JP2003214438A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain increase of running torque and heat generation of a rolling bearing due to shear of a lubricant, by straightening the flow of the lubricant caused by slip of respective rolling body surfaces with respect to respective pocket inside surfaces, for instance, in fast rotation. <P>SOLUTION: On the inside surfaces of each pocket 11 of the holder 10, a plurality of fine groves 12 nearly parallel with the relative movement direction of the rolling body surface to the inside surface of the pocket 11 are formed. The relative movement direction of each rolling body surface to the inside surface of the corresponding pocket 11 is a circumferential direction of a circle formed by using, as a center axis, a virtual line generally parallel with the rotation axis of a bearing inner ring via the center of the pocket 11. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings. The present invention relates to improvement of low torque performance and low heat generation performance of rolling bearings used in general industrial machines such as machine tools and mainly used in a high speed rotation range, and extension of life.

[0002]

2. Description of the Related Art As a conventional rolling bearing, there is a ball bearing in which a plurality of rolling elements held by a cage are incorporated between a pair of inner and outer races each having a raceway surface. As shown in FIG. 28, the retainer 30 is formed in an annular shape, and each rolling element can be rolled in a plurality of pockets 31 opened on the inner peripheral side at predetermined intervals in the circumferential direction. keeping. However, since the inner peripheral surface 31a of each pocket 31 of the cage 30 is formed as a smooth surface, it has a poor lubricating oil retention property and has a large contact area with each rolling element to suppress heat generation. There was a problem that it was difficult.

Therefore, as shown in FIGS. 29 (a) to 29 (c), as a rolling bearing cage 40 aiming at solving the problem of heat generation between each rolling element and each pocket of the cage, the following patent document is used. As shown in FIG. 29 (a), the thin groove 42 parallel to the inner peripheral surface of the pocket 41 holding each rolling element is shown in FIG.
What has formed is described. The narrow groove 42 is formed along the depth direction of each pocket 41 as shown in FIG. 29 (b), or along the circumferential direction as shown in FIG. 29 (c).

[0004]

[Patent Document 1] JP-A-8-184318 (second to second)
(Page 3, Figure 1)

[0005]

However, the conventional rolling bearing cage 4 shown in FIGS. 29 (a) to 29 (c) is used.
At 0, the narrow groove 42 on the inner peripheral surface of the pocket 41 does not follow the direction in which the movement direction of the rolling element surface accompanying the rotation of the rolling element is taken into consideration, and the movement direction of the rolling element surface and the thin inner circumferential surface of the pocket 41 are narrowed. The direction of the groove 42 does not substantially match. Therefore, there is a problem that the heat generated between the surface of each rolling element and the inner peripheral surface of each pocket 41 of the cage 40 cannot be sufficiently suppressed. In addition, there is a problem in that there is a large variation in the lubrication state between the inner peripheral surface of the pocket 41 of the cage 40 and the rolling elements due to the lubricant, and abrasion of the inner peripheral surface of the pocket 41 of the cage 40 and the rolling elements cannot be sufficiently suppressed. there were.

The present invention is capable of rectifying the flow of the lubricant caused by the slip between the surface of each rolling element and the inner peripheral surface of each pocket of the cage at the time of high speed rotation, and the rolling bearing caused by the shearing of the lubricant. It is an object of the present invention to provide a rolling bearing capable of suppressing an increase in rotation torque and heat generation of the cage and further reducing wear of the inner peripheral surface of the pocket of the cage and the rolling elements.

[0007]

The above object of the present invention is to provide a rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings. This can be achieved by a rolling bearing characterized in that a plurality of narrow grooves are formed on the inner peripheral surface of the pocket, the plurality of fine grooves being substantially parallel to the relative movement direction of the rolling element surface with respect to the inner peripheral surface of the pocket.

In the rolling bearing having the above structure, for example, when rotating at high speed, each rolling element also rotates at high speed, and the sliding speed between the surface of each rolling element and the inner peripheral surface of each pocket of the cage becomes high. At this time, the flow of the lubricant is caused by the slip between the surface of each rolling element and the inner peripheral surface of each pocket of the cage. The flow of the lubricant is guided and narrowed by the thin grooves formed on the inner peripheral surface of each pocket of the cage. Therefore, shearing of the lubricant is significantly suppressed, increase in the rotational torque of the rolling bearing and heat generation due to shearing of the lubricant are avoided, and power loss is reduced.

It is preferable that the groove formed on the inner peripheral surface of each pocket of the cage has a cross-sectional shape that tapers in the groove depth direction. According to this, the effect of reducing the fluid friction force is obtained, and the smooth movement of the lubricant in the groove is ensured.

The cross-sectional dimension of the groove formed on the inner peripheral surface of each pocket of the cage is the ratio of the height to the ball diameter h / D =
0.002-0.01, and the ratio of width to ball diameter s
It is preferable that /D=0.004 to 0.04. According to this, the effect of reducing the fluid friction force is obtained, and the smooth movement of the lubricant in the groove is ensured.

