JP2016138643A - Wave-shaped holder for ball bearing and ball bearing using wave-shaped holder for ball bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a wave-shaped holder for a ball bearing capable of restricting entrainment of lubricant agent into a pocket and reducing allophone and provide a ball bearing using the wave-shaped holder for a ball bearing.SOLUTION: This wave-shaped holder for a ball bearing is constructed to guide balls for holding balls in pockets 7 arranged to pass through an annular part 6 in a radial direction. This wave-shaped holder for a ball bearing has a ball shroud plate part 8 forming each of the pockets 7 and a connecting part 9 becoming a part between the adjoining pockets 7 are alternatively arranged side by side in a circumferential direction. A side surface at the connecting part 9 facing to axial direction of the bearing is provided with a flange 18 protruded in an axial direction of the bearing.SELECTED DRAWING: Figure 11

Description

  The present invention relates to a ball bearing corrugated cage and a ball bearing using the ball bearing corrugated cage, and, for example, relates to a technique for reducing cage noise in a ball bearing for a motor or the like.

  2. Description of the Related Art Conventionally, for example, ball bearings for motors that use a cage made of synthetic resin have been proposed (for example, Patent Documents 1 and 2). As shown in FIG. 14, this synthetic resin cage is a so-called corrugated cage in which concave spherical surfaces 50 are formed along the outer circumference of the ball at both circumferential ends of the inner surface of the pocket Pt (Patent Document 2). ).

JP 2013-245762 A JP 2013-7468 A

  In the cage 52 of FIG. 14, when the cage 52 moves in the radial direction during the bearing operation, the pocket inner diameter portion 50a in the concave spherical surface 50 formed at both ends in the circumferential direction of the pocket inner surface is in line contact, The adhered grease was caught in the pocket of the cage 52 and the drag resistance was increased. As a result, abnormal noise was generated in the cage 52.

  That is, as shown in FIG. 15, a load F (that is, radial load F) of a belt that is hung on a pulley (not shown) at the tip of the rotation shaft Sh is applied to the ball bearing that supports the rotation shaft Sh of the motor. 15, the radial internal and external force Fa applied to the cage 52 from the ball 51 in the state shown in FIG. 15 is increased by the entrainment of grease in the pocket, and as shown in FIG. Unevenly revolves. In this state, when grease is further entrained in the pocket, as shown in FIG. 17, the instantaneous change in the ball revolution speed and the balance of the radial and internal forces Fa applied from the ball 51 to the cage 52 are lost, and the cage 52 swings around. 15 to 17 indicates the rotation direction of the ball bearing, that is, the cage 52. The arc La in FIGS. 15 to 17 indicates the contact position between the ball and the cage pocket during rotation. In FIGS. 16 and 17, the bias of the retainer 52 is displayed more emphasized than actual.

  Even when a radial load due to the belt load is not applied to the ball bearing, grease is entrained in the pocket, so that a momentary change in the ball revolving speed and a balance between the radial and internal forces applied from the ball 51 to the cage 52 can be achieved. It is considered that the cage 52 has collapsed and is swung around. In this state, as shown in FIG. 14, the ball is positively guided by the cage pocket inner diameter portion 50a, and the cage 52 vibrates due to the variation in the grease thickness between the ball and the cage pocket, thereby generating abnormal noise. It is thought that.

  An object of the present invention is to provide a ball bearing corrugated cage capable of suppressing the entrainment of a lubricant in a pocket and reducing abnormal noise, and a ball bearing using the corrugated cage for the ball bearing. It is.

The corrugated cage for a ball bearing according to the present invention is a ball that holds balls in pockets provided in a plurality of locations in the circumferential direction of the annular portion around the center axis of the bearing and extending radially through the annular portion. A ball bearing cage for a guide ball bearing, wherein the spherical shell plate portion forming each of the pockets and the connecting portion that is a portion between adjacent pockets are alternately arranged in the circumferential direction,
A flange protruding in the bearing axial direction is provided on at least a side surface of the connecting portion facing the bearing axial direction.

  According to this configuration, it is possible to prevent the lubricant from entering the bearing raceway surface along the bearing axial direction side surface of the cage. In particular, when the flange is attached to the outer diameter side portion in the radial direction, the lubricant on the side surface of the cage is more reliably prevented from moving from the inner diameter side to the outer diameter side due to the centrifugal force during bearing operation. Thus, it is possible to prevent the lubricant from excessively entering the outer ring raceway surface. Therefore, it is possible to prevent excessive lubricant from adhering to the ball and entering the pocket. Thereby, it becomes difficult to entrain the lubricant in the pocket of the cage.

