JP2010048326A - Angular contact ball bearing, double-row angular contact ball bearing, and roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an angular contact ball bearing, a double-row angular contact ball bearing, and a roller bearing, capable of reducing torque, preventing leakage of grease, enhancing sealing performance against mud, and saving the space simultaneously and at low cost. <P>SOLUTION: The angular contact ball bearing has a recess in each crown-shaped retainer 5 to reduce the scraping amount of grease adhered to a ball 4 at an inside diameter surface 5d of the retainer 5. Thereby, the grease is prevented from adhering to an outside diameter section 2D of an inner ring 2. Further, a sealing member 6 has an inner peripheral surface Lmb facing a seal groove 7 in a main lip Lm, and an inclined surface Lba formed at the inner periphery of a labyrinth lip. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an angular ball bearing, a double-row angular ball bearing, and a rolling bearing, and relates to, for example, a technique for solving grease leakage of a ball bearing used for a rotation support portion and achieving muddy water resistance.

Of the bearings used for the rotation support portion, as a countermeasure against grease leakage resistance of a bearing that uses balls as rolling elements, it is common to take a countermeasure with a seal shape. However, when the seal type is non-contact, the torque becomes low, but the grease leakage resistance and the mud water resistance become problems. If the seal type is contact, the muddy water resistance is increased, but the torque is increased. In addition, a so-called respiration phenomenon causes grease leakage and adsorption, resulting in high torque. In particular, there is a muddy water measure in which a labyrinth clearance is formed by changing a seal lip shape (Patent Document 1).
JP 2001-140907 A

The labyrinth clearance formed by changing the shape of the seal lip prevents grease leakage and muddy water intrusion, and does not discharge muddy water in the seal groove of the bearing ring. Therefore, there is a problem that the seal lip is worn by the muddy water that has entered the seal groove of the race.
A technique has also been proposed in which a pair of slinger is fitted and fixed to a fixed shaft to which a sealed type rolling bearing is fitted so as to sandwich the rolling bearing in the axial direction, but in order to provide a slinger in the axial direction of the bearing. Space is required, the number of parts increases, and the manufacturing cost increases.

  An object of the present invention is to provide an angular ball bearing, a double-row angular ball bearing, and a rolling bearing that can simultaneously achieve low torque, grease leakage resistance, mud water resistance, and space saving at low cost.

  The angular ball bearing according to the first aspect of the present invention is an angular ball bearing in which a plurality of balls interposed between inner and outer rings are held by a cage, and a sealing member for closing a bearing space between the inner and outer rings is provided on the outer ring. , A shoulder is formed between a seal groove formed on the side of the race of the inner ring and an end of the inner ring, and the seal member is mounted on the inner peripheral surface of the outer ring facing the seal groove The inner circumferential portion of the seal member is provided with a main lip that contacts the track-side groove wall of the seal groove, and a labyrinth slip protruding above the shoulder, and the inner circumferential end of the seal member has the Provided with a main lip and a labyrin slip, an inner peripheral surface facing the seal groove on the main lip, and an inclined surface that gradually increases in diameter toward the tip of the labyrin slip on the inner periphery of the labyrin slip The retainer is formed in a crown shape having a plurality of pockets that are partially opened on one side surface of the annular body and hold balls therein, and are attached to the balls. The retainer is provided with grease scraping suppressing means for suppressing the grease to be scraped off from the inner diameter surface of the retainer.

  According to this configuration, since the above-described grease scraping suppressing means is provided in the crown-shaped cage, it is possible to suppress grease leakage from the back surface side of the cage. Thereby, it is possible to prevent the grease from adhering to the outer diameter portion of the inner ring. Furthermore, a main seal lip and a labyrinth slip are provided on the inner peripheral portion of the seal member, an inner peripheral surface facing the seal groove is provided on the main lip, and an inclined surface is formed on the inner periphery of the labyrin slip, thereby providing a contact seal. The tip of the main lip can be brought into contact with the track-side groove wall of the seal groove at a contact position lower than the upper end position of the shoulder-side groove wall facing the track-side groove wall of the seal groove. Therefore, the scattered muddy water does not directly hit the tip of the seal lip. Therefore, even if this bearing is used in an environment where muddy water or the like is scattered, the tip of the seal lip can be stably brought into contact with the raceway-side groove wall of the seal groove, and the sealing performance of the contact seal can be sufficiently ensured. Therefore, leakage of grease in the bearing is prevented and mud water resistance is obtained. Therefore, it is not necessary to increase the urging force of the lip or the like, so that the torque can be reduced.

  In this invention, the double row angular contact ball bearing of the second invention comprises an outer ring having a double row raceway surface on the inner periphery, an inner ring having a double row raceway surface facing the raceway surface on the outer periphery, and these inner rings, A double row ball interposed between the raceways of the outer ring, two cages for holding the balls in each row, and seal members on both sides that are provided on the outer ring and block the bearing space between the inner ring and the outer ring. In the double-row angular ball bearing, a shoulder is formed between a seal groove formed on a side of the race of the inner ring and an end of the inner ring, and the inner peripheral surface of the outer ring facing the seal groove The seal member is mounted on the inner peripheral portion of the seal member, and a main lip that contacts the track-side groove wall of the seal groove and a labyrinth slip protruding above the shoulder portion are provided on the inner peripheral portion of the seal member. On the side tip, the main lip and labyrinth slip Providing an inner peripheral surface facing the seal groove on the main lip, and forming an inclined surface gradually increasing in diameter toward the tip of the labyrin slip on the inner periphery of the labyrin slip, The crown has a shape in which a part of the annular body is open on one side surface and holds a ball inside the annular body at a plurality of circumferential positions of the annular body, and the pocket surfaces of the two cages face each other. Each of the cages is provided with grease scraping suppression means that is arranged as described above and suppresses the grease adhering to the balls from being scraped off at the inner diameter surface of the cage.