Further, the above object of the present invention is to provide a rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings. Can be achieved by a rolling bearing characterized in that a plurality of grooves for generating dynamic pressure are formed.

In the rolling bearing having the above structure, when the rolling element rotates in the predetermined direction, the lubricant flows along the predetermined direction in the groove for generating the dynamic pressure, and the pressure is generated in the groove.
By this pressure, the rolling element is supported by the cage in a non-contact state. Therefore, wear of the inner peripheral surface of the pocket of the cage and the rolling elements is reduced, and the service life is extended.

It is preferable that the plurality of grooves for generating dynamic pressure of the retainer are formed of herringbone grooves formed in a dogleg shape. The herringbone groove ensures high load capacity, stability and oil retention.

The direction of the letter to the herringbone groove is
The cage is preferably formed so as to face the claw side on the inner peripheral surface of each pocket. According to this, as the rolling element rotates, the lubricant flows in the groove for dynamic pressure generation toward the dogleg-shaped tip of the herringbone groove, and the lubricant is sufficiently applied to the claw side of the inner peripheral surface of each pocket. A large amount of lubricant is supplied. Therefore, the lubricant can be efficiently supplied to necessary portions such as the race surface.

The area where the groove is formed on the inner peripheral surface of each pocket of the cage is preferably 30 to 70% of the surface area of the inner peripheral surface of each pocket. According to this, the pressure is smoothly generated in the groove due to the flow of the lubricant, and the rolling element is reliably supported by the cage in the non-contact state.

Further, the above object of the present invention is to provide a rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings, wherein the cage has an outer peripheral surface or an inner peripheral surface. A plurality of lubricant reservoir grooves are formed on at least a part of the surface, and a plurality of grooves for dynamic pressure generation are formed on the inner peripheral surface of each pocket, and the lubricant reservoir groove and the groove for dynamic pressure generation are formed. Can be achieved by a rolling bearing characterized in that

In the rolling bearing having the above structure, the lubricant reservoir groove and the groove for generating dynamic pressure are communicated with each other, so that the lubricant may be depleted from the inner peripheral surface of the pocket of the cage, for example. Even if it falls, the surface tension (capillary phenomenon) causes the lubricant to be supplied from the lubricant reservoir groove to the groove for generating dynamic pressure. Therefore, the pressure is smoothly generated in the groove due to the flow of the lubricant, and the rolling element is reliably supported by the cage in a non-contact state.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION The first of the rolling bearings of the present invention is described below.
The embodiment will be described in detail with reference to FIGS. 1 is an overall perspective view of a cage showing a first embodiment of a rolling bearing of the present invention, FIG. 2 is a schematic perspective view showing a pocket inner peripheral surface of the cage in FIG. 1, and FIG. 3 is a perspective view of the rolling bearing in FIG. FIG. 4 is a graph showing the total heat generation amount compared with the conventional example, and FIG. 4 is a graph showing the heat generation amount of the pocket portion of the rolling bearing in FIG. 1 compared with the conventional example.

As shown in FIGS. 1 and 2, the ball bearing, which is the rolling bearing of this embodiment, includes a pocket 11 of a cage 10.
A plurality of rolling elements (not shown) held by the above are incorporated between a pair of inner and outer rings (not shown) having raceway surfaces. Since this ball bearing is mainly used for supporting a radial load, the rotation axis of each rolling element is substantially parallel to the rotation axis of the inner ring. Therefore, the movement of the surface of each rolling element with respect to the inner peripheral surface of each pocket 11 of the cage 10 is a circular movement with the virtual line passing through the center of the pocket 11 and being substantially parallel to the rotation axis of the inner ring.

In the ball bearing of this embodiment, a plurality of fine grooves 12 are provided on the inner peripheral surface of each pocket 11 of the cage 10 so as to be substantially parallel to the movement direction of the rolling element surface. The width, depth and interval of the narrow groove 12 are all set to 0.01 mm. (In FIG. 2, it is exaggerated from the actual product for the sake of clarity.)

The operation of this embodiment will be described. In the ball bearing of the present embodiment, for example, during high-speed rotation, each rolling element also rotates at high speed, and the sliding speed between the surface of each rolling element and the inner peripheral surface of each pocket 11 of the cage 10 is also high. At this time, the lubricant flows between the surface of each rolling element and the inner peripheral surface of each pocket 11 of the cage 10 due to slippage. The flow of the lubricant is substantially parallel to the relative movement direction of each rolling element surface with respect to the inner peripheral surface of each pocket 11 of the cage 10, and is guided by the narrow groove 12 formed in the inner peripheral surface of each pocket 11. And it is rectified. Therefore, the shearing of the lubricant is greatly suppressed,
Increase in rotational torque of ball bearings due to lubricant shearing,
Also, heat generation is suppressed, and power loss is reduced.