  Accordingly, drag resistance can be reduced. As a result, it is possible to prevent the ball revolving speed from changing instantaneously and to prevent the balance of the force in the radial direction applied from the ball to the cage from being lost, thereby suppressing the cage from swinging. Therefore, it is possible to reduce the abnormal noise by suppressing the vibration of the cage.

  The annular portion may include two annular bodies facing each other in the axial direction of the annular portion, and the annular bodies may be combined to face the axial direction to form a plurality of pockets. . In this case, after inserting a plurality of balls between the raceway surfaces of the inner and outer rings, the cage can be easily assembled by combining two annular bodies from both sides in the axial direction.

  If this cage is made of resin and the two annular bodies have the same shape, the two annular bodies can be molded with one type of molding die, so that the cost of the cage can be reduced while suppressing mold costs, There is no need to separate the two annular bodies to be combined, and the management of the annular bodies is easy.

  The ball bearing according to the present invention is a ball bearing for a motor using any one of the above-described ball bearing wave cages. In this case, the motor can be rotated at a higher speed. That is, the noise from the ball bearing can be reduced even if the motor is rotated at a high speed.

The corrugated cage for a ball bearing according to the present invention is a ball that holds balls in pockets provided in a plurality of locations in the circumferential direction of the annular portion around the center axis of the bearing and extending radially through the annular portion. A ball bearing cage for a guide ball bearing, wherein the spherical shell plate portion forming each of the pockets and the connecting portion that is a portion between adjacent pockets are alternately arranged in the circumferential direction, A flange projecting in the bearing axial direction is provided on at least a side surface of the coupling portion facing the bearing axial direction. For this reason, it is possible to suppress the entrainment of the lubricant in the pocket and reduce the noise.
Since the ball bearing according to the present invention is for a motor using any of the ball bearing corrugated cages according to the present invention, it is possible to suppress the entrainment of the lubricant in the pocket and to reduce noise.

It is sectional drawing of the ball bearing using the cage for ball bearings concerning the embodiment of this invention and a reference proposal example. (A) is a perspective view of the principal part of the cage for ball bearings of a reference proposal example, (B) is the figure which expanded the principal part of FIG. 2 (A). It is sectional drawing which shows the state before couple | bonding two annular bodies of the ball bearing retainer. (A) is the top view which looked at a part of the cage for ball bearings from the outer diameter side, (B) is the figure which expanded a part of FIG. 3 (A). It is the VV sectional view taken on the line of FIG. It is the VI-VI sectional view taken on the line of FIG. It is a perspective view of the principal part of the cage for ball bearings concerning other examples of a reference proposal. It is the top view which looked at the principal part of the ball bearing retainer from the outer diameter side. It is the IX-IX sectional view taken on the line of FIG. It is the XX sectional view taken on the line of FIG. It is a perspective view of the principal part of the corrugated cage for ball bearings concerning the embodiment of this invention. It is a top view of the corrugated cage for ball bearings. It is the XIII-XIII sectional view taken on the line of FIG. It is a perspective view which shows the pocket etc. of the cage for ball bearings of a prior art example. It is a figure explaining the state at the time of the belt load addition of the ball bearing of a prior art example. It is a figure explaining the state which the retainer for ball bearings rotates in one direction. It is a figure explaining the state at the time of grease entrainment.

Embodiments of this invention and reference proposal examples will be described with reference to the drawings.
The ball bearing retainer according to this embodiment and the reference proposal example is applied to, for example, a deep groove ball bearing retainer that rotatably supports a rotating shaft of a motor.
[About ball bearings]
FIG. 1 is a cross-sectional view of a ball bearing using a ball bearing cage 1 according to this embodiment and a reference proposal example. This ball bearing is provided at both ends of an inner ring 2, an outer ring 3, a plurality of balls 4 interposed between the inner and outer rings 2, 3, a cage 1 that holds these balls 4, and inner and outer rings 2, 3. And sealing members 5 and 5 for sealing the space. Grease is sealed in the bearing space. The retainer 1 of the reference proposed example shown in FIGS. 2 to 6 is a ball guide and is an outer diameter constraining type. The ball guide in this case is a guide type that is supported by the inner ring 2 that is the rotating side wheel via the ball 4 so that the cage 1 does not contact the inner and outer rings 2 and 3. The ball 4 is made of, for example, a steel ball or ceramics.