According to this configuration, each crown-shaped cage is provided with grease scraping suppression means for suppressing the grease adhering to the ball from being scraped by the inner diameter surface of the cage, so that the pocket surfaces of the two cages face each other. Since it is arranged, grease leakage from the back side of the cage is suppressed. As a result, it is possible to prevent grease from adhering to the outer diameter part of the inner ring and to prevent adhesion of grease to the seal groove of the race ring. It is not necessary to change the design of the shape of the seal groove, and it is not necessary to secure a space for providing a slinger or the like in the axial direction. Therefore, the number of parts can be made smaller than that described in the above-mentioned patent document, and the manufacturing cost can be reduced.
Furthermore, a main lip and a labyrinth slip are provided on the inner peripheral portion of the sealing member, an inner peripheral surface facing the seal groove is provided on the main lip, and an inclined surface is formed on the inner periphery of the labyrin slip. Can be brought into contact with the track-side groove wall of the seal groove at a contact position lower than the upper end position of the shoulder-side groove wall facing the track-side groove wall of the seal groove. Other effects similar to those of the first aspect are achieved.

  In the double-row angular contact ball bearing, the above-described cage shape can suppress grease from adhering to the outer diameter portion of the inner ring, and can suppress grease leakage from the back surface side of the cage, that is, from the non-pocket side. Furthermore, by using the sealing member, grease leakage in the bearing can be prevented and muddy water resistance can be obtained.

  The grease scraping suppressing means may be provided with a recessed portion extending from the pocket opening edge on the inner diameter side of the cage toward the outer diameter side of the cage on the inner surface of each pocket. In this case, the amount by which the grease adhering to the ball is scraped off by the inner diameter surface of the cage is reduced by the recess. By the recess, grease that can be deposited near the pocket opening edge of the cage can smoothly enter the inner surface of the pocket and contribute to lubrication.

The inclination angle of the inclined surface of the labyrinth slip may be set to 10 degrees or more and 40 degrees or less with respect to the outer peripheral surface of the shoulder portion. When this inclination angle is set, the muddy water accumulated in the seal groove is moved outward in the axial direction along the inclined surface of the labyrin slip by the centrifugal force caused by the rotation of the seal member, and is easily discharged to the outside of the bearing.
If the inclination angle of the inclined surface of the labyrin slip is less than 10 degrees, the centrifugal force acting on the muddy water is reduced by the rotation of the seal member, so that the muddy water is not sufficiently discharged. This is because when the inclination angle exceeds 40 degrees, the gap between the shoulder portion and the shoulder side groove wall of the seal groove and the inclined surface of the labyrinth slip becomes wide, and the sealing performance of the labyrinth seal deteriorates.

The inclined surface of the labyrinth slip is provided with a stepped portion projecting toward the shoulder side groove wall of the seal groove at the axially inner end thereof, and continuously provided on the inner peripheral surface of the main lip through this stepped portion. May be. Since the stepped portion protrudes toward the shoulder side groove wall of the seal groove, a narrowed portion is formed in the labyrinth seal formed by the labyrin slip, and the sealing performance by the labyrinth seal is ensured.
When the sealing member is an elastic body reinforced with a cored bar, the rigidity of the sealing member is increased, and the tip of the sealing lip stably contacts the inner wall of the sealing groove without undesirably elastically deforming. Can be.

The elastic body of the sealing member may be hydrogenated nitrile rubber or ester acrylic rubber. This hydrogenated nitrile rubber is superior to nitrile rubber generally used as a seal member and has no problem in chemical resistance. Maintains stable properties and can be used at higher temperatures.
Ester-resistant acrylic rubber, like hydrogenated nitrile rubber, is superior in heat resistance as compared to nitrile rubber, and has improved chemical resistance against chemicals such as ester rubber of acrylic rubber and compressor oil of air conditioner. For this reason, when ester-acrylic-resistant rubber | gum is employ | adopted as an elastic body of a sealing member, the stable property is maintained and it can use at higher temperature.

You may provide the recessed part extended from the inner diameter edge of a retainer in the back surface of each pocket of the said retainer to a retainer outer diameter side. Thereby, the area of the inner diameter surface in the pocket can be reduced, and the effect of preventing grease leakage can be improved.
The rolling bearing according to the third aspect of the present invention is the one in which the seal member and the cage according to the first aspect are applied to the rolling bearing.
Since the crown-shaped cage is provided with the grease scraping suppressing means, it is possible to suppress grease leakage from the rear side of the cage and prevent the grease from adhering to the outer diameter portion of the inner ring. Further, by using the above seal member, the same effects as those of the first invention other than the first invention for preventing grease leakage in the bearing and obtaining muddy water resistance can be obtained.