Next, a second embodiment of the rolling bearing of the present invention will be described in detail with reference to FIG. FIG. 5 is a schematic perspective view showing an inner peripheral surface of the pocket of the cage of the rolling bearing of this embodiment. As shown in FIG. 5, the ball bearing, which is the rolling bearing of the present embodiment, is mainly used for supporting an axial load. Therefore, the rotary shaft of each rolling element forms a substantially constant angle with the rotary shaft of the inner ring. keep. Therefore, the relative motion of the surface of each rolling element with respect to the inner peripheral surface of each pocket 21 of the cage 20 is centered on the rotation axis of the rolling element which passes through the center of the pocket 21 and has a substantially constant angle with the rotation axis of the inner ring. It becomes a circular movement. The ball bearing of the present embodiment is provided with each pocket 2 of the cage 20.
A plurality of narrow grooves 22 that are substantially parallel to the movement direction of the surface of the rolling element are formed on the inner peripheral surface of the roller 1. Note that other configurations and operations are the same as those in the first embodiment.

As described above, according to the above embodiments,
Narrow grooves 12 and 22 are formed on the inner peripheral surfaces of the pockets 11 and 21 of the cages 10 and 20, respectively, and the narrow grooves 12 and 22 are relative movements of the rolling element surface with respect to the inner peripheral surfaces of the pockets 11 and 21. It is provided substantially parallel to the direction. Each pocket 11,
21. In the first embodiment, the relative movement direction of each rolling element surface with respect to the inner peripheral surface is the circumferential direction of a circle having a virtual axis passing through the center of the pocket 11 and being substantially parallel to the rotation axis of the inner ring as the central axis. is there. Further, in the second embodiment, it is a circumferential direction of a circle that passes through the center of the pocket 21 and has the rotation axis of the rolling element having a substantially constant angle with the rotation axis of the inner ring as the central axis.

Therefore, for example, at the time of high-speed rotation, the flow of the lubricant caused by slippage between the surface of each rolling element and the inner peripheral surface of each pocket 11, 21 of the cage 10, 20 is caused by the inner peripheral surface of each pocket 11, 21. The flow can be rectified by the fine grooves 12 and 22 on the surface, and the fluid resistance of the lubricant can be reduced. As a result, it is possible to suppress an increase in the rotation torque of the ball bearing and heat generation due to shearing of the lubricant, and it is possible to reduce power loss due to the shearing force of the lubricant, resulting in low torque performance and low heat generation of the ball bearing. The performance can be improved.

[0025]

EXAMPLE Next, a comparative experiment of the total calorific value (W) between the ball bearing having the cage 10 of the above embodiment and the ball bearing having the conventional cage (see FIG. 28) was conducted. All ball bearings had an inner diameter of 17 mm, an outer diameter of 47 mm, and a width of 14 mm, and the experimental conditions were a radial load of 100 mm.
kgf and rotation speed were 20000 rpm. as a result,
As shown in FIG. 3, in the ball bearing of the first embodiment, the total calorific value is kept low as compared with the ball bearing of the conventional example.

Further, the cage 10 for the ball bearing of the above embodiment.
The calorific value (W) of the pocket portion, that is, the calorific value due to the fluid frictional resistance generated between the surface of each rolling element and the inner peripheral surface of each pocket of the cage was calculated. As a result, as shown in FIG.
In the ball bearing of the first embodiment, the heat generation amount of the pocket portion of the cage 10 is suppressed to about 10% lower than that of the conventional ball bearing. Therefore, the above-described narrow groove 12 is formed on the inner peripheral surface of each pocket 11 of the cage 10, and is formed substantially parallel to the relative movement direction of each rolling element surface with respect to the inner peripheral surface of each pocket 11. The effect was proven.

FIG. 6 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a third embodiment of the present invention, and FIG. 7 is shown in FIG.
FIG. 3 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing of FIG. FIG. 8 is a schematic cross-sectional view of the cage of the ball bearing shown in FIG. 6 as viewed from the side, in which (a) shows the inner ring side and (b) shows the outer ring side. FIG. 9 is a schematic perspective view showing the entire cage of the ball bearing shown in FIG.

In the ball bearing 50 of the third embodiment shown in FIG. 6, the cage 60 is a crown cage as shown in FIG. 9, and a plurality of pockets 61 for holding the rolling elements 51 have a pair of pockets 61, respectively. The holding claws 62 are projected. Further, a plurality of grooves 63 for generating dynamic pressure are formed on the inner peripheral surface of each pocket 61 of the cage 60. The plurality of grooves 63 for generating dynamic pressure are herring horn grooves 63a formed in a dogleg shape.
And a straight groove 63b linearly formed between the herringbone grooves 63a. The herringbone groove 63a is formed so that the dog-legged direction is opposite to the right and left sides in FIG. 7 with the straight groove 63b interposed therebetween.

That is, in the herringbone groove 63a, on the side of the holding claw 62 on the left side in FIG. 7 on the inner peripheral surface of the pocket 61, the tip of the V-shape is downward in FIG.
On the holding claw 62 side on the right side in FIG. 7 on the inner peripheral surface of the pocket 61, the tip of the V-shape is formed to face upward in FIG. 7. The herring horn groove 63a is widely used for a hydrodynamic bearing because it has high load capacity, stability, and oil retention. Further, the straight groove 63b has a function of supplying a lubricant to the herringbone grooves 63a on both left and right sides in FIG.