[Schematic configuration of the entire cage]
The cage 1 holds the balls 4 interposed between the inner and outer rings 2 and 3 in pockets 7 provided at a plurality of locations in the circumferential direction of the annular portion 6 around the bearing center axis L. Each pocket 7 is provided through the annular portion 6 in the radial direction. The cage 1 is made of resin, for example, and is manufactured by injection molding. As the resin material, for example, a thermoplastic resin such as polyamide (PA), polyphenylene sulfide (PPS), or polyether ether ketone (PEEK) is applied. For example, glass fibers, carbon fibers, and aramid fibers are mixed in the resin applied to the cage 1 in order to increase the strength. The cage 1 may be, for example, a corrugated cage obtained by pressing an iron plate.

[About the connection structure of the cage 1]
FIG. 2A is a perspective view of the main part of the cage 1, and FIG. 2B is an enlarged view of the main part of FIG. The cage 1 is a so-called corrugated cage in which spherical shell-shaped plate portions 8 that form the pockets 7 and connecting portions 9 that are portions between adjacent pockets are alternately arranged in the circumferential direction. As shown in FIG. 3, the annular portion 6 of the cage 1 has two annular bodies 10, 10 facing each other in the axial direction of the annular portion 6. A plurality of pockets 7 are formed in combination facing each other. The two annular bodies 10, 10 of this embodiment have the same shape and are combined in the opposite directions.

  4A is a plan view of a part of the cage 1 as viewed from the outer diameter side, and FIG. 4B is an enlarged view of part of FIG. 4A. Each annular body 10 has a spherical shell plate half 8a that forms a hemispherical pocket 7, and a connecting half 9a that is a portion between adjacent hemispherical pockets. A spherical shell-shaped plate portion 8 is formed by combining two spherical shell-shaped plate portion halves 8a, 8a facing each other. Further, the connecting portion 9 is formed by combining the two connecting portion halves 9a, 9a facing each other. The connecting portion 9 has a mating surface 11 that comes into surface contact when the two connecting portion halves 9a and 9a are combined. The mating surface 11 is a plane perpendicular to the axial direction.

  Engagement holes 12 penetrating both side surfaces are formed in the connecting portion half body 9a. An engaging claw 13 that is inserted into and engaged with an engaging hole 12 formed in the other connecting part half 9a is formed in one connecting part half 9a. An engagement step portion 12 a is provided in the engagement hole 12. A hook portion 13 a that can be engaged with the engagement step portion 12 a of the engagement hole 12 corresponding to the engagement claw 13 is formed at the distal end portion of the engagement claw 13. The two annular bodies 10 and 10 are made to oppose each other in the axial direction, and each engaging claw 13 of one connecting portion half body 9a is inserted into each engaging hole 12 of the corresponding other connecting portion half body 9a. Further, the corrugated portion 13a of each engagement claw 13 is engaged with the engagement step portion 12a of each engagement hole 12 to form a waveform holder in which the two annular bodies 10 and 10 are coupled to each other.

  Each spherical shell plate half 8a is provided with a protruding wall portion 8aa protruding in the axial direction. In a state where the two annular bodies 10 and 10 are coupled to each other, a protrusion projecting in the axial direction on the one spherical shell plate half body side is provided at one end in the circumferential direction of one spherical shell plate half body 8a. Wall part 8aa is provided. At the other circumferential end of the other spherical shell plate half body 8a, a protruding wall portion 8aa protruding in the axial direction on the one spherical shell plate half body side is provided.

  Further, in a state where the two annular bodies 10 and 10 are coupled to each other, a protruding wall portion of the one spherical shell plate half body 8a is formed at one end in the circumferential direction of the other spherical shell plate half body 8a. A fitting recess 8ab into which 8aa is fitted is provided. A fitting recess 8ab into which the protruding wall 8aa of the other spherical shell half plate 8a is fitted is provided on the other circumferential end of the one spherical shell half plate 8a. A minute gap is formed between the tip surface of the protruding wall 8aa and the bottom surface of the fitting recess 8ab facing the tip surface. The front end surface of the protruding wall portion 8aa and the bottom surface of the fitting recess 8ab are formed at positions shifted from the axial center of the pocket 7 in the axial direction.