In the third invention, the grease scraping suppressing means is provided with a recessed portion extending from the pocket opening edge on the inner diameter side of the cage toward the outer diameter side of the cage, on the inner surface of each pocket.
A pair of claws facing in the circumferential direction are provided on the open side of each pocket so as to protrude in the axial direction, and the outer diameter of the cage is larger than the distance between the tips on the inner diameter side of the pair of claws of each pocket. You may narrow the space | interval between the front-end | tips on the side.
The amount of grease that adheres to the balls is scraped off by the inner surface of the cage due to the recess. Further, the pair of claws provided on the open side of each pocket protrudes the grease adhering to the ball, for example, from the outer ring side to the outer diameter part of the inner ring. Scrape off the outer diameter side of the cage away from the nail. Thereby, grease leakage from the bearing can be prevented more reliably.

A pair of claws facing in the circumferential direction are provided on the open side of each pocket in the retainer so as to protrude in the axial direction, and the gap between the tips on the inner diameter side of the pair of claws of each pocket is opened. What connected between the front-end | tips of an outer diameter side may be used.
The grease adhering to the ball is not brought close to the outer diameter part of the inner ring from the outer ring side, for example, and the grease from the inner ring side can be scraped off on the outer diameter side of the retainer of the claw away from the outer diameter part of the inner ring.
The interval between the tips of the pair of claws of each pocket may be reduced stepwise from the inner diameter side of the cage toward the outer diameter side of the cage. In this case, the nail can be easily formed by various manufacturing methods, and the manufacturing cost of the cage can be reduced.
You may make the space | interval between the front-end | tips of a pair of nail | claw of each said pocket infinitely narrow toward a cage outer diameter side from a cage inner diameter side. In this case, the rigidity of the nail itself can be increased as compared with the case where the interval between the tips of the pair of claws is narrowed stepwise.

When the total width of the claw projected onto the straight line in the radial direction of the cage passing through the center in the circumferential direction of the cage in the pocket is defined as It, the width Ie of the claw portion on the holding outer diameter side of the claw projected onto the straight line is 2 You may set the width | variety of the said nail | claw part by the side of a cage outer diameter so that it may become / 3It or less. In this case, the grease leakage preventing effect can be further increased.
The angle of the claw tip on the cage inner diameter side and the claw tip on the cage outer diameter side with respect to the cage circumferential direction from the position corresponding to the pocket center in the cross section along the cage circumferential direction of the claw is determined on the cage outer diameter side. Setting the angle of the claw tip to be 1.5 times or more of the angle of the claw tip on the inner diameter side of the cage is preferable for further improving the grease leakage preventing effect.

A double row angular contact ball bearing according to a first aspect of the present invention is an angular contact ball in which a plurality of balls interposed between inner and outer rings are held by a cage, and a seal member for closing a bearing space between the inner and outer rings is provided on the outer ring. In the bearing
A shoulder is formed between a seal groove formed on a side of the race of the inner ring and an end of the inner ring, and the seal member is attached to an inner peripheral surface of the outer ring facing the seal groove, A main lip that contacts the track-side groove wall of the seal groove and a labyrinth slip that protrudes above the shoulder are provided on the inner peripheral portion of the seal member, and the main lip is provided on the inner peripheral end of the seal member. And an inner circumferential surface facing the seal groove on the main lip, and an inclined surface that gradually increases in diameter toward the tip of the labyrin slip is formed on the inner circumference of the labyrin slip. The retainer has a crown shape in which a part of one side portion of the annular body is opened to hold a ball therein, and has a plurality of pockets in the circumferential direction of the annular body, and the grease is attached to the ball. Scraped with the inner surface of the cage Grease scraping suppressing means suppresses the order provided in the cage can be achieved at low torque, resistance to grease leakage, at the same time a low cost muddy water resistance, and saving space.

A double-row angular contact ball bearing according to a second aspect of the present invention includes an outer ring having a double-row raceway surface on the inner periphery, an inner ring having a double-row raceway surface facing the raceway surface, and the inner and outer rings. A plurality of balls interposed between the raceway surfaces, two cages for holding the balls in each row, and seal members on both sides that are provided on the outer ring and block the bearing space between the inner ring and the outer ring. In the double-row angular contact ball bearing, in the first invention, the seal member, two crown-shaped cages are provided,
Since each of the cages is provided with grease scraping suppression means that is arranged so that the pocket surfaces of the two cages face each other and the grease adhering to the balls is scraped off by the cage inner diameter surface, low torque Grease leakage resistance, muddy water resistance, and space saving can be achieved simultaneously and at low cost.

A rolling bearing according to a third aspect of the present invention is the rolling bearing in which a plurality of balls interposed between the inner and outer rings are held by a cage, and the outer ring is provided with a seal member that closes a bearing space between the inner ring and the outer ring. Since the seal member and the crown-shaped cage in the first invention are provided, low torque, grease leakage resistance, mud water resistance, and space saving can be achieved simultaneously and at low cost.

