JPH07269567A - Slide roller bearing - Google Patents

Abstract

PURPOSE:To make the manufacture easier while securing a sufficient loading capacity, by making the contacting area between a roller and a cylindrical member larger. CONSTITUTION:A roller 16 is provided between a cylindrical member 10 and a shaft member 12 at the inner side of the cylindrical member 10. The outer peripheral surface 18 of the roller 16 is made in a curved surface having a curvature radius almost the same as the curvature radius of the inner peripheral surface of the cylindrical member 10. On the outer peripheral surface of the shaft member 12, a roller groove 13 with a circular arc section having the curvature radius almost the same as the curvature radius of the roller outer peripheral surface 18 is extended in the axial direction, and the roller 16 is fitted to the roller groove 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slide roller bearing for slidably supporting a moving object in a mold device, a machine tool or the like.

[0002]

2. Description of the Related Art Conventionally, as slide bearings for supporting slides, slide ball bearings as shown in FIG. 7 and slide roller bearings as shown in FIG. 8 have been known.

In FIG. 7, a hollow shaft member 92 is inserted inside a cylindrical member 90, and a cylindrical retainer 94 is inserted between the outer peripheral surface of the shaft member 92 and the inner peripheral surface of the cylindrical member 90. The retainer 94 holds a plurality of balls 96 in a rollable manner at predetermined intervals. The balls 96 are arranged at different positions in the circumferential direction, and a ball groove 92a extending in the axial direction is formed at a position corresponding to each ball 96 on the outer peripheral surface of the shaft member 92. Then, while the ball 96 rolls, the cylindrical member 9
The shaft member 92 can move relative to 0 in the axial direction.

In FIG. 8, a roller 98 is provided instead of the ball 96 in FIG. 7, and the roller 98 is provided.
In order to roll like the ball 96, flat roller sliding surfaces 90a and 92b are formed on the inner peripheral surface of the cylindrical member 90 and the outer peripheral surface of the shaft member 92, respectively.

[0005]

In the slide ball bearing of FIG. 7, the ball 96 and the inner peripheral surface of the cylindrical member 90 are in substantially point contact with each other, and the contact area between them is very small. Therefore, when the load is applied in the radial direction, the ball 96
Due to this, a large pressure acts on the inner peripheral surface of the cylindrical member 90, and the load capacity is greatly reduced accordingly.

On the other hand, in the slide roller bearing shown in FIG. 8, the contact area between the roller 98 and the inner peripheral surface of the cylindrical member 90 is relatively large, but on the other hand, it has the following drawbacks.

In order to make the roller 98 rollable,
A flat roller sliding surface 90a must be formed not only on the outer peripheral surface of the shaft member 92 but also on the inner peripheral surface of the cylindrical member 90. The work of forming such a flat surface on the inner peripheral surface of the cylindrical member 90 is much more difficult than the work of forming a flat surface or a groove on the outer peripheral surface of the shaft member 92, and it is necessary to use a special processing device. Yes, the cost is high. Especially, when the inner diameter of the cylindrical member 90 is small, the manufacture becomes extremely difficult. If the position of the roller sliding surface 90a on the side of the cylindrical member 90 and the position of the roller sliding surface 92b on the side of the shaft member 92 are slightly displaced in the circumferential direction, the contact between these roller sliding surfaces 90a, 92b and the roller 98 is locally generated. It shortens the life of the bearing. That is, if the processing accuracy of each member is lowered even a little, there is no method for compensating for this and the bearing performance is immediately reflected. To improve the bearing load capacity, the roller 9
It is effective to increase the number of circumferentially arranged 8 to provide more support points, but in the structure of FIG. 8, the number of flat roller sliding surfaces 90a that can be formed on the inner circumferential surface of the cylindrical member 90 is limited. Therefore, the increase in the number of arranged rollers is also significantly restricted.

In view of such circumstances, it is an object of the present invention to provide a slide roller bearing which is easy to manufacture and has a high load capacity.

