WO2021215447A1 - Rolling-bearing cage and rolling bearing - Google Patents

Abstract

In a rolling-bearing cage (6), pockets (12) for holding balls (5) are formed at a plurality of circumferential positions of a ring-like body (10). In a cross section of the ring-like body cut along a plane including the centers of the pockets (12) and perpendicular to the cage axis, an outer-diameter-side radial guide gap (δ1) that is a gap in the radial direction of the ring-like body (10) between each of pocket opening edges (10a) on an outer-circumferential-surface side of the ring-like body (10) and each of the balls (5) is 1 to 2% of the diameter d5 of the ball (5). An inner-diameter-side radial guide gap δ2 that is a gap in the radial direction of the ring-like body (10) between each of pocket opening edges (10b) on an inner-circumferential-surface side of the ring-like body (10) and each of the balls (5) is at least 1.5-times the outer-diameter-side radial guide gap δ1. A band width H, which is the radial dimension of the ring-like body (10), is 40 to 45% of the diameter d5 of the ball (5).

Description

Rolling bearing cages and rolling bearings Related application

This application claims the priority of Japanese Patent Application No. 2020-077049 filed on April 24, 2020, and is cited as a part of the present application by reference in its entirety.

The present invention relates to a cage for rolling bearings and a rolling bearing, for example, a technique applied to a cage made of synthetic resin or the like and capable of suppressing abnormal noise caused by the cage.

A synthetic resin cage used for rolling bearings has been proposed (Patent Document 1).
This synthetic resin cage is composed of two annular bodies facing each other in the axial direction, and a plurality of pockets for accommodating balls are formed between the two annular bodies at intervals in the circumferential direction. This synthetic resin cage is a so-called rolling element guide type cage, and can prevent excessive temperature rise and wear of the inner peripheral surface and the outer peripheral surface of the cage as compared with the raceway ring guide type cage.

Japanese Unexamined Patent Publication No. 2013-7468

As shown in FIG. 15, when a radial load Fr is applied between the inner and outer rings 104 and 105 of the rolling bearing 100 and the rolling bearing 100 is operated at a low speed of 200,000 or less with a dn value (dn value = inner diameter d × rotation speed n). A load region LD and a non-load region NL are generated in the rolling bearing 100, and the cage 101 rotates while repeating swinging and radial deformation.

In this case, in the conventional resin corrugated cage, as shown in FIGS. 16 and 17, the radial clearance δa of the rolling element 103 between the pocket 102 and the rolling element 103 is on the inner diameter side (“B” side in FIG. 17). ) Is larger on the outer diameter side (“A” side in FIG. 17), and serves as a rolling element guide in contact with the rolling element 103 on the inner diameter side of the pocket 102. Therefore, as shown in FIGS. 15 and 18, the rolling element 103 in the non-load region NL may receive a radial force F1 from the cage pocket inner diameter guide surface 102a to vibrate the outer ring and generate an abnormal noise. ..

An object of the present invention is to provide a roller bearing cage and a rolling bearing capable of suppressing abnormal noise caused by the cage.

The rolling bearing cage of the present invention is a rolling bearing cage in which pockets for holding the rolling element are formed at a plurality of locations in the circumferential direction of the annular body.
In a cross section cut in a plane including the center of the pocket and perpendicular to the cage axis,
The radial guide clearance δ1 on the outer diameter side, which extends to the radial gap between the annular body and the opening edge of the pocket on the outer peripheral surface side of the annular body, is 1 to 2% of the diameter of the rolling element. And
Moreover, the radial guide clearance δ2 on the inner diameter side, which extends to the radial clearance of the annular body between the opening edge of the pocket on the inner peripheral surface side of the annular body and the rolling element, is the radial guide clearance δ2 on the outer diameter side. It is more than 1.5 times δ1 and
The band width, which is the radial dimension of the annular body, is 40 to 45% of the diameter of the rolling element.
The 1 to 2% of the diameter of the rolling element is more than 1% and less than 2% of the diameter of the rolling element.
40 to 45% of the diameter of the rolling element is more than 40% and less than 45% of the diameter of the rolling element.
In each of the radial guide gaps δ1 and δ2, the positional relationship between the cage and the rolling element coincides with the centers of the arrangement circles of the pockets at a plurality of locations and the centers of the arrangement circles of the plurality of rolling elements. There is even a plow in a state of positional relationship.