  An embodiment of the present invention will be described with reference to FIGS. The ball bearing 1 according to this embodiment is a single-row angular ball bearing. As shown in FIG. 1, this single row angular contact ball bearing has a plurality of balls 4 interposed between raceway surfaces 2a and 3a of an inner ring 2 and an outer ring 3, and a cage 5 (or a later-described) that holds these balls 4. A cage 5C) is provided, and one end on the pocket opening side of the annular space formed between the inner and outer rings 2 and 3 is sealed with a seal member 6 shown in FIGS. The raceway surfaces 2a and 3a are formed so as to have a predetermined contact angle shown by a one-dot chain line in FIG. The counter bore portion forming the outer diameter surface of the inner ring on the left side in FIG. 1 without the seal groove 7 is formed to have a smaller diameter than the outer diameter portion 2D on the right side in the figure. Thereby, the inner ring 2 can be easily incorporated into the outer ring 3 and the ball 4 from the outer diameter surface of the left inner ring. Furthermore, the distance between the inner diameter surface 5d of the cages 5 and 5C on the back side of the pocket and the inner ring outer diameter surface can be increased. Grease is sealed in the bearing space.

In this angular ball bearing, by using the following seal member 6 and a cage 5 described later, low torque, grease leakage resistance, mud water resistance, and space saving are simultaneously achieved at low cost.
As shown in FIGS. 1 and 2, a circumferential seal groove 7 is formed on the right side of the raceway surface 2 a in the inner ring 2, and a locking groove 8 is formed on the inner peripheral surface of the outer ring 3 facing the seal groove 7. . The outer peripheral edge 9 of the seal member 6 is press-fitted and fixed in the locking groove 8.
The seal groove 7 of the inner ring 2 is formed by a groove wall 7a on the raceway surface side of the inner ring 2, a bottom surface 7b, and a groove wall 7c on the shoulder 2b side. The groove wall 7c is inclined outward in the axial direction, and is formed continuously with the outer peripheral surface of the shoulder 2b.
The groove wall 7a is referred to as "track side groove wall 7a", and the groove wall 7c is referred to as "shoulder side groove wall 7c".

The seal member 6 will be described.
As shown in FIGS. 3 and 4, the seal member 6 is formed of a contact seal, has a cored bar 6a and an elastic member 6b, and an axially inward seal lip 6c is provided on the inner peripheral side of the elastic member 6b. Yes. The seal member 6 is obtained by reinforcing an elastic member 6b made of synthetic rubber or the like with a cored bar 6a. As a synthetic rubber used for the elastic member 6b, hydrogenated nitrile rubber or ester acrylic rubber can be employed.
The hydrogenated nitrile rubber is superior to nitrile rubber generally used as a sealing member and has no problem in chemical resistance, so it maintains stable properties and is used at higher temperatures. Can do. Like the hydrogenated nitrile rubber, the ester-resistant acrylic rubber has excellent heat resistance compared to nitrile rubber, and has improved chemical resistance against chemicals such as ester oil of acrylic rubber and compressor oil of air conditioners. And can be used at higher temperatures.

  The seal member 6 is formed with a constricted portion 6ba having a small thickness at a portion of the elastic member 6b on the inner peripheral portion thereof. The constricted portion 6ba is formed thinly from the main lip Lm or the labyrinth slip Lb, which will be described later, or from both sides including the boundary thereof toward the outer diameter side. A seal lip 6c is provided at the inner peripheral end of the constricted portion 6ba. The seal lip 6c has a main lip Lm brought into contact with the track-side groove wall 7a of the seal groove 7 and a labyrinth slip Lb protruding above the shoulder 2b.

The main lip Lm faces the track-side groove wall 7a of the seal groove 7 and has an inclined wall surface Lma that expands outward, and an inner circumference that is located radially inward of the inclined wall surface Lma and faces the bottom surface 7b of the seal groove 7 It has surface Lmb, and tip part Lmc which makes inclined wall surface Lma and inner peripheral surface Lmb continue.
As shown in FIGS. 2 to 4, when the outer peripheral edge portion 9 of the seal member 6 is press-fitted and fixed in the locking groove 8 of the outer ring 3, the tip end portion Lmc of the main lip Lm is the track-side groove wall 7 a of the seal groove 7. Slid in contact. The main lip Lm is provided at the distal end portion of the constricted portion 6ba formed to be thin, and the constricted portion 6ba is elastically deformed in the axial direction of the arrow A1 in FIG. The followability to is maintained. As a result, grease inside the bearing can be prevented from leaking into the seal groove 7, and foreign matter and muddy water from the outside can be prevented from entering the bearing.

The labyrinth slip Lb faces the range from the shoulder 2b to the shoulder-side groove wall 7c of the seal groove 7, and a labyrinth seal Ls is formed. As shown in FIG. 4, an inclined surface Lba that has a diameter reduced inward is provided on the inner peripheral portion of the labyrinth slip Lb. The inclined surface Lba is set so that the inclination angle α3 with respect to the outer peripheral surface of the shoulder 2b of the inner ring 2 is 10 degrees or more and 40 or less. When the inclination angle α3 is set in this way, the muddy water adhering to the inclined surface Lba moves axially outward along the inclined surface Lba by the centrifugal force due to the rotation of the seal member 6, and is discharged to the outside of the bearing. .
When the inclination angle α3 is less than 10 degrees, the centrifugal force due to the rotation of the seal member 6 does not sufficiently act on the muddy water adhering to the labyrin slip Lb, so that the muddy water is difficult to be discharged. When the inclination angle α3 exceeds 40 degrees, the gap between the outer peripheral surface of the shoulder 2b and the inclined surface Lba of the labyrinth slip Lb becomes wide, and the sealing performance by the labyrinth seal Ls decreases. For this reason, the inclination angle α3 is set to 10 degrees or more and 40 or less.