[0009]

As a means for solving the above problems, the present invention provides a roller between an inner peripheral surface of a cylindrical member and an outer peripheral surface of a shaft member inserted inside the cylindrical member. In a slide roller bearing in which the shaft member moves in the axial direction relative to the cylindrical member while rolling with the roller, the outer peripheral surface of the roller has a curvature substantially equal to the inner peripheral surface of the cylindrical member. A curved surface having a radius is formed, and an outer peripheral surface of the shaft member is formed with a roller groove extending in the axial direction and having an arc-shaped cross section with a radius of curvature substantially equal to that of the outer peripheral surface of the roller, and the roller is fitted into the roller groove. (Claim 1).

More preferably, the width dimension of the roller is set to be substantially equal to the width dimension of the roller groove (claim 2).

Further, it is more preferable that the radius of curvature of the entire outer peripheral surface of the roller or both ends thereof is set to be slightly smaller than the radius of curvature of the inner peripheral surface of the cylindrical member and the radius of curvature of the roller groove. Item 3). Here, "slightly small" means that when the roller elastically deforms in the flat direction due to the radial load generated when the bearing is used, the roller comes into contact with the inner peripheral surface of the cylindrical member over substantially the entire width direction. It means that.

[0012]

According to the bearing of the present invention, since the roller contacts the inner peripheral surface of the cylindrical member over substantially the entire area in the width direction, the contact area between the two is relatively large. The pressure acting on the peripheral surface is low.

Moreover, since the outer peripheral surface of the roller has substantially the same curvature as the inner peripheral surface of the cylindrical member, it is not necessary to form a special roller sliding surface on the inner peripheral surface of the cylindrical member, and the number of rollers arranged in the circumferential direction can be reduced. Can be set more than the conventional slide roller bearing. Further, since each roller can be displaced by a small amount in the circumferential direction with respect to the cylindrical member during the sliding operation, even if the parallelism between the cylindrical member and the shaft member is slightly deviated, this can be compensated to some extent by the circumferential displacement of each roller. Can be supplemented.

Regarding the width of the roller, the smaller the width, the smaller the contact area between the roller and the inner peripheral surface of the cylindrical member, and conversely, if the width is larger than the width of the roller groove, Both edges (corners) of the roller groove may bite into the outer peripheral surface of the roller to shorten the life of the roller. In the bearing according to claim 2, the width dimension of the roller is substantially equal to the width dimension of the roller groove. Since the dimensions are set to be equal, it is possible to secure the maximum contact area between the roller and the inner peripheral surface of the cylindrical member while preventing both peripheral edge portions of the roller groove from biting into the outer peripheral surface of the roller.

In the bearing of claim 3, the radius of curvature of the entire outer peripheral surface of the roller or both ends thereof is slightly smaller than the radius of curvature of the inner peripheral surface of the cylindrical member and the radius of curvature of the groove surface of the roller groove. The load applied to both ends of the roller (so-called edge load) is reduced, and the outer peripheral surface of the roller contacts the inner peripheral surface of the cylindrical member and the roller groove surface over substantially the entire width direction due to elastic deformation of the roller in the flat direction during use. To do. Further, if the roller maximum outer diameter is set to be smaller than the distance between the inner peripheral surface of the cylindrical member and the roller groove surface to generate radial preload, the stability of the bearing is further enhanced.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described with reference to FIGS.

In FIGS. 1 to 3, a shaft member (hollow shape in this embodiment) 12 is inserted inside the cylindrical member 10, and between the outer peripheral surface of the shaft member 12 and the inner peripheral surface of the cylindrical member 10. A cylindrical retainer 14 is provided on the inner surface of the roller, and the plurality of rollers 16 are rotatably held by the retainer 14. More specifically, a plurality of substantially rectangular through holes 15 are arranged in parallel in the axial direction on the cylindrical wall of the retainer 14 at predetermined intervals (120 ° in the illustrated example) in the circumferential direction. The roller 16 is fitted in.

As shown in FIGS. 3 and 4, each roller 16
The outer peripheral surface 18 of the cylindrical member 1 has a curved surface and the radius of curvature thereof is 1
It is set equal to the radius of curvature R of the inner peripheral surface of 0. A roller groove 13 extending in the axial direction is formed at a position corresponding to each roller 16 on the outer peripheral surface of the shaft member 12,
These roller grooves 13 have an arcuate cross section having a radius of curvature equal to the radius of curvature R, and each roller 16 is fitted in each roller groove 13.