When the cage is used as a rolling element guide, if the radial guide clearance δ1 on the outer diameter side is set to 1% or less of the diameter of the rolling element, the guide clearance of the cage becomes too small and the temperature of the cage rises. When the radial guide clearance δ1 on the outer diameter side is 2% or more of the diameter of the rolling element, the guide clearance of the cage is large, the cage swings around, and the cage noise becomes loud.
When the band width of the cage is 40% or less of the diameter of the rolling element, the rigidity of the cage is reduced, and the cage becomes abnormal or the vibration of the cage becomes large. When the band width is 45% or more of the diameter of the rolling element, the dynamic space volume of the rolling bearing increases and the grease held in the stationary space volume decreases, which leads to a decrease in the life of the rolling bearing. In addition, the grease shear resistance between the pocket and the rolling element increases, so that the vibration or temperature rise of the cage becomes large.

According to this configuration, the rigidity of the cage can be increased by making the bandwidth of the cage more than 40% and less than 45% of the diameter of the rolling element. At the same time, the radial guide clearance δ1 on the outer diameter side is more than 1% and less than 2% of the diameter of the rolling element, and the radial guide clearance δ2 on the inner diameter side is 1.5 times or more the radial guide clearance δ1 on the outer diameter side. And. As a result, the rolling element serves as a guide for the rolling element on the outer diameter side of the pocket, and the rolling element in the non-load region does not receive a radial force from the cage. Therefore, the rolling element does not vibrate the outer ring of the rolling bearing, and the abnormal noise caused by the cage can be suppressed.

The pitch circle diameter of the pocket may be smaller than the pitch circle diameter of the rolling element. By determining the positional relationship between the pocket of the cage and the rolling element in this way, the rolling element can be easily used as a guide for the outer diameter side of the pocket.

The pocket guide surface including the opening edge of the pocket on the outer peripheral surface side and the pocket guide surface including the opening edge of the pocket on the inner peripheral surface side may be formed of curved surfaces having different curvatures. When the radial guide clearances δ1 and δ2 are defined by the plurality of pocket guide surfaces in this way, other bearings such as seals are used rather than the case where the pitch circle diameter of the pocket is smaller than the pitch circle diameter of the rolling element. It is possible to facilitate the design in which the cage is non-interfering with the components.

The pocket guide surface including the opening edge of the pocket on the outer peripheral surface side may be formed of a curved surface, and the pocket guide surface including the opening edge of the pocket on the inner peripheral surface side may be formed of a flat surface.
When the radial guide clearances δ1 and δ2 are defined by the plurality of pocket guide surfaces in this way, other bearings such as seals are used rather than the case where the pitch circle diameter of the pocket is smaller than the pitch circle diameter of the rolling element. It is possible to facilitate the design that does not interfere with the components.

The cage is composed of two annular bodies that overlap each other in the axial direction, and the respective annular bodies are arranged at predetermined intervals in the circumferential direction, and a plurality of pocket wall portions each forming an inner wall surface of the pocket. It may have a plurality of connecting plate portions that connect the pocket wall portions that are adjacent to each other in the circumferential direction. In this case, the cage can be assembled by a simple operation of two annular bodies facing each other and pushing the other annular body into one of the annular bodies in the axial direction.

The cage may have a crown shape in which the pocket is opened on one side surface in the axial direction of the annular body. In this case, the number of parts can be reduced as compared with the cage composed of two annular bodies, and the cage structure can be simplified.

The rolling bearing of the present invention is provided with the cage for the rolling bearing described in any of the above. In this case, the above-mentioned effects can be obtained for the cage for rolling bearings of the present invention.

The rolling element may be a ceramic ball. In this case, the specific gravity can be made smaller than that of a steel ball made of, for example, bearing steel, the speed of the rolling bearing can be increased, and the heat resistance can be improved.

Any combination of claims and / or at least two configurations disclosed in the specification and / or drawings is included in the present invention. In particular, any combination of two or more of each claim is included in the present invention.