[About the pocket 7 of the cage 1]
FIG. 5 is a cross-sectional view taken along line VV in FIG. 6A is a cross-sectional view taken along line VI-VI in FIG. 4B, and FIG. 6B is a cross-sectional view of each annular body 10 before assembly of the cage. As shown in FIGS. 2 (B), 5 and 6, the inner surface of each pocket 7 is located on the circumferentially opposite portion on both sides facing each other in the circumferential direction, on the outer diameter side portion in the radial direction. Ball guide surfaces 14 are provided. The ball guide surface 14 is formed in a cross-sectional shape (tapered shape) that is inclined so as to approach the pocket central axis L1 as it goes toward the tip, and has a planar shape. Due to the ball guide surface 14, the cage 1 is configured as a ball guide with an outer diameter restraint type. Further, the axial guide surfaces 15 and 15 on both sides facing each other in the bearing axial direction of the pocket 7 are arc surfaces whose cross section perpendicular to the pocket central axis L1 is an arc shape. The “arc surface” may be either a cylindrical surface or a spherical surface.

  The “planar shape” includes not only a flat surface but also a curved surface shape that slightly protrudes toward the pocket side when the ball guide surface 14 comes into contact with the ball 4 (FIG. 5B). In addition, the spherical shell plate 8 is a groove-like gap between the corresponding protruding wall 8aa and the bottom of the fitting recess 8ab in a state where the two spherical shell halfs 8a and 8a are assembled. A recess δ is formed. Of the recesses δ, the groove-like recess δ1 in the ball guide surface 14 is formed at a position shifted in the axial direction from the axial center of the pocket 7. The recess δ1 extends in a direction perpendicular to the bearing axial direction, and communicates with a groove-like recess δ2 in the opposing plane 16 described later.

  The portions other than the ball guide surface 14 in the circumferentially opposite portions on both sides of each pocket 7 have a planar shape parallel to a plane including the pocket central axis L1 and the bearing axial direction. These portions having a planar shape are referred to as “opposing plane 16”. The base ends of the ball guide surfaces 14 are connected to the opposing flat surfaces 16 at the circumferentially opposing portions on both sides. The opposing flat surface 16 is formed at a position that is recessed by a predetermined small distance in the pocket diameter-expanding direction from both side edges 15a of the arc in the adjacent axial guide surfaces 15. In addition, the both ends 15a of the circular arc in the adjacent axial direction guide surface 15 are connected to the front-end | tip of the ball guide surface 14. FIG.

  Of the groove-shaped recess δ, the recess δ2 extending from the radially outer diameter side portion to the vicinity of the center in the opposing plane 16 is also formed at a position shifted in the axial direction from the axial center of the pocket 7. The recess δ2 extends in a direction perpendicular to the bearing axial direction. The axial position of the recess δ2 is connected at the same axial position as the recess δ1 on the ball guide surface 14. Of the groove-shaped recess δ, the recess δ3 in the radially inner portion on the opposed plane 16 is formed so as to be substantially in the center of the pocket 7 in the axial direction. The concave portion δ3 in the radially inner side portion and the concave portion δ2 near the center in the radial direction communicate with each other via a concave portion δ4 extending in the bearing axial direction.

[Test conditions and test results]
The ball bearing provided with the cage described above was incorporated into a testing machine, and a test was performed to determine whether abnormal noise was generated in the cage. The test conditions are as follows.
<Test conditions>
Test machine: Servo motor Belt load: 3400N
Rotation ^{speed: 1000min -1 → 7000min -1 → 3000min} -1 → 7000min -1
However, 7000Min ^-1 from 1000min ^-1, or to step up every 1000min ^-1 when increasing the rotation speed from 3000 min ^-1 to 7000Min ^-1, when decreasing the rotational speed from 7000Min ^-1 to 3000 min ^-1 1000min ^-1 Step down every time.
Judgment method: Auditory judgment

＜試験結果＞
同表１において、「○」は、聴覚判定により保持器に異音が発生していないことを表し、「×」は、聴覚判定により保持器に異音が発生したことを表す。試験結果によると、本実施形態の保持器は、各回転速度において異音が発生しなかった。

<Test results>
In Table 1, “◯” indicates that no abnormal sound is generated in the cage by auditory determination, and “X” indicates that abnormal noise is generated in the holder by auditory determination. According to the test results, the cage of the present embodiment did not generate abnormal noise at each rotation speed.

