load range of the inner ring 26 as a fixed wheel.

Next, a second embodiment in which the present invention is applied to a single row cylindrical roller bearing having a flange on the inner ring side will be described. FIGS. 4A and 4B show a cylindrical roller bearing according to the present embodiment. FIG. 4A shows a side cross section of the cylindrical roller bearing, and shows a cross section taken along the line CC of the central portion in the axial direction of the cylindrical roller bearing shown in FIG. 4B. As shown in FIG. 4, the cylindrical roller bearing 40 includes a collar 41a on an inner ring 41, and an inner ring 41 and an outer ring 42.
The axial shape of the raceway surface and the axial shape of the rolling surface of the roller 43 have a substantially arc shape. The radius of curvature of this arc is set to be larger than the distance from the outer ring raceway surface to the bearing axis. The rollers 43 are held at a constant circumferential interval by a retainer 46.

In this case, an annular groove 44 is formed at the axial center of the outer peripheral surface of the outer ring 42, which is a fixed ring, over the entire outer peripheral surface, and the bottom groove of the annular groove 44 communicates with the raceway surface of the outer ring. A small hole, that is, a lubricant supply hole 45 is provided. As shown in FIG. 4, the lubricant supply holes 45a, 45b, 45c, 45d are
A total of four points are provided at equal intervals within the range of 100 in the circumferential angle of 100 °. When assembling the bearing, assemble it so that the center position of this circumferential angle of 100 ° is the center position of the non-load zone.
According to the above configuration, a plurality of lubricant supply holes 45a, 45b, 45c,
Since 45d is not located in the bearing load area and is located in the non-load area, even if a large radial load is applied to the bearing, the rolling of the rollers 43 in the load area is smooth, while The lubricant is stably supplied into the bearing from the lubricant supply holes 45a, 45b, 45c, 45d.

As described above, the present invention can be applied to the cylindrical roller bearing 40 having a flange on the inner ring side.
The same operation and effect as the embodiment can be obtained. Further, it is sufficiently possible to apply the present invention to a roller bearing having a flange on the outer ring, a roller bearing having a flange on both the inner ring and the outer ring, and a roller bearing having no flange on both the inner and outer rings. Further, the present invention is also applicable to ball bearings.

[0023]

According to the present invention, by providing a lubricant supply hole on a raceway ring, which is a fixed ring in a non-load zone of a load applied to a rolling bearing, ± 60 ° from the center of the non-load zone. The lubricant can be stably supplied to the inside of the bearing from the lubricant supply holes provided within the range. For this reason, even when a radial load or the like is applied, since the lubricant supply hole does not exist in the load area, the rollers can smoothly roll on the raceway surface, and the generation of noise and vibration can be suppressed. it can.

Further, by attaching a positioning mark at the time of assembling to the side surface of the fixed ring, the position of the lubricant supply hole of the rolling bearing can be adjusted to a position where no radial load is applied.
Even if a load is applied, it can be easily and reliably adjusted to a position where the load is small, and the operation of assembling the bearing can be further simplified.

Further, since the lubricant supply holes are provided at a plurality of locations within a range of 120 ° in the non-load zone, the number of lubricant supply holes is larger than that in a case where the lubricant is supplied from one lubricant supply hole. Can be introduced into the bearing at a relatively low supply pressure, and a smooth rotation operation of the bearing can be obtained more reliably.

[Brief description of the drawings]

FIG. 1 is a diagram illustrating a state in which a radial force is applied to a roller bearing, for explaining a schematic content of the present invention.

FIG. 2 is a configuration diagram of a cylindrical roller bearing according to the first embodiment.

FIG. 3 is a view of the cylindrical roller bearing in FIG.

FIG. 4 is a configuration diagram of a cylindrical roller bearing according to a second embodiment.

FIG. 5 is a bearing cross-sectional view showing a lubricant supply hole position of a conventional roller bearing.

FIG. 6 is a bearing cross-sectional view showing a lubricant supply hole position of a conventional needle roller bearing.

[Explanation of symbols]

 1,26,41 Inner ring 2,21,42 Outer ring 3,23,43 Roller 24a, 24b, 24c, 45a, 45b, 45c, 45d Lubricant supply hole Fr Radial load Q1, Q2, Q3, Q4, Q5 Load

Claims (1)

[Claims] 1. A rolling bearing in which a lubricant supply hole for supplying a lubricant into a bearing is provided in one of an inner ring and an outer ring, wherein the lubricant supply hole is formed on the inner ring or the fixed ring as a fixed ring. A rolling bearing provided at a plurality of locations within a range of ± 60 ° from a center of a non-load zone in which a radial load of any one of the outer races is not applied.