The present invention will be more clearly understood from the following description of preferred embodiments with reference to the accompanying drawings. However, the embodiments and drawings are for illustration and description purposes only and should not be used to define the scope of the invention. The scope of the present invention is determined by the appended claims. In the accompanying drawings, the same reference numerals in a plurality of drawings indicate the same or corresponding parts.
It is sectional drawing of the rolling bearing provided with the cage which concerns on embodiment of this invention. It is a perspective view of the cage. It is an enlarged sectional view of the cage. FIG. 3A is a cross-sectional view taken along the line IIIB-IIIB of FIG. 3A. It is sectional drawing which cut | cut the cage in the plane which includes the center of a pocket and is perpendicular to the center of cage. It is a partially enlarged view near the pocket of FIG. It is sectional drawing which shows the positional relationship between the cage and a rolling element in a non-load region by partially enlarging. It is sectional drawing which shows the positional relationship between the cage and a rolling element in a load region partially enlarged. It is sectional drawing of the tester which acoustically tests the cage and the conventional cage. It is a figure which shows the acoustic test result of the cage. It is a figure which shows the acoustic test result of the conventional cage. It is sectional drawing which shows the vicinity of the pocket of the cage which concerns on other embodiment of this invention partially enlarged. It is sectional drawing which shows the vicinity of the pocket of the cage which concerns on still another Embodiment of this invention partially enlarged. It is sectional drawing of the rolling bearing provided with the cage which concerns on still another embodiment of this invention. It is a perspective view of the cage. It is a figure explaining the mechanism of abnormal noise generation. FIG. 5 is a cross-sectional view of a conventional cage cut along a plane including the center of a pocket and perpendicular to the center of the cage. It is a partially enlarged view of FIG. It is sectional drawing which shows the positional relationship between the conventional cage and a rolling element in a non-load region by partially enlarging.

[First Embodiment]
The cage and rolling bearing according to the embodiment of the present invention will be described with reference to FIGS. 1 to 9.
<About rolling bearings>
This rolling bearing is used, for example, as a rolling bearing for a motor. However, it is also possible to apply this rolling bearing to applications other than motors.
As shown in FIG. 1, the rolling bearing 1 of this example is a deep groove ball bearing, and is a plurality of rolling elements interposed between the inner ring 2, the outer ring 3, and the rolling surfaces 2a, 3a of the inner and outer rings 2, 3. A ball 5 which is a ball 5 and a cage 6 which holds each ball 5 are provided, and a sealing plate 4 which is a non-contact seal is provided. The ball 5 is a steel ball or a ceramic ball.

An annular space is formed between the outer circumference of the inner ring 2 and the inner circumference of the outer ring 3, and the openings at both ends of the annular space in the axial direction are closed by the sealing plates 4 and 4. Lubricating grease is sealed in the closed annular space. A seal mounting groove is formed on the inner peripheral surface of the outer ring 3, and an inner ring seal groove is formed on the outer peripheral surface of the inner ring 2. The sealing plate 4 is formed in a disk shape from a steel plate or the like. The outer end of the sealing plate 4 is attached to the seal mounting groove, and the inner end of the sealing plate 4 is inserted into the inner ring seal groove with a predetermined gap so as not to contact the inner ring 2.

<About cage 6>
As shown in FIGS. 2 and 3A, the cage 6 is of a rolling element guide type, and is composed of two synthetic resin annular bodies 10 and 10 that overlap each other in the axial direction. As shown in FIGS. 1 and 4, in the cage 6, in a state where the two annular bodies 10 and 10 are connected, the outer peripheral surfaces of the annular bodies 10 and 10 form a cylindrical surface having the same diameter, and the annular body 6 is formed. The inner peripheral surfaces of 10 and 10 form a cylindrical surface having the same diameter.

As shown in FIGS. 3A and 3B, each annular body 10 is formed by, for example, injection molding a synthetic resin. The two annular bodies 10 and 10 have the same shape and can be molded with the same mold. As the synthetic resin, for example, polyamide (for example, PA46), polyphenylene sulfide (PPS), polyetheretherketone (PEEK), or the like can be adopted. Glass fiber, carbon fiber, aramid fiber, or the like is added to the synthetic resin forming each annular body 10 in order to increase the strength.

Each annular body 10 has a plurality of semi-cylindrical pocket wall portions 13 and a plurality of connecting plate portions 14. The plurality of semi-cylindrical pocket wall portions 13 form an inner wall surface of the pocket 12 which is arranged at regular intervals in the circumferential direction and each holds the ball 5. The plurality of connecting plate portions 14 connect the pocket wall portions 13 adjacent to each other in the circumferential direction.