The area of the inner peripheral surface of each pocket 61 of the cage 60 in which the groove 63 for generating dynamic pressure is formed is 30 to 70% of the surface area of the inner peripheral surface of each pocket 61. The cross-sectional shape of the groove 63 is rectangular, triangular,
For example, an arc shape. The cross-sectional dimension of the groove 63 has a height h = 0.0.
02-0.02 mm and width s = 0.1-1.0 m
m. The groove 63 is formed by, for example, forming a groove shape in advance in a mold for injection-molding the cage 60, thereby forming the cage 6
It is formed simultaneously with zero injection molding.

As shown in FIGS. 8A and 8B, a plurality of lubricant reservoir grooves 64 are formed on a part of the outer peripheral surface and the inner peripheral surface of the cage 60. Each lubricant reservoir groove 64 is
When the lubricant is exhausted from the inner peripheral surface of the pocket 61 of the cage 60, the lubricant is communicated along the direction of arrow D in FIG. 8 due to the surface tension (capillary phenomenon) when the lubricant is exhausted. Is supplied to the groove 63 for generating dynamic pressure. The height and width of each lubricant reservoir groove 64 are preferably equal to or greater than that of the dynamic pressure generating groove 63.

The operation of the ball bearing 50 of the third embodiment will be described. In the ball bearing 50 of the third embodiment, the rolling elements 51 are shown in FIG.
When rotating in the direction of the middle arrow A, in the dynamic pressure generating groove 63 of the cage 60, the lubricant flows in the direction of the arrow B in FIG. 6 toward the dogleg-shaped tip end of the herringbone groove 63a, and the dynamic pressure is generated. Pressure is generated in the groove 63 by the same principle as that of the fluid bearing. Due to this pressure, the rolling elements 51 are supported by the cage 60 in a non-contact state. Further, since the herringbone groove has a function of scraping oil into the inside of the cage pocket, it has an effect of retaining oil even when the supply of oil from the outside is cut off. Therefore, wear of the inner peripheral surface of the pocket 61 of the cage 60 and the rolling elements 51 is reduced, and the life of the ball bearing 50 is extended.

In the above embodiment, if the rolling element 51 is rotated in the opposite direction to the above, negative pressure or cavitation is generated in the dynamic pressure generating groove 63 of the cage 60, and the rolling element 51 is prevented. Since the dynamic pressure for supporting in a non-contact state is not generated, it is necessary to pay attention to the rotation direction of the rolling element 51 and the formation direction of the groove 63 for generating the dynamic pressure on the inner peripheral surface of each pocket 61 of the cage 60. There is.

FIG. 10 is a schematic sectional view of a main part of a ball bearing showing a fourth embodiment of the rolling bearing of the present invention, and FIG.
It is the schematic which expands and shows the pocket inner peripheral surface of the cage of the ball bearing of FIG. In the ball bearing 70 of the fourth embodiment shown in FIGS. 10 and 11, a preload is applied to the outer ring 71 and the inner ring 72 in the direction of arrow C in FIG. Further, the groove 81 for generating the dynamic pressure of the cage 80 is formed at an angle of about 45 ° with respect to the rotation direction of the rolling element 73 so as to face the holding claw 62 side of each pocket 61 (see FIG. 9). . That is, the dynamic pressure generating groove 81 is composed of an oblique groove 81a formed obliquely with respect to the rotation direction of the rolling element 73 and a straight groove 81b linearly formed between the oblique grooves 81a. Other configurations are the same as those in the third embodiment.

The operation of the ball bearing of the fourth embodiment will be described.
In the ball bearing 70 of the fourth embodiment, the groove 81 for generating the dynamic pressure of the cage 80 is inclined at about 45 ° with respect to the rotating direction of the rolling element 73 so that the groove 81 for generating the dynamic pressure faces the holding claw 62 side of each pocket 61. 10 is formed, when the rolling element 73 rotates in the direction of arrow A in FIG. 10, in the groove 81 for generating dynamic pressure, arrow B in FIG.
The lubricant flows in the direction. As a result, a sufficient amount of lubricant is supplied to the holding claw 62 side on the inner peripheral surface of each pocket 61, and the groove 8 is formed by the same principle as that of the hydrodynamic bearing.
Pressure is generated within 1. By this pressure, the rolling elements 73 are supported by the cage 80 in a non-contact state. Therefore, wear of the inner peripheral surface of the pocket 61 of the cage 80 and the rolling elements 73 is reduced.