That is, each roller 16 is sandwiched between the inner peripheral surface of the cylindrical member 10 and the groove surface of the roller groove 13. Here, the maximum outer diameter of each roller 16 is set to be equal to the distance between the inner peripheral surface of the cylindrical member 10 and the groove surface of the roller groove 13, and the width dimension of each roller 16 is set to the roller groove 13.
Is set to be equal to the width dimension of. And each roller 1
The shaft member 12 can be relatively moved in the axial direction with respect to the cylindrical member 10 with the rolling movement of 6 (arrow in FIG. 2).

According to such a slide roller bearing, each roller 16 makes contact with the inner peripheral surface of the cylindrical member 10 over substantially the entire area in the width direction, so that a relatively large contact area between them can be secured. . Accordingly, the pressure applied from the roller to the inner peripheral surface of the cylindrical member can be reduced, and the load capacity of the entire bearing can be increased.

Moreover, since the outer peripheral surface 18 of the roller 16 is a curved surface having a radius of curvature R equivalent to that of the inner peripheral surface of the cylindrical member 10, the cylindrical member such as the conventional slide roller bearing shown in FIG. It is not necessary to form a special roller sliding surface on the inner peripheral surface. Therefore, even if the inner diameter of the cylindrical member 10 is small, it can be easily manufactured, the cost can be significantly reduced, and an eccentric load acts on each roller 16 due to an error in the forming position of the roller groove 13. Hateful. The number of rollers 16 arranged in the circumferential direction is also shown in FIG.
The number of rollers 16 can be set more than that of the slide roller bearing shown in (1), and more rollers 16 than the three rollers in the illustrated example can be arranged freely in the circumferential direction.

Further, since each roller 16 can be displaced by a small amount in the circumferential direction with respect to the cylindrical member 10 during the sliding operation,
Even if the parallelism between the cylindrical member 10 and the shaft member 12 is slightly deviated, this can be absorbed to some extent by the circumferential displacement of the rollers 16.

In this bearing, if the width dimension of the roller 16 is small, the contact area between the roller 16 and the inner peripheral surface of the cylindrical member 10 is reduced accordingly, and conversely, the roller width dimension of the roller groove 13 is smaller. If the width is larger than the width dimension, both peripheral edge portions (corner portions) of the roller groove 13 may bite into the outer peripheral surface 18 of the roller 16 to shorten the life of the roller 16. If the width dimension of is set to be substantially the same as the width dimension of the roller groove 13,
While preventing both peripheral edges of the roller groove 13 from biting into the roller outer peripheral surface 18, the roller 16 and the cylindrical member 10 are prevented.
It is possible to secure the maximum contact area with the inner peripheral surface of the.

However, in the case where the width of the roller groove 13 cannot be set large because the hardness of each roller 16 is relatively high and the shaft member 12 has a small thickness, as shown in FIG. The width of the roller 16 to the roller groove 1
It may be set larger than the width dimension of 3. With such a setting, a large contact area between the roller 16 and the cylindrical member 10 can be secured.

In the above embodiment, the outer peripheral surface 18 of the roller 16 is
The radius of curvature of the roller is set to be equal to the radius of curvature R of the cylindrical member 10, but as shown in FIG.
Or the radius of curvature of both ends of the roller outer peripheral surface 18 is set to a radius R'which is slightly smaller than the radius of curvature R of the inner peripheral surface of the cylindrical member and the radius of curvature of the roller groove 13, and the roller is used at the time of use. The outer peripheral surface 18 of the roller 16 may be brought into contact with the inner peripheral surface of the cylindrical member 10 and the groove surface of the roller groove 13 over the entire width direction by the deformation of the roller 16 in the flat direction. By such so-called crowning, the load applied to both ends of the roller 16 (so-called edge load) is reduced, and at the time of use, a large contact area between the roller 16 and the inner peripheral surface of the cylindrical member 10 is secured as in the above-described embodiment. It is possible. Further, the roller 1
By setting the maximum outer diameter of 6 to be larger than the distance between the inner peripheral surface of the cylindrical member 10 and the groove surface of the roller groove 13 to generate radial preload, the stability of the bearing can be further improved. It is possible.