The tip of the labyrinth slip Lb is provided near the shoulder side wall 7c of the seal groove 7. Therefore, the distance that the muddy water adhering to the labyrin slip Lb moves on the inclined surface Lba by the centrifugal force caused by the rotation of the seal member 6 is shortened, and the muddy water accumulated in the seal groove 7 is easily discharged.
A step portion Ds is provided between the inner peripheral surface Lmb of the main lip Lm and the inclined surface Lba of the labyrinth slip Lb. The step portion Ds is provided so as to protrude toward the shoulder side groove wall 7 c of the seal groove 7. Thereby, since the inner peripheral surface Lmb of the main lip Lm is continuously formed through the step portion Ds and the inclined surface Lba of the labyrin slip Lb, the muddy water accumulated in the seal groove 7 is caused by the rotation of the seal member 6. It is easy to be discharged to the outside of the bearing along the inclined surface Lba of the labyrinth slip Lb by centrifugal force.

  Further, when the step portion Ds is provided so as to protrude, a narrowed portion is formed between the outer peripheral edge portion of the inner peripheral surface Lmb of the main lip Lm and the shoulder side groove wall 7c of the seal groove 7. With this narrowed portion, the sealing performance by the labyrinth seal Ls can be secured. Since a narrowed portion is also formed between the peak portion Yd at the boundary between the seal groove 7 and the shoulder portion 2b and the inclined surface Lba of the labyrin slip Lb, the sealing performance by the labyrinth seal Ls can be further secured.

As shown in FIG. 2, the inner diameter D _L of the tip of the seal lip 6c before incorporation into the bearing of the sealing member 6 is smaller than the diameter D ₁ of the inner ring 2 of the shoulder portion 2b, the inner diameter D _L and the diameter D ₁ difference _D L -D ₁ with the sealing member 6 as incorporated easily into the bearing, is defined to a value equal to or greater than -0.2 mm.
When the seal member 6 is fixed to the locking groove 8 of the outer ring 3 and incorporated in the bearing, the tip of the seal lip 6c is placed on the track-side groove wall 7a of the seal groove 7 as shown in FIG. Contact is made at a contact height position that is lower in the radial direction by δ than the upper end position of the part-side groove wall 7c. Therefore, even if this bearing is used in an environment where water, mud, etc. scatter, water, mud, etc. do not directly hit the tip Lmc of the seal lip 6c, and the tip Lmc is stable with the track-side groove wall 7a. Contact.

An angular contact ball bearing provided with a seal member 6 is attached to a rotating test machine in an environment in which foreign matter such as water and mud scatters intermittently, and the contact height position δ of the seal groove 7 of the tip Lmc to the track side groove wall 7a A foreign matter intrusion test was conducted to investigate the amount of foreign matter intruded into the bearing space when the angle was changed. The contact height position δ is −0.1 mm, −0.05 mm (Example), which is lower than the upper end position of the shoulder side groove wall 7c in the radial direction, and is equal to or higher than the upper end position of the shoulder side groove wall 7c. The height was changed to 0.0 mm, 0.05 mm, and 0.1 mm (comparative example). The amount of foreign matter intrusion was determined by measuring the mass increase W of the bearing before and after the test. The test conditions are as follows.
・ Bearing speed: 2000rpm
・ Test time: 3 hours

  FIG. 5 shows the result of the foreign substance penetration test. White circles represent examples, and black circles represent comparative examples. From the test results, in the comparative examples in which the contact height position δ of the tip end portion Lmc is the same as or higher than the upper end position of the shoulder side groove wall 7c, the mass increase amount W of the bearing is remarkable. On the other hand, in each example in which the contact height position δ is lower than the upper end position of the shoulder side groove wall 7c, the bearing mass increase amount W is not recognized remarkably, and foreign matter hardly penetrates. Therefore, by making the contact height position δ of the front end portion Lmc of the seal lip 6c lower than the upper end position of the shoulder side groove wall 7c of the inner ring 2, the front end portion Lmc is stably brought into contact with the track side groove wall 7a, It was confirmed that a sufficient sealing property can be secured by preventing the intrusion of foreign matter.

The cage 5 will be described.
As shown in FIGS. 1 and 6, the cage 5 has a crown shape having pockets 11 for holding the balls 4 therein at a plurality of locations in the circumferential direction of the annular body 12. The inner surface of each pocket 11 has a concave spherical curved surface shape along the outer surface of the ball 4. The pocket opening side of the cage 5 is directed inward in the axial direction, and the back side of the pocket is opened to the left end side. As shown in FIG. 6, the portion between the adjacent pockets 11, 11 of the annular body 12 becomes a connecting portion 13. On the open side of each pocket 11, a pair of claw-shaped tips (claws) 14, 14 facing in the circumferential direction protrude in the axial direction indicated by arrow A <b> 1 in FIG. 49.