Here, the outer ring 71 and the inner ring 7 of the ball bearing 70.
Preload is applied to 2 in the direction of arrow C in FIG.
For example, in a conventional ball bearing 90 as shown in FIG. 30, the rolling element 91 is preloaded in the direction of arrow C in FIG. 30, and the outer ring raceway groove 92 and the retainer 1 on the retaining claw 101 side of the retainer 100 are retained.
No. 00 is in contact with the inner ring raceway groove 93 on the back side to operate. In such a case, according to the result of the visualization investigation by the present inventors, the lubricant does not circulate on the holding claw 101 side of the retainer 100 and collects on the back side of the retainer 100. It is difficult for an oil film to be formed between 92 and the rolling element 91.

However, in the ball bearing 70 of this embodiment, the lubricant flows in the groove 81 for generating the dynamic pressure of the retainer 80 in the direction of arrow B in FIG.
A sufficient amount of lubricant is supplied to the 2 side. Therefore, the lubricant can be efficiently supplied to necessary portions such as the race surface.
Further, pressure is generated in the groove 81 by the same principle as that of the hydrodynamic bearing, and the rolling element 73 is supported by the retainer 80 in a non-contact state by this pressure.

FIG. 12 is a schematic sectional view of a main part of a ball bearing showing a fifth embodiment of the rolling bearing of the present invention, and FIG.
It is the schematic which expand | deploys and shows the pocket inner peripheral surface of the cage | basket of the ball bearing of FIG. In the ball bearing 110 of the fifth embodiment shown in FIGS. 12 and 13, the groove 121 for generating the dynamic pressure of the cage 120 is a herring horn groove 1 formed in a dogleg shape.
21a and a straight groove 121b linearly formed between the herringbone grooves 121a. The herringbone groove 121a is formed so that the dog-legged direction is opposite to the right and left sides in FIG. 13 with the straight groove 121b interposed therebetween.

That is, the herringbone groove 121a is
On the side of the holding claw 62 on the left side in FIG. 13 of the inner peripheral surface of the pocket 61 (see FIG. 9), the tip of the V-shape is inclined downward at an angle of about 45 ° to the left in FIG. 13 is formed on the right side in FIG. 13 on the side of the holding claw 62 so that the tip of the V-shape is inclined upward at an angle of about 45 ° in FIG. Regarding the operation of this embodiment, the fourth
It is similar to the embodiment.

FIG. 14 is a schematic sectional view of an essential part of a ball bearing showing a rolling bearing according to a sixth embodiment of the present invention, and FIG.
It is the schematic which expands and shows the pocket inner peripheral surface of the cage of the ball bearing of FIG. In the ball bearing 130 of the sixth embodiment shown in FIGS. 14 and 15, the groove 141 for generating the dynamic pressure of the cage 140 is a herring horn groove 1 formed in a dogleg shape.
41a and a straight groove 141b linearly formed between the herringbone grooves 141a. The herringbone groove 141a is formed so that the dog-legged direction is opposite to the right and left sides in FIG. 7 with the straight groove 141b interposed therebetween.

That is, the herringbone groove 141a is
On the left side of the holding claw 62 in FIG. 15 on the inner peripheral surface of the pocket 61 (see FIG. 9), the tip of the V-shape is diagonally downward left in FIG. 15, and the inner peripheral surface of the pocket 61 in FIG. On the side of the holding claw 62 on the right side, the tip of the V shape is
5 is formed so as to be obliquely upward right in the middle. Other configurations and operations are the same as those in the fourth embodiment.

FIG. 16 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a seventh embodiment of the present invention, and FIG.
It is the schematic which expands and shows the pocket inner peripheral surface of the cage | basket of the ball bearing of FIG. In the ball bearing 150 of the seventh embodiment shown in FIGS. 16 and 17, the groove 161 for generating the dynamic pressure of the cage 160 has a curved portion 161a that curves at 90 °, and a linear shape that is continuous with the curved portion 161a. It is composed of a section 161b. The linear portion 161b has the holding claw 6 that is larger than the curved portion 161a on the inner peripheral surface of the pocket 61 (see FIG. 9).
It is formed on the second side.

That is, on the holding claw 62 side on the left side in FIG. 17 on the inner peripheral surface of the pocket 61, the linear portion 161b is located on the left side in FIG. 17 of the curved portion 161a, and the pocket 6t.
On the side of the holding claw 62 on the right side in FIG. 17 on the inner peripheral surface, the linear portion 161b is formed on the right side in FIG. 17 of the curved portion 161a. Other configurations and operations are the same as those in the fourth embodiment.

FIG. 18 is a schematic sectional view of an essential part of a ball bearing showing an eighth embodiment of the rolling bearing of the present invention, and FIG.
It is the schematic which expands and shows the pocket inner peripheral surface of the cage | basket of the ball bearing of FIG. In the ball bearing 170 of the eighth embodiment shown in FIGS. 18 and 19, the structure of the cage 80 is the same as that of the fourth embodiment, but the cage 80 is
The rolling element 73 is held from the side opposite to that of the fourth embodiment (the left side of the rolling element 73 in FIG. 18 in this embodiment).
In the middle, the rotation direction A of the rolling elements 73 and the lubricant flow direction B are opposite to those in the fourth embodiment.