[Function and effect]
According to the cage 1 described above, the ball guide surface 14 provided on the outer circumferential side portion of the inner surface of the pocket 7 and positioned on the outer diameter side portion in the radial direction has an inclined cross-sectional shape and a planar shape. Therefore, during the bearing operation, the contact between the ball guide surface 14 and the ball 4 is a point contact. Thereby, compared with the case of a line contact, it becomes difficult to entrain the grease adhering to the ball | bowl 4 in the pocket of the holder | retainer 1. FIG. Accordingly, drag resistance can be reduced.

  In other words, even if the grease once enters the pocket while adhering to the ball 4, the grease does not stay in the pocket 7, and the grease extends in an annular shape over substantially the entire circumference other than the contact point between the ball guide surface 14 and the ball 4. From the gap, it is smoothly discharged out of the pocket while remaining attached to the ball 4. Accordingly, drag resistance can be reduced. As a result, it is possible to prevent the ball revolving speed from changing instantaneously and to prevent the balance of the forces in the radial direction applied from the ball 4 to the cage 1 from being lost, thereby preventing the cage 1 from swinging. Therefore, it is possible to reduce the abnormal noise by suppressing the vibration of the cage 1.

Further, since the axial guide surfaces 15 on both sides of the pocket 7 are arc surfaces whose cross section perpendicular to the pocket central axis L1 has an arc shape, the cage 1 is elastically deformed by using the cage 1 in a high-speed rotation range, for example. When this occurs, it is possible to prevent the contact surface pressure between the axial guide surfaces 15 on both sides of the pocket 7 and the ball 4 from fluctuating greatly, thereby preventing abnormal heat generation of the ball bearing and wear of the cage 1. Further, it is possible to prevent grease from staying on the axial guide surface 15 of the pocket 7, thereby further reducing drag resistance. In this example, the high-speed rotation range is 5000 min ⁻¹ or more, but is not limited to this rotation speed.

The annular portion 6 has a plurality of pockets 7 formed by combining two annular bodies 10 and 10 facing each other in the axial direction so as to face each other in the axial direction. For this reason, after inserting a plurality of balls 4 between the raceway surfaces of the inner and outer rings 2, 3, the cage 1 can be easily assembled by combining the two annular bodies 10, 10 from both sides in the axial direction.
Since the cage 1 is made of resin and the two annular bodies 10 and 10 have the same shape, the two annular bodies 10 and 10 can be molded with one type of molding die. For this reason, it is possible to reduce the cost of the cage 1 while suppressing the cost of the mold, and it is not necessary to separate the two annular bodies 10 and 10 to be combined, and the management of the annular body 10 is easy.
In the case of a ball bearing for a motor using this cage 1, the motor can be rotated at a higher speed. That is, the noise from the ball bearing can be reduced even if the motor is rotated at a high speed.

[Other Reference Proposal Examples and Embodiments]
In the following description, the same reference numerals are assigned to the portions corresponding to the matters described in the preceding forms in each embodiment, and overlapping descriptions are omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in advance unless otherwise specified. The same effect is obtained from the same configuration. Not only the combination of the parts specifically explained in each form, but also the forms can be partially combined if there is no problem in the combination.

  FIG. 7 is a perspective view of a main part of a ball bearing retainer 1A according to another reference proposal example, and FIG. 8 is a plan view of the main part of the ball bearing retainer 1A viewed from the outer diameter side. is there. 9 is a cross-sectional view taken along line IX-IX in FIG. 10A is a cross-sectional view taken along line XX in FIG. 8, and FIG. 10B is a cross-sectional view of each annular body 10 before the cage is assembled. As shown in FIGS. 7 to 10, the cage 1 </ b> A is a ball guide and has an inner diameter restraining type. In the cage 1A, a ball guide surface 14 provided on a radially inner side portion of the inner surface of the pocket 7 at a circumferentially opposed portion is formed in a slanting cross-sectional shape and a planar shape.