FIG. 49 is a diagram of a conventional example in which the pocket inner surface is a monotonous spherical surface in a portion corresponding to FIG.
On the other hand, on the inner surface of the pocket 11 of the cage 5 of the present invention, as shown in FIG. 6A, a plurality of recesses 16 extending from the pocket opening edge on the cage inner diameter side to the cage outer diameter side. Is provided. By providing the recessed portion 16 as a grease scraping suppressing means, the amount of grease adhering to the ball 4 is scraped off by the inner diameter surface 5d of the cage 5, and the outer diameter portion 2D (FIG. 1) of the inner ring 2 is reduced. ) Prevents grease from adhering to

  In this example, the recessed portions 16 are two locations located on both sides of the center OW11 in the cage circumferential direction at the opening edge of the pocket 11. The inner surface shape of each recessed portion 16 is an arc shape having a radius of curvature Rb smaller than the radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 11 in the cross-sectional shape along the circumferential direction of the cage. The said cross-sectional shape is synonymous with the cross-sectional shape which cut the dent part 16 in the plane perpendicular | vertical to a holder | retainer central axis. Specifically, as shown in FIG. 6B, the inner surface shape of each recess 16 is a cylindrical surface shape that substantially follows the surface of each virtual cylinder V centered on the straight line L in the radial direction of the cage 5. is there. The recessed portion 16 extends from the pocket opening edge on the cage inner diameter side to the vicinity of the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases from the cage inner diameter edge toward the ball arrangement pitch circle PCD. That is, the shape gradually becomes shallower and narrower. The ball arrangement pitch circle PCD is also referred to as a pocket PCD.

  The positions of the two recessed portions 16 are, for example, two symmetrical places where the orientation angle in the circumferential direction with respect to the center OW11 in the circumferential direction of the cage at the opening edge of the pocket 11 is 40 ° ± 15 °. The depth of the recessed portion 16 is preferably such that the distance Rc from the center O11 of the recessed spherical surface of the pocket inner surface to the deepest position of the recessed portion 16 is 1.05 times or more the radius of the ball 4 (just 1.05). May be double). It is good also considering the recessed part 16 as three or more places.

As a modified form in which the ball bearing cage 5 according to this embodiment is partially changed, as shown in FIG. 7, the pocket back side of the inner diameter surface of the connecting portion 13 may be deleted. The pocket 11 has a shape in which the back side of the pocket is surrounded by an arcuate shell portion 11a.
In the embodiment shown in FIGS. 6 to 8, the recess 16 can reduce the amount of grease scraped off the ball 4 by the inner surface 5 d of the cage 5. Increasing the amount leads to grease leakage. In this case, grease also adheres to the inner diameter surface of the connecting portion 13, and this portion of grease can move only in the axial direction. When the range of the connecting portion 13 in the axial direction overlaps with the region where the outer diameter portion 2D exists, that is, when the inner diameter surface of the connecting portion 13 is located on the bearing end surface side of the raceway surface 2a, the inner diameter surface of the connecting portion 13 Grease leaks out of the bearing. Therefore, as shown in FIG. 7, by removing the pocket back side of the inner diameter surface of the connecting portion 13, the grease is prevented from leaking out of the bearing from the inner diameter surface of the connecting portion 13.

  In the modification of FIG. 7, an example is shown in which the deletion is performed from the inner diameter surface to the outer diameter surface on the pocket back surface side of the connecting portion 13, but when considering the strength of the cage 5, the deletion amount may be small. desirable. In order to suppress the adhesion of grease to the outer diameter portion 2D of the inner ring 2, it is effective to increase the distance between the outer diameter surface of the inner ring 2 and the inner diameter surface 5d of the cage 5. Only a part of them may be deleted, and a conventional wall surface may be left on the outer diameter side. In the cross-section at the circumferential center position of the connecting portion 13 between the adjacent pockets 11, 11, the axial position of the end point on the back side of the pocket of the inner diameter surface that is left without being deleted of the connecting portion 13 is the position of the raceway surface 2 a. Positioning on the center side of the raceway surface 2a rather than the shoulder is important for preventing grease leakage.

  This is shown in FIG. 8 as a schematic diagram of the positional relationship in the axial direction Y by superposing the sectional view of the inner ring 2 indicated by a virtual line on the cage 5 of FIG. In the drawing, the axial position Yb of the connecting portion 13 may be on the center side (Yb <Ya) of the raceway surface 2a with respect to the axial position Ya of the shoulder portion of the raceway surface 2a of the inner ring 2. The position of Yb in the figure is a position on the back side of the pocket where the inner diameter surface of the connecting portion 13 may exist, and extends to the same position as the axial position on the back side of the pocket at the center of the pocket 11 on the outer diameter side. There may be an outer wall surface. Similarly, the axial thickness of the connecting portion 13 may gradually or gradually increase from the Yb position toward the outer diameter side toward the pocket back side.

9 and 10 show the test results of confirming the grease adhesion state. In this test, a ball bearing incorporating the cage 5 of FIG. 7 and a ball bearing incorporating a general crown-shaped cage shown in FIG. 49 were operated and compared under the same conditions. FIG. 9 shows a grease adhesion state of a ball bearing using the cage 5 of FIG. 7, and FIG. 10 shows a grease adhesion state of a ball bearing using a general crown-shaped cage.
From the test results of FIG. 9 and FIG. 10, in the ball bearing (FIG. 10) incorporating a general crown-shaped cage, a large amount of grease exists between the cage inner surface and the outer diameter portion of the inner ring. Grease leaks toward the inner ring seal groove on the outer side in the direction, that is, the front side of the drawing. If a seal member is attached to the outer ring, grease flows between the seal groove and the seal tip, and leaks to the outside of the bearing as the temperature inside the bearing rises.
In the ball bearing (FIG. 9), a very small amount of grease is observed on the inner diameter portion of the cage 5, but not on the inner ring outer diameter portion.