That is, when the rolling element 73 rotates in the direction of arrow A in FIG. 19, the lubricant flows in the direction of arrow B in FIG. Due to the above principle, pressure is generated in the groove 81. By this pressure, the rolling elements 73 are supported by the cage 80 in a non-contact state. As a result, the pocket 61 of the retainer 80 (see FIG.
Wear of the inner peripheral surface and the rolling elements 73 is reduced.

FIG. 20 is a schematic sectional view of an essential part of a ball bearing showing a ninth embodiment of the rolling bearing of the present invention, and FIG.
It is the schematic which expand | deploys and shows the pocket inner peripheral surface of the cage | basket of the ball bearing of FIG. In the ball bearing 180 of the ninth embodiment shown in FIGS. 20 and 21, the retainer 190 is the rolling element 73.
Is held from the side opposite to the fifth embodiment (the left side of the rolling element 73 in FIG. 20 in the present embodiment). In addition, the holder 190
Herringbone groove 191a of groove 191 for generating dynamic pressure of
On the side of the holding claw 62 on the left side in FIG. 21 on the inner peripheral surface of the pocket 61 (see FIG. 9), the tip of the V-shape is inclined downward at an angle of about 45 ° in FIG.
On the side of the holding claw 62 on the right side in FIG. 21 on the inner peripheral surface, the tip of the V-shape is formed so as to face upward at an angle of about 45 ° to the left in FIG. For other configurations, refer to the above fifth.
It is similar to the embodiment.

The operation of the ball bearing of the ninth embodiment will be described.
In the ball bearing 180 of the ninth embodiment, the rolling element 73 is shown in FIG.
When rotated in the direction of the middle arrow A, the lubricant flows in the direction of the arrow B in FIG.
Pressure is generated in the groove 191 according to the same principle as that of the hydrodynamic bearing. Due to this pressure, the rolling elements 73 are supported by the cage 190 in a non-contact state. As a result, wear of the inner peripheral surface of the pocket 61 of the cage 190 and the rolling elements 73 is reduced.

FIG. 22 is a schematic sectional view of the essential parts of a ball bearing showing a tenth embodiment of the rolling bearing of the present invention.
FIG. 23 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing of FIG. 22 in a developed manner. In the ball bearing 200 of the tenth embodiment shown in FIGS. 22 and 23, the herringbone groove 211a of the dynamic pressure generating groove 211 of the cage 210 is the left side in FIG. 23 on the inner peripheral surface of the pocket 61 (see FIG. 9). On the side of the holding claw 62 of FIG. 23, the tip of the V-shape is diagonally upward to the right in FIG.
On the side of the holding claw 62 on the right side of the middle, the tip of the V-shape is formed so as to face obliquely downward to the left in FIG. Other configurations and operations are similar to those of the ninth embodiment.

FIG. 24 is a schematic sectional view of the essential parts of a ball bearing showing an eleventh embodiment of the rolling bearing of the present invention.
FIG. 25 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG. 24 in a developed manner. In the ball bearing 220 of the eleventh embodiment shown in FIGS. 24 and 25, the groove 231 for generating the dynamic pressure of the cage 230 has a curved portion curved at 90 ° and a linear portion continuous with the curved portion. Curved groove 231a having
And a straight groove 231b linearly formed between the curved grooves 231a. The straight portion of the curved groove 231a communicates with the straight groove 231b in the orthogonal direction.

That is, on the side of the holding claw 62 on the left side in FIG. 25 on the inner peripheral surface of the pocket 61 (see FIG. 9), the straight portion of the curved groove 231a is on the right side in FIG. 25, the straight portion of the curved groove 231a is formed on the left side in FIG. 25 of the curved portion. The operation of this embodiment is the same as that of the ninth embodiment.

26 and 27 are schematic cross-sectional views showing examples of the cross-sectional shape of the narrow groove of the cage of the ball bearing which is each embodiment of the rolling bearing of the present invention.

Referring to FIG. 26, the cross-sectional shape of the narrow groove 241 of the cage 240 is formed in a substantially V shape. As for the height h and the width s of the fine groove 241, the dimensionless height h ⁺ is 5 to 2
When 0 and the dimensionless width s ⁺ is in the range of 9 to 70, the fluid frictional force reducing effect can be obtained. Here, h ⁺ = hw s ⁺ = sw w = (riω / ν) √ (C / 8) C = (16 / Re) / {(ri / ro) ² + ri / r
o} Re = riω ・ (ro −ri) / ν

Ri is the ball radius, ro is the pocket radius, ν is the kinematic viscosity of the lubricant, and ω is the rotational angular velocity of the ball. In each of the above-described embodiments, ri = 0.00437 [m], ro = 0.
00448 [m], ν = 0.000002 [m ² /
s] and ω = 3150 [1 / s], h is 0.
02-0.08 [mm], s is 0.04-0.3 [m
m] is effective, so h = 0.05 [mm], s
= 0.15 [mm].