  Of the groove-shaped recess δ, the recess δ1 between the protruding wall portion 8aa and the fitting recess 8ab on the ball guide surface 14 is formed at a position shifted in the axial direction from the axial center of the pocket 7. The recess δ1 extends in a direction perpendicular to the bearing axial direction and communicates with the recess δ2 of the opposing plane 16. A concave portion δ 2 extending inward and outward in the radial direction on the opposing plane 16 is also formed at a position shifted in the axial direction from the center in the axial direction of the pocket 7.

  According to the cage 1A, since the ball guide surface 14 provided on the inner circumferential side portion of the inner surface of the pocket 7 and positioned on the radially inner side portion has an inclined cross-sectional shape and a planar shape, the bearing During driving, the contact between the ball guide surface 14 and the ball 4 is a point contact (FIG. 9B). Thereby, compared with the case of a line contact, it becomes difficult to entrain the grease adhering to the ball | bowl 4 in the pocket 7 of the holder | retainer 1A. In addition, the same operational effects as the above-described reference proposal example are exhibited.

  FIG. 11 is a perspective view of a main part of the corrugated cage 1B for ball bearings according to the embodiment. 11 (a) and 11 (b) are perspective views of the ball bearing corrugated cage 1B as seen from different directions. 12 is a plan view of the cage 1B, and FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. As shown in FIGS. 11 to 13, the cage 1 </ b> B is provided with convex portions 17 on the axial guide surfaces 15 and 15 on both sides of each pocket 7. The radially outer diameter side portion 15b of the axial guide surface 15 is formed in a conical surface. That is, the radially outer diameter side portion 15b of the axial guide surface 15 is provided with an axial ball guide surface formed in a cross-sectional shape that is inclined so as to approach the pocket central axis toward the tip. In the axial direction guide surface 15, other than the axial direction ball guide surface, an arc surface 15c having a circular arc cross section perpendicular to the pocket central axis L1 is used. Convex portions 17 are provided on the respective arc surfaces 15c.

  These convex portions 17 are provided on the axial guide surfaces 15 on both sides in the vicinity of an axis L2 around which the ball rotates within the pocket, like a boss portion protruding in a hemispherical shape toward the pocket side. The diameter and protrusion amount of the convex portion 17 are determined to be several percent of the ball diameter based on, for example, results of tests and simulations. However, it is not limited to this example. The convex portion 17 suppresses an increase in the contact range between the annular portion 6 and the ball when the annular portion 6 is deformed by the centrifugal force during the bearing operation and the shape of the pocket 7 is deformed. In this example, one projection 17 is provided on each axial guide surface 15, but a plurality of projections 17 may be provided.

  As shown in FIGS. 11 and 12, the retainer 1B is provided with a flange 18 that prevents grease from entering the inner and outer ring raceway surfaces directly along the bearing axial direction side surface of the retainer 1B. In this example, a flange 18 projecting in the bearing axial direction is provided on the radially outer diameter side portion of the side surface facing the bearing axial direction in the connecting portion 9 and the side surface facing the bearing axial direction in the spherical shell plate portion 8. It has been. The flanges 18 are provided on both sides in the bearing axial direction.

  The width dimension of the cage 1B including both side flanges 18 and 18 in the connecting portion 9 and the width dimension of the cage 1B including both side flanges 18 and 18 in the spherical shell plate 8 are the same. The one axial flange 18 in the connecting portion 9 and the one axial flange 18 in the spherical shell-shaped plate portion 8 are formed to have the same axial tip position. The same applies to the other flange 18 in the axial direction.

The spherical shell plate portion 8 is provided with an inner flange 19 that suppresses grease from entering the pocket 7. Specifically, an inner flange 19 that protrudes a predetermined small distance to the inside of the pocket is provided on the radially inner diameter side edge portions on both sides facing each other in the circumferential direction among the inner surfaces of the pocket 7 in the spherical shell-shaped plate portion 8. ing. The inner flange 19 is formed in an arc shape in plan view (FIG. 12). The reason why the inner flanges 19 are hardly provided on the axial guide surfaces 15 on both sides is as follows. Even if the grease enters the axial guide surface 15 of the pocket 7 due to centrifugal force, the axial guide surface 15 has the convex portion 17, so that the grease does not stay in the pocket and the axial guide surface 15. This is because it is smoothly discharged out of the pocket through a gap other than the point contact of the ball.
Other configurations are the same as those of the cage shown in FIGS.