  From the test results, in the cage 5, the inner surface of each pocket 11 is provided with a recess 16 as a grease scraping suppressing means that extends from the pocket opening edge on the cage inner diameter side to the cage outer diameter side. The amount of grease that adheres to the inner surface 5d of the cage 5 is reduced. Thereby, grease adhesion to the outer diameter part 2D of the inner ring 2 can be prevented. If no grease adheres to the outer diameter portion 2D, the grease can be prevented from flowing into the seal groove 7 (FIG. 1), and grease leakage can be prevented.

For example, in the conventional iron plate corrugated cage, grease in which the radius from the cage center of the inner circumferential portion of the pocket is larger than the radius from the cage center of the inner circumferential portion of the pocket When the leakage prevention structure is applied to a crown-shaped cage, it is necessary to partially delete the shape of the central bottom portion of the pocket. For this reason, the strength of the cage is greatly reduced, making it difficult to put it into practical use. Specifically, when the centrifugal force due to the rotation of the cage acts, distortion at the center bottom of the pocket is large, and this portion is broken or the amount of displacement of the connecting portion between adjacent pockets toward the outer diameter side is increased. Increases and causes contact with the outer ring.
On the other hand, since the recessed portion 16 of the cage 5 in the ball bearing 1 is not located at the bottom of the pocket 11, the strength reduction of the cage 5 can be reduced and can be practically used.

According to the angular ball bearing 1 described above, the concave portion 16 is provided in the crown-shaped cage 5, and the amount of grease adhering to the ball 4 can be reduced by the inner diameter surface 5d of the cage 5. Thereby, grease adhesion to the outer diameter part 2D of the inner ring 2 can be prevented. Therefore, it is possible to prevent the grease from adhering to the seal groove 7 of the inner ring 2. It is not necessary to change the design of the shape of the seal groove 7, and it is not necessary to secure a space for providing a slinger or the like. Therefore, the number of parts can be made smaller than that described in the above-mentioned patent document, and the manufacturing cost can be reduced.
Furthermore, in the seal member 6, the tip end portion Lmc of the seal lip 6c can be brought into contact with the track-side groove wall 7a at a contact position lower than the upper end position of the shoulder-side groove wall 7c facing the track-side groove wall 7a of the seal groove 7. Thereby, the scattered muddy water does not directly hit the front end portion Lmc of the seal lip 6c. Therefore, the tip of the seal lip 6c can be stably brought into contact with the track-side groove wall 7a, and the sealing performance of the seal member 6 can be sufficiently ensured.

The counter bore portion that forms the outer diameter surface of the inner ring on the left side of FIG. 1 is formed with a smaller diameter than the outer diameter portion 2D on the right side of the same figure. Easy to incorporate from the surface. Furthermore, the distance between the inner diameter surface 5d of the cages 5 and 5C on the back side of the pocket and the inner ring outer diameter surface can be increased. In this case, due to the synergistic effect of reducing the amount of the grease adhering to the balls 4 scraped by the inner diameter surface 5d of the cage 5 by the recess 16 as the grease scraping suppressing means of the cage 5, Prevents adhesion of grease to the diameter surface.
The right seal member 6 can prevent leakage of grease in the bearing and obtain muddy water resistance.

Next, another embodiment of the present invention will be described.
In the following description, the same reference numerals are given to portions corresponding to the matters described in the preceding forms in each embodiment, and overlapping description may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.
The example of FIG. 11 is a cage according to the embodiment of FIG. 6, in which the cross-sectional shape of the recess 16 (cross-sectional shape along the circumferential direction of the cage) is a polygonal shape instead of an arc shape. As shown in FIG. 5B, the shape is a polygonal shape substantially along the surface of each polygonal column VA centered on the straight line LA in the radial direction of the cage 5. This recessed portion 16 extends from the opening edge on the inner diameter side of the cage to the vicinity of the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases and becomes shallower as it approaches the ball arrangement pitch circle PCD from the inner diameter edge of the cage. And it is the shape which becomes narrow. Other configurations are the same as those in the example of FIG.

  Since the polygonal recess 16 is provided in the cage 5, the amount of the grease adhering to the balls 4 is scraped off by the inner diameter surface of the cage 5 is reduced. At the same time, the grease can be smoothly led from the inner diameter edge of the cage to the ball arrangement pitch circle PCD, and can contribute to lubrication efficiently. Since the polygonal recess 16 is gradually shallower and narrower as it approaches the ball arrangement pitch circle PCD, the grease oil film is held in the vicinity of the ball arrangement pitch circle PCD, contributing to lubrication efficiently and extending the bearing life. I can plan.