[0026]

As described above, according to the present invention, in the slide roller bearing in which the roller is interposed between the cylindrical member and the shaft member, the outer peripheral surface of the roller has a radius of curvature substantially equal to the inner peripheral surface of the cylindrical member. Since a roller groove having an arcuate cross section having a curvature radius substantially equal to that of the roller outer peripheral surface is formed on the outer peripheral surface of the shaft member, the roller and the cylindrical member are formed in the same manner as the conventional slide roller bearing. It is possible to eliminate the work of forming a special roller sliding surface on the inner peripheral surface of the cylindrical member while increasing the contact area with and ensuring a sufficient load capacity. By omitting such a roller sliding surface, manufacturing can be facilitated even when the inner diameter of the cylindrical member is small, and the cost can be significantly reduced, and the number of rollers arranged in the circumferential direction can be increased as compared with the conventional slide roller bearing. This has the effect of further improving the stability of the bearing. Further, even if there is some error in the position where the roller groove is formed, this does not cause a significant offset load on each roller. Further, since each roller can be displaced by a small amount in the circumferential direction with respect to the cylindrical member during the sliding operation, even if the parallelism between the cylindrical member and the shaft member is slightly deviated, this can be compensated to some extent by the circumferential displacement of each roller. It is possible to make up for it.

Further, in the bearing according to claim 2,
Since the width dimension of the roller is set to be substantially equal to the width dimension of the roller groove, contact between the roller and the inner peripheral surface of the cylindrical member is prevented while preventing both peripheral edge portions of the roller groove from biting into the outer peripheral surface of the roller. There is an effect that the maximum area can be secured.

In the bearing according to the third aspect, the radius of curvature of the entire roller outer peripheral surface or both ends thereof is slightly smaller than the radius of curvature of the inner peripheral surface of the cylindrical member and the radius of curvature of the groove surface of the roller groove. By so-called crowning, the load applied to both ends of the roller (so-called edge load) can be reduced, and, during use, the outer peripheral surface of the roller is elastically deformed in the flat direction over substantially the entire widthwise direction of the inner peripheral surface of the cylindrical member. And, there is an effect that it can be brought into contact with the roller groove surface.

[Brief description of drawings]

FIG. 1 is a sectional front view of a slide roller bearing according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is a sectional front view showing a main part of the slide roller bearing.

FIG. 4 is a perspective view of a roller used for the slide roller bearing.

FIG. 5 is a sectional front view showing a modified example of the slide roller bearing.

FIG. 6 is a sectional front view showing a modified example of the slide roller bearing.

FIG. 7 is a sectional front view showing a conventional slide ball bearing.

FIG. 8 is a sectional front view showing a conventional slide roller bearing.

[Explanation of symbols]

 10 Cylindrical member 12 Shaft member 13 Roller groove 16 Roller 18 Roller outer peripheral surface R Curvature radius of cylindrical member inner peripheral surface

Claims (3)

[Claims] 1. A roller is interposed between an inner peripheral surface of a cylindrical member and an outer peripheral surface of a shaft member inserted inside the cylindrical member,
In a slide roller bearing in which the shaft member moves axially relative to the cylindrical member while the roller is rolling, the outer peripheral surface of the roller has a radius of curvature substantially equal to the inner peripheral surface of the cylindrical member. A curved surface is formed on the outer peripheral surface of the shaft member, the roller groove extending in the axial direction and having an arc-shaped cross section having a radius of curvature substantially equal to that of the outer peripheral surface of the roller, and the roller is fitted into the roller groove. A characteristic slide roller bearing. 2. The slide roller bearing according to claim 1, wherein a width dimension of the roller and a width dimension of the roller groove are set to be substantially equal to each other. 3. The slide roller bearing according to claim 1, wherein the radius of curvature of the entire outer peripheral surface of the roller or both ends thereof is smaller than the radius of curvature of the inner peripheral surface of the cylindrical member and the radius of curvature of the roller groove. A slide roller bearing characterized by being set to a small size.