  According to the cage 1B, when the annular portion 6 is deformed by the centrifugal force during the bearing operation and the shape of the pocket 7 is deformed, the ball is brought into contact with the convex portion 17 of the axial guide surface 15. Particularly in this example, since the so-called conical ball guide surface is provided on the radially outer diameter side portion 15b of the axial guide surface 15, the shape of the pocket 7 is elastically deformed or the like without the convex portion 17. Then, it is conceivable that the ball makes excessive line contact with the conical ball guide surface.

  However, since the convex portion 17 is provided on the axial guide surface 15 as described above, the ball is brought into point contact with the convex portion 17 of the axial guide surface 15 without making a line contact with the conical ball guide surface. obtain. Therefore, it is possible to reliably prevent the ball bearing from generating abnormal heat and wear the retainer 1B by suppressing the contact surface pressure of the ball against the axial guide surface 15. Further, since the contact between the convex portion 17 of the axial guide surface 15 and the ball is a point contact, the grease attached to the ball is less likely to be caught in the pocket of the cage 1B as compared with the case of the line contact. Accordingly, drag resistance can be reduced. In addition, since the convex portions 17 are provided in the axial guide surfaces 15 and 15 on both sides in the vicinity of the axis L2 around which the ball rotates, the ball can be rotated and revolved stably. As a result, the swinging of the cage 1B can be more reliably suppressed.

  Since the flange 18 projecting in the bearing axial direction is provided on the side surface of the connecting portion or the like, the grease can be prevented from entering the inner and outer ring raceway surfaces directly along the bearing axial direction side surface of the cage 1B. In particular, since the flange 18 is attached to the outer diameter side portion in the radial direction, the grease on the side surface of the cage is more reliably suppressed from moving from the inner diameter side in the radial direction to the outer diameter side due to centrifugal force during bearing operation. Can be prevented from excessively penetrating the outer ring raceway surface. Therefore, it is possible to prevent excessive grease from adhering to the ball and entering the pocket. This makes it difficult for the grease to be caught in the pocket of the cage 1B. Therefore, drag resistance can be reduced.

  Further, the grease tends to enter the pocket by centrifugal force during the operation of the bearing. However, since the inner flange 19 is provided, the grease can be prevented from excessively entering the pocket. Thereby, it becomes difficult to further entrain the grease in the pocket. Therefore, drag resistance can be reliably reduced.

In each reference proposal example and embodiment, the following modifications can be applied.
The cage is not limited to resin but may be made of metal. For example, it may be formed by machining brass or the like. In this case, the cage may not be a mating cage composed of two annular bodies.
The place where the flange is provided is not limited to the outer diameter side portion in the radial direction. For example, a flange projecting in the bearing axial direction may be provided on a radially inner side portion or a portion near the center in the radial direction among the side surfaces of the connecting portion or the like.

Lubricating oil may be applied as a lubricant instead of grease. In this case, for example, a lubricating oil having a viscosity of VG32 or higher can be considered.
An angular ball bearing may be applied as a ball bearing using each cage.
Although the ball bearing of the embodiment is a double-sided seal type, a seal may be provided only on one side, or a so-called open type without both seals.
These ball bearings can also be applied to uses other than motors. Also in this case, noise from the ball bearing can be reduced.

  As mentioned above, although the form for implementing this invention based on embodiment was demonstrated, embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

DESCRIPTION OF SYMBOLS 1B ... Cage 4 ... Ball 6 ... Ring part 7 ... Pocket 8 ... Spherical shell plate part 9 ... Connection part 10 ... Ring body 15 ... Axial direction guide surface

Claims (3)

A ball guide ball bearing retainer for holding a ball in a plurality of locations in the circumferential direction of the annular portion around the bearing central axis and holding the ball in a pocket provided through the annular portion in the radial direction, In the corrugated cage for ball bearings in which the spherical shell-shaped plate portion forming each pocket and the connecting portion that is a portion between adjacent pockets are alternately arranged in the circumferential direction,
A ball bearing corrugated cage characterized in that a flange projecting in the bearing axial direction is provided on at least a side surface of the connecting portion facing the bearing axial direction.   2. The ball bearing corrugated cage according to claim 1, wherein the annular portion has two annular bodies facing each other in the axial direction of the annular portion, and the annular bodies are opposed to the axial direction. A corrugated cage for a ball bearing in which a plurality of the pockets are formed in combination.   A ball bearing for a motor using the corrugated cage for a ball bearing according to claim 1.

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