In the example of FIG. 12, the recesses 16 provided on the inner surface of the pocket 11 are provided at two locations on both sides of the center OW11 in the cage circumferential direction at the opening edge of the pocket 11, and each recess 16 is The cage extends to the vicinity of the outer edge 5g of the cage. The cross-sectional shape along the circumferential direction of the cage of the inner surface of these recesses 16 is an arc shape having a curvature radius RBb smaller than the curvature radius Ra of the concave spherical surface serving as the inner surface of the pocket 11, as shown in FIG. Further, the shape is substantially along the surface of one virtual ring VB. The virtual ring VB may be an outer peripheral surface of a grindstone that processes the recess 16. The virtual ring VB has a ring outer diameter that fits in the pocket 11 and has a donut shape with a circular cross-sectional shape at an arbitrary circumferential position, and the ring center OVB is located with respect to the cage center axis O as shown in FIG. Have a tilt.
Since the cage 5 is provided with the recess 16 having an arc-shaped cross section extending from the inner diameter edge of the cage to the vicinity of the outer diameter edge 5g of the cage, the grease adhering to the balls 4 is scraped off by the inner diameter surface 5d of the cage 5. Reduce the amount. At the same time, a part of the grease from the raceway surface 2a of the inner ring 2 to the inner diameter edge of the cage is moved to the outer diameter edge 5g of the cage via the recess 16 and smoothly guided to the raceway surface 3a of the outer ring 3. Is possible. Therefore, the bearing life can be extended.

In the present invention, the cross-sectional shape of the recess 16 along the circumferential direction of the cage is not limited to the shape of each example of FIGS. 6 to 8, but is partially elliptical, rectangular, trapezoidal, or any other arbitrary shape. It is good also as a cross-sectional shape. The cross-sectional shape of the recess 16 may be asymmetric with respect to the center of the recess.
The inner surface shape of the pocket 11 is not limited to a spherical shape, and may be any shape as long as the inner diameter side of the ball arrangement pitch circle PCD becomes a smaller diameter as it approaches the opening diameter of the cage inner diameter side. For example, the ball arrangement pitch circle PCD Further, the outer diameter side portion may be a cylindrical surface shape, and the inner diameter side portion may be a conical surface shape.

  14 shows an example in which the thickness t1 of the shell 11a of the pocket 11 is made relatively thick in the embodiment of FIG. An increase in the thickness t1 of the shell portion 11a causes an increase in the area of the inner diameter surface 5d of the cage 5, and thus tends to promote grease leakage. In particular, on the inner diameter surface 5d, a position where a large amount of grease accumulates is in the vicinity of the axial position (indicated by the symbol P) coinciding with the shoulder of the raceway surface 2a of the inner ring 2 in FIG. It is important to reduce the area of the inner diameter surface 5d of the cage 5 in the vicinity of the position. Therefore, in this embodiment, the recessed portion 26 is provided also on the outer surface of the shell portion 11a of the pocket 11 to reduce the area of the inner diameter surface of the pocket 11. As a result, a reduction in the amount of grease deposited on the inner diameter surface 5d of the cage 5 and an improvement in the strength of the cage alone can be achieved.

In order to reduce the area of the inner diameter surface 5d of the cage 5, the recessed portion 16 provided on the inner surface of the pocket 11 is made larger than the recessed portion 16 of each of the cages 5 as shown in a partially enlarged perspective view in FIG. You may do it.
As shown in a partially enlarged perspective view in FIG. 16, the annular body 12 constituting the retainer 5 is held in a shape in which the axial thickness on the inner diameter side is thin and gradually increases toward the outer diameter side. The area of the inner diameter surface 5d of the vessel 5 may be reduced. Similarly, the axial thickness of the annular body 12 may be increased stepwise from the inner diameter side to the outer diameter side.

  The cage 5 of FIG. 17 is a weight reduction by deleting a part of the pair of tip portions 14 protruding to the open side of the pocket 11 in the embodiment of FIG. When the ball bearing 1 is used at high speed rotation, the influence of centrifugal force acting on the cage 5 becomes large. In order to reduce the stress of the cage 5 due to the centrifugal force, it is effective to reduce the weight of the cage 5. Thus, in this embodiment, the outer diameter side of the tip portion 14 is partially deleted. At the time of high speed rotation, the front end portion 14 of the cage 5 is deformed so as to be inclined toward the outer diameter side with respect to the central portion of the pocket 11, so the ball 4 is guided on the inner diameter side of the front end portion 14. Therefore, even if a part of the outer diameter side of the tip end portion 14 is deleted, there is no adverse effect on the bearing function.

  In each of the embodiments described above, a preferable position of the recessed portion 16 on the inner surface of the pocket 11 is a position indicated by a symbol P in FIG. That is, the position in the bearing axial direction of the recessed portion 16 is a place that substantially coincides with the shoulder portion of the inner ring raceway surface 2 a when the cage 5 is incorporated into the ball bearing 1. This is because a large amount of grease accumulates on the inner diameter surface 5d of the cage 5 due to contact between the balls 4 and the inner ring raceway surface 2a and in the vicinity of the axial position that coincides with the shoulder portion of the raceway surface. Therefore, by defining the axial position of the recessed portion 16 at a location that coincides with the shoulder portion of the inner ring raceway surface 2a when the cage 5 is incorporated in the ball bearing 1, it accumulates on the inner diameter surface 5d of the cage 5. The obtained grease is effectively guided to the recess 16. Therefore, the amount of grease that adheres to the balls 4 is scraped off by the inner diameter surface 5d.

  The cage 5 of FIG. 18 is obtained by replacing the two recessed portions 16 on the inner surface of the pocket 11 with one recessed portion 16 in the cage according to the embodiment of FIGS. The recess