The connecting plate portion 14 has a mating surface 15 that comes into surface contact when the two annular bodies 10 and 10 are joined. A coupling claw 16 projecting in the axial direction and a coupling hole 17 into which the coupling claw 16 of the other annular body 10 is inserted are formed in the vicinity of the center of the mating surface 15 in the coupling plate portion 14. A hook portion 19 is formed at the axial tip portion of the coupling claw 16, and the hook portion 19 of one annular body 10 engages with a step portion 18 formed on the inner surface of the coupling hole 17 of the other annular body 10. By this engagement, the coupling claw 16 is prevented from coming off from the coupling hole 17, and the two annular bodies 10 and 10 are coupled to each other.

The joint plate portion 14 has a protruding wall portion 20 and a housing recess 21. The protruding wall portion 20 is provided at one end in the circumferential direction of the mating surface 15 of one of the annular bodies 10 so as to project in the axial direction. The accommodating recess 21 is provided at the other end of the mating surface 15 of one annular body 10 in the circumferential direction, and accommodates the protruding wall portion 20 of the other annular body 10. Since the connecting plate portion 14 has the above-mentioned protruding wall portion 20 and the accommodating recess 21, the joint of the annular bodies 10 and 10 when the two annular bodies 10 and 10 are joined is from the axial center of the pocket 12. It is designed to be in a misaligned position. Thereby, when the ball 5 comes into contact with the coupling plate portion 14 due to the delay or advance of the ball 5 during the bearing operation, it is possible to prevent the ball 5 from coming into contact with the joint position of the two annular bodies 10 and 10. .. Therefore, the ball 5 can be stably held.

In a state where the two annular bodies 10 and 10 are connected, the protruding wall portion 20 and the accommodating recess 21 are sized so that gaps 22 and 23 in the circumferential direction and the axial direction are formed between the projecting wall portion 20 and the accommodating recess 21. ing. As a result, it is possible to prevent the protruding wall portion 20 and the accommodating recess 21 from interfering with each other due to the shrinkage difference after the annular body 10 is injection-molded. 15 can be surely brought into close contact with each other.

Partial concave spherical surfaces 25 along the outer circumference of the ball 5 are formed at both ends of each pocket 12 in the circumferential direction. The partially concave spherical surface 25 is formed so as to face each other in the front-rear direction of the ball 5 with the ball 5 in between. The radius of curvature of the partially concave spherical surface 25 is set to be slightly larger than the radius of the ball 5.

4, the retainer 6 is a sectional view taken along a plane perpendicular to the cage axis L1 including the center P ₁₂ of the pocket 12 (FIG. 2). FIG. 5 is a partially enlarged view of the vicinity of the pocket 12 of FIG. Wherein the center _{P 12} of the pocket 12, as shown in FIGS. 3A and 3B, in a state bound together two annular members 10, 10, and axis L2 of the pocket wall 13, of each pocket 12 This is the point where the lines L3 passing through the centers of the partially concave spherical surfaces 25 and 25 at both ends in the circumferential direction intersect.

In the cross section shown in FIGS. 4 and 5, there is a radial guide gap δ1 on the outer diameter side of the annular body 10 with the opening edge 10a of the pocket 12 on the outer peripheral surface side of the annular body 10 and the ball 5. However, it is 1 to 2% (more than 1% and less than 2%) of the diameter d5 of the ball 5. In the positional relationship between the cage 6 and the ball 5 where the center Cp of the arrangement circle of the pocket 12 at a plurality of locations coincides with the center Cb of the arrangement circle of the plurality of balls 5, the opening edge 10a of the pocket 12 on the outer peripheral surface side The radial distance of the annular body 10 from the ball 5 inserted into the pocket 12 corresponds to the radial guide clearance δ1 on the outer diameter side.

Further, in the cross section, the radial guide clearance δ2 on the inner diameter side, which extends to the radial gap of the annular body 10 between the opening edge 10b of the pocket 12 on the inner peripheral surface side of the annular body 10 and the ball 5, is on the outer diameter side. It is 1.5 times or more the radial guide clearance δ1. The opening edge 10b of the pocket 12 on the inner peripheral surface side in the positional relationship between the cage 6 and the ball 5 in which the center Cp of the array circle of the pocket 12 at a plurality of locations coincides with the center Cb of the array circle of the plurality of balls 5. The radial distance in the annular body 10 between the ball 5 and the ball 5 inserted in the pocket 12 corresponds to the radial guide clearance δ2 on the inner diameter side.

By defining the radial guide clearance δ1 on the outer diameter side and the radial guide clearance δ2 on the inner diameter side in this way, the ball 5 is used as the pocket outer diameter side rolling element guide. Specifically, regarding the positional relationship between the pocket 12 of the cage 6 and the ball 5, the pitch circle diameter PCD ₁₂ of the pocket 12 which is the pocket PCD is smaller than _{the pitch circle diameter PCD 5} of the ball 5 which is the ball PCD. By doing so, the ball 5 is used as a pocket outer diameter side rolling element guide in the non-load region where the radial load is not applied (FIG. 6). In the load range where a radial load is applied, the ball 5 is used as a guide for the rolling element on the inner diameter side of the pocket (FIG. 7). Further, the band width H, which is the radial dimension of the annular body 10, is 40 to 45% (more than 40% and less than 45%) of the diameter d5 of the ball 5.

<Acoustic test>
Rolling bearing provided with a cage (pocket outer diameter side rolling element guide, outer diameter side guide clearance to rolling element diameter ratio: 1 to 2%, band width to rolling element diameter ratio: 40 to 45%) according to the present embodiment. And a rolling bearing equipped with a conventional cage (rolling element guide on the inner diameter side of the pocket) were subjected to an acoustic test using the testing machine 30 shown in FIG.
<Test conditions>
Nominal number of rolling bearing to be tested: 6312
Rotation speed: 3000min ^-1
Load: Radial load Fr = 4000N
Confirmation item: Presence or absence of abnormal noise due to hearing

In the testing machine 30, the drive shaft 31 is rotationally supported by the housing Hs via two rolling bearings BR1 and BR2, and one end of the drive shaft 31 in the longitudinal direction is driven by a motor (not shown) via a belt. It is configured to be rotatable around C1. Of the two rolling bearings BR1 and BR2, the rolling bearing BR1 on the right side of FIG. 8 close to the motor is used as the rolling bearing for testing, and the rolling bearing BR2 on the left side of FIG. 8 on the antimotor side is used as the support bearing. The drive shaft 31 and the inner rings of the rolling bearings BR1 and BR2 are rotated by driving the motor, and the radial load is applied to the rolling bearing BR1 by the belt load.

<Acoustic test results>

<Frequency analysis result>
According to the frequency analysis result by the testing machine 30, as shown in FIG. 9, the cage according to the present embodiment (Table 1: the cage of the present embodiment) makes an abnormal noise as compared with the conventional cage shown in FIG. The frequency band has dropped.

<Effect>
When the cage is used as a rolling element guide, if the radial guide clearance δ1 on the outer diameter side is set to 1% or less of the diameter of the rolling element, the guide clearance of the cage becomes too small and the temperature of the cage rises. When the radial guide clearance δ1 on the outer diameter side is 2% or more of the diameter of the rolling element, the guide clearance of the cage is large, the cage swings around, and the cage noise becomes loud.

If the band width of the cage is 40% or less of the diameter of the rolling element, the rigidity of the cage decreases, and the cage becomes abnormal or the vibration of the cage increases. When the band width is 45% or more of the diameter of the rolling element, the dynamic space volume of the rolling bearing increases and the grease held in the stationary space volume decreases, which leads to a decrease in the life of the rolling bearing. In addition, the grease shear resistance between the pocket and the rolling element increases, so that the vibration or temperature rise of the cage becomes large.

According to the cage 6 of the present embodiment, the rigidity of the cage 6 can be increased by setting the band width H of the cage 6 to more than 40% and less than 45% of the diameter d5 of the ball 5. At the same time, the radial guide clearance δ1 on the outer diameter side is more than 1% and less than 2% of the diameter d5 of the ball 5, and the radial guide clearance δ2 on the inner diameter side is 1.5 times the radial guide clearance δ1 on the outer diameter side. That is all. As a result, the ball 5 serves as a cartwheel guide on the outer diameter side of the pocket, and the ball 5 in the non-load region does not receive a radial force from the cage 6. Therefore, the ball 5 does not vibrate the outer ring 3, and the abnormal noise caused by the cage 6 can be suppressed.

_{By making the pitch circle diameter PCD 12} of the pocket 12 which is the pocket PCD _{smaller than the pitch circle diameter PCD 5} of the ball 5 which is the ball PCD, the ball 5 can be easily used as a cartwheel guide on the outer diameter side of the pocket.