Further, referring to FIG. 27, the retainer 250
The cross-sectional shape of the narrow groove 251 is formed in a substantially U shape. The height h and the width s of the narrow groove 251 can be set in the same manner as in the case of the substantially V-shaped narrow groove 241 described above.

As described above, according to the third to eleventh embodiments, the holders 60, 80, 120, 140, 160,
On the inner peripheral surface of each pocket 61 of 190, 210, 230,
Multiple grooves 63, 81, 121, 141, 1 for generating dynamic pressure
61, 191, 211, 231 are formed. Therefore, the surfaces of the rolling elements 51, 73 and the cages 60, 80,
It is possible to rectify the flow of the lubricant generated by the sliding of the inner peripheral surface of each pocket 61 of the 120, 140, 160, 190, 210, and 230, and the groove 6 is formed by the lubricant.
3, 81, 121, 141, 161, 191, 211,
231, a dynamic pressure can be generated, and the rolling elements 51.
73 to holders 60, 80, 120, 140, 160, 1
90, 210, 230 can be supported in a non-contact state. Thereby, the cages 60, 80, 120, 14
0, 160, 190, 210, 230 pockets 61
The wear of the inner peripheral surface and the rolling elements 51.73 can be reduced, and the service life can be extended.

According to the above fourth to seventh embodiments,
The grooves 81, 121, 141, 161 for generating dynamic pressure of the cages 80, 120, 140, 160 are formed obliquely with respect to the rotation direction of the rolling elements 73 so as to face the holding claw 62 side of each pocket 61. Since there is a lubricant in each pocket 61
The lubricant can be guided to the holding claw 62 side of the inner peripheral surface, and a sufficient amount of lubricant can be supplied to the holding claw 62 side of each pocket 61 in which the lubricant is difficult to circulate. Therefore, the lubricant can be efficiently supplied to a necessary portion such as the race surface, and the wear of the inner peripheral surface of the pocket 61 of the cage 80, 120, 140, 160 and the rolling element 73 can be further reduced.
As a result, the life can be further extended.

In the third to eleventh embodiments, the cages 60, 80, 120, 140, 160, 190, 2 are retained.
Although 10 and 230 are configured as a crown-shaped cage, the same effect can be obtained not only by the crown-shaped cage but also by a hollow cage. In this case, a method of forming a groove for dynamic pressure generation by rolling or etching can be considered.

[0058]

As described above, according to the rolling bearing of the present invention, a plurality of thin grooves are formed on the inner peripheral surface of each pocket of the cage, the grooves being substantially parallel to the relative movement direction of the rolling element surface with respect to the inner peripheral surface of the pocket. Is formed, it is possible to rectify the flow of the lubricant generated by the slip between the surface of each rolling element and the inner peripheral surface of each pocket of the cage by the narrow groove on the inner peripheral surface of each pocket during high-speed rotation. . Therefore, the fluid resistance of the lubricant can be reduced, the rotational torque of the rolling bearing due to the shear of the lubricant can be increased, and the heat generation can be suppressed, and the power loss due to the shearing force of the lubricant can be reduced. it can.

Further, according to the rolling bearing of the present invention, since a plurality of grooves for generating dynamic pressure are formed on the inner peripheral surface of each pocket of the cage, each rolling element surface and each pocket of the cage are formed. It is possible to rectify the flow of the lubricant generated by the sliding with the inner peripheral surface, generate dynamic pressure in the groove by the lubricant, and support the rolling elements in the cage in a non-contact state. . As a result, wear of the inner peripheral surface of the pocket of the cage and the rolling elements can be reduced, and the service life can be extended.

Further, according to the rolling bearing of the present invention, since a plurality of grooves for generating dynamic pressure are formed on the inner peripheral surface of each pocket of the cage, the surface of each rolling element and each pocket of the cage are formed. It is possible to rectify the flow of the lubricant generated by the sliding with the inner peripheral surface, generate dynamic pressure in the groove by the lubricant, and support the rolling elements in the cage in a non-contact state. . As a result, wear of the inner peripheral surface of the pocket of the cage and the rolling elements can be reduced, and the service life can be extended. Further, a plurality of lubricant reservoir grooves are formed on at least a part of the outer peripheral surface or the inner peripheral surface of the cage, and the lubricant reservoir groove and the groove for generating dynamic pressure are communicated with each other. Even if the lubricant runs out from the inner peripheral surface of the cage pocket, surface tension (capillary phenomenon) can be used to supply the lubricant from the lubricant reservoir groove to the groove for generating dynamic pressure. it can. As a result, pressure can be smoothly generated in the groove due to the flow of the lubricant, and the rolling element can be reliably supported by the cage in a non-contact state.

[Brief description of drawings]

FIG. 1 is an overall perspective view of a cage showing a first embodiment of a rolling bearing of the present invention.

2 is a schematic perspective view of an essential part showing an inner peripheral surface of a pocket of the cage in FIG. 1. FIG.

FIG. 3 is a graph comparing the total heat generation amount of the ball bearing in FIG. 1 with a conventional example.