Since the two annular bodies 10 and 10 have the same shape and can be molded with the same mold, the molds can be shared and the manufacturing cost can be reduced. Further, the cage 6 can be assembled by a simple operation in which the two annular bodies 10 and 10 are opposed to each other and the other annular body 10 is pushed in the axial direction with respect to one of the annular bodies 10.

When the rolling element is a ceramic ball, the specific gravity can be made smaller than that of a steel ball made of, for example, bearing steel, the speed of the rolling bearing 1 can be increased, and the heat resistance can be improved.

<About other embodiments>
In the following description, the same reference numerals will be given to the parts corresponding to the matters previously described in each embodiment, and duplicate description will be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described above unless otherwise specified. It produces the same action and effect from the same configuration. Not only the combination of the parts specifically described in each embodiment, but also the combinations of the embodiments can be partially combined as long as the combination does not cause any trouble.

[Second Embodiment]: Pocket Composite R Shape As shown in FIG. 11, the pocket guide surface 32 including the opening edge 10a of the pocket 12 on the outer peripheral surface side (where the opening edge 10a is located) and the inner peripheral surface side. The pocket guide surface 33 including the opening edge 10b of the pocket 12 (where the opening edge 10b is located) may be formed of curved surfaces having different curvatures from each other.

In this example, the positional relationship between the pocket 12 of the cage 6 and the ball 5 is such that the pocket PCD and the ball PCD match. The radius of curvature R ₃₂ of the outer peripheral surface side of the pocket guide surface 32 is slightly smaller than the radius of curvature R ₃₃ of the inner peripheral surface side pocket guide surface 33. Further, the center of curvature C2 of the pocket guide surface 32 on the outer peripheral surface side is located on the inner diameter side of the center of the pocket 12 and one side in the circumferential direction on the pocket guide surface side. The center of curvature C3 of the pocket guide surface 33 on the inner peripheral surface side is located at the center of the pocket 12. The pocket guide surface 33 on the inner peripheral surface side and the pocket guide surface 32 on the outer peripheral surface side are smoothly connected. Although not shown, a pocket guide surface connecting the pocket guide surface 33 on the inner peripheral surface side and the pocket guide surface 32 on the outer peripheral surface side may be formed.

In this way, when the radial guide clearances δ1 and δ2 are defined by the plurality of pocket guide surfaces 32 and 33, the pitch circle diameter of the pocket is smaller than the pitch circle diameter of the rolling element, and the seal or the like is used. It is possible to facilitate a design that does not interfere with other bearing components. Other than that, it has the same effect as that of the above-described embodiment.

[Third Embodiment]: Pocket sphere R + straight shape As shown in FIG. 12, the pocket guide surface 32 including the opening edge 10a of the pocket 12 on the outer peripheral surface side is formed of a curved surface, and the pocket 12 on the inner peripheral surface side has a curved surface. The pocket guide surface 33 including the opening edge 10b may be configured to be flat.

In this example, the positional relationship between the pocket 12 of the cage 6 and the ball 5 is such that the pocket PCD and the ball PCD match. The center of curvature C2 of the pocket guide surface 32 on the outer peripheral surface side is located on the pocket PCD and is located unilaterally in the circumferential direction on the pocket guide surface side with respect to the center of the pocket 12.

In this way, when the radial guide clearances δ1 and δ2 are defined by the plurality of pocket guide surfaces 32 and 33, the pitch circle diameter of the pocket is smaller than the pitch circle diameter of the rolling element, and the seal or the like is used. It is possible to facilitate a design that does not interfere with other bearing components. Other than that, it has the same effect as that of the above-described embodiment.

<Crown cage>
As shown in FIGS. 13 and 14, the cage 6A is provided with pockets 12 which are partially opened on one side surface of the annular body 10 and hold the balls 5 inside at a plurality of positions in the circumferential direction of the annular body 10. It may have a crown shape. The cage 6A is composed of one annular body 10, and a pocket 12 is opened on one side surface of the annular body 10 in the axial direction to form a crown shape. The pocket wall portion of each pocket 12 is formed in a partially spherical shape. The cage 6A is arranged so that the open side of the pocket faces inward in the bearing axial direction and the back side of the pocket faces the seal member 4A at a slight distance. On the open side of each pocket 12, a pair of claw-shaped tip portions 34, 34 facing in the circumferential direction are provided so as to project in the axial direction.

Also in this cage 6A, the band width H of the cage 6A is more than 40% and less than 45% of the diameter of the ball 5, and the radial guide clearance δ1 (see FIG. 5) on the outer diameter side is the diameter of the ball 5. It is more than 1% and less than 2% of d5, and the radial guide clearance δ2 on the inner diameter side (see FIG. 5) is 1.5 times or more the radial guide clearance δ1 on the outer diameter side. As a result, the ball 5 serves as a cartwheel guide on the outer diameter side of the pocket, and the ball 5 in the non-load region does not receive a radial force from the cage 6A. Therefore, the ball 5 does not vibrate the outer ring 3, and the abnormal noise caused by the cage 6A can be suppressed. Since the cage 6A is composed of one annular body 10, the number of parts can be reduced as compared with the cage composed of two annular bodies, and the cage structure can be simplified.

Although not shown, it may be a crown-shaped cage in which a pocket 12 is opened on one side surface in the axial direction of the annular body 10 and a pair of claw-shaped tip portions 34, 34 is not formed.

The pocket wall portion 13 of each annular body 10 in the first embodiment is not limited to a semi-cylindrical shape, and may be a hemispherical shape. For rolling bearings, it is possible to apply not only non-contact seals but also contact seals. Further, it may be an open type rolling bearing without a seal.

The rolling bearing is not limited to deep groove ball bearings, and may be other rolling bearings such as angular contact ball bearings and cylindrical roller bearings, for example. It is also possible to apply any of the rolling bearings to machine tools, industrial machines, vehicles and the like. It is also possible to form each annular body by 3D printer or machining.

Although the embodiment for carrying out the present invention based on the embodiment has been described above, the embodiment disclosed this time is an example in all respects and is not limiting. The scope of the present invention is shown by the scope of claims rather than the above description, and it is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

1 ... Rolling bearing 5 ... Ball (rolling element)
6, 6A ... Cage 10 ... Ring 10a ... Opening edge of pocket on outer peripheral surface 10b ... Opening edge of pocket on inner peripheral surface 12 ... Pocket, 13 ... Pocket wall 14 ... Coupling plate 32, 33 ... Pocket Information surface

Claims (8)

1. A roller bearing cage in which pockets for holding a rolling element are formed at a plurality of locations in the circumferential direction of the annular body.
   In a cross section cut in a plane including the center of the pocket and perpendicular to the cage axis,
   The radial guide clearance δ1 on the outer diameter side, which extends to the radial gap between the annular body and the opening edge of the pocket on the outer peripheral surface side of the annular body, is 1 to 2% of the diameter of the rolling element. And
   Moreover, the radial guide clearance δ2 on the inner diameter side, which extends to the radial clearance of the annular body between the opening edge of the pocket on the inner peripheral surface side of the annular body and the rolling element, is the radial guide clearance δ2 on the outer diameter side. It is more than 1.5 times δ1 and
   The band width, which is the radial dimension of the annular body, is 40 to 45% of the diameter of the rolling element.
   Roller bearing cage.
2. The roller bearing cage according to claim 1, wherein the pitch circle diameter of the pocket is smaller than the pitch circle diameter of the rolling element.
3. In the roller bearing cage according to claim 1, the pocket guide surface including the opening edge of the pocket on the outer peripheral surface side and the pocket guide surface including the opening edge of the pocket on the inner peripheral surface side are mutually aligned. A cage for rolling bearings that is composed of curved surfaces with different curvatures.
4. In the roller bearing cage according to claim 1, the pocket guide surface including the opening edge of the pocket on the outer peripheral surface side is formed of a curved surface, and the pocket guide surface including the opening edge of the pocket on the inner peripheral surface side. Rolling bearing cage consisting of a flat surface.
5. In the roller bearing cage according to any one of claims 1 to 4, the cage is composed of two annular bodies that overlap each other in the axial direction, and each annular body is formed in the circumferential direction. A roller bearing cage having a plurality of pocket wall portions arranged at predetermined intervals and each forming an inner wall surface of the pocket, and a plurality of coupling plate portions connecting the pocket wall portions adjacent to each other in the circumferential direction.
6. In the rolling bearing cage according to any one of claims 1 to 4, the cage holds a rolling bearing having a crown shape in which the pocket is opened on one side surface in the axial direction of the annular body. vessel.
7. A rolling bearing provided with a cage for the rolling bearing according to any one of claims 1 to 6.
8. The rolling bearing according to claim 7, wherein the rolling element is a ceramic ball.

Images