FIG. 4 is a graph comparing a heat generation amount of a pocket portion of the ball bearing in FIG. 1 with a conventional example.

FIG. 5 is a schematic perspective view of a main part of a pocket inner peripheral surface of a cage showing a second embodiment of the rolling bearing of the present invention.

FIG. 6 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a third embodiment of the invention.

FIG. 7 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG. 6 in a developed manner.

8 is a schematic cross-sectional view of the cage of the ball bearing shown in FIG. 6 as viewed from the side.

9 is a schematic perspective view showing the entire cage of the ball bearing shown in FIG.

FIG. 10 is a schematic sectional view of an essential part of a ball bearing showing a fourth embodiment of the rolling bearing of the present invention.

FIG. 11 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing of FIG. 10 in a developed manner.

FIG. 12 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a fifth embodiment of the invention.

FIG. 13 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing in FIG. 12 in a developed manner.

FIG. 14 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a sixth embodiment of the invention.

15 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG. 14 in a developed manner.

FIG. 16 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a seventh embodiment of the invention.

FIG. 17 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG. 16 in a developed manner.

FIG. 18 is a schematic sectional view of an essential part of a ball bearing showing an eighth embodiment of the rolling bearing of the present invention.

FIG. 19 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing in FIG. 18 in a developed manner.

FIG. 20 is a schematic sectional view of a main part of a ball bearing, showing a rolling bearing according to a ninth embodiment of the invention.

21 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG. 20 in a developed manner.

FIG. 22 is a schematic sectional view of a main part of a ball bearing showing a rolling bearing according to a tenth embodiment of the invention.

FIG. 23 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing shown in FIG.

FIG. 24 is a schematic sectional view of a main part of a ball bearing showing an eleventh embodiment of a rolling bearing of the present invention.

FIG. 25 is a schematic view showing the inner peripheral surface of the pocket of the cage of the ball bearing in FIG. 24 in a developed manner.

FIG. 26 is a schematic sectional view showing an example of a pocket shape of a cage of a ball bearing which is each embodiment of the rolling bearing of the present invention.

FIG. 27 is a schematic cross-sectional view showing another example of the pocket shape of the cage of the ball bearing which is each embodiment of the rolling bearing of the present invention.

FIG. 28 is a schematic perspective view of essential parts showing an inner peripheral surface of a pocket of a conventional ball bearing cage.

FIG. 29 is a main part schematic perspective view showing another conventional cage for a rolling bearing.

FIG. 30 is a schematic sectional view of a main part of still another conventional rolling bearing.

[Explanation of symbols]

10,20 cage 11,21 pockets 12,22 narrow groove 60 cage 61 pockets 62 holding claw 63 Groove for generating dynamic pressure 63a Herring horn groove 63b Straight groove 64 Lubricant collecting groove

   ─────────────────────────────────────────────────── ─── Continued front page    F term (reference) 3J101 AA02 AA32 AA42 AA52 AA62                       BA25 BA44 CA01 CA15 DA14                       FA32

Claims (8)

[Claims] 1. A rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings, wherein the inner peripheral surface of each pocket of the retainer is arranged with respect to the inner peripheral surface of the pocket. A rolling bearing having a plurality of thin grooves formed substantially parallel to the relative movement direction of the rolling element surface. 2. A rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of bearing rings, wherein a dynamic pressure generating member is provided on an inner peripheral surface of each pocket of the cage. A rolling bearing having a plurality of grooves formed therein. 3. A plurality of grooves for generating dynamic pressure of the cage,
The rolling bearing according to claim 2, wherein the rolling bearing is formed of a herringbone groove formed in a dogleg shape. 4. The rolling bearing according to claim 3, wherein the direction of the V shape of the herringbone groove is formed to face the claw side of the inner peripheral surface of each pocket of the cage. 5. The area where the groove is formed on the inner peripheral surface of each pocket of the cage is 30 to 70% in terms of the area ratio with respect to the surface area of the inner peripheral surface of each pocket. The rolling bearing according to at least one of 4 to 4. 6. The rolling bearing according to claim 1, wherein the groove formed on the inner peripheral surface of each pocket of the cage has a cross-sectional shape that tapers in the groove depth direction. . 7. The cross-sectional dimension of the groove formed on the inner peripheral surface of each pocket of the cage has a ratio of height to ball diameter h / D =
0.002-0.01, and the ratio of width to ball diameter s
/D=0.004-0.04, The rolling bearing of Claim 1 characterized by the above-mentioned. 8. A rolling bearing in which a plurality of rolling elements respectively held in a plurality of pockets of a cage are incorporated between a pair of races, wherein the cage is plural on at least a part of an outer peripheral surface or an inner peripheral surface. The lubricant reservoir groove is formed, and a plurality of grooves for generating dynamic pressure are formed on the inner peripheral surface of each pocket, and the lubricant reservoir groove and the groove for generating dynamic pressure are communicated with each other. Rolling bearing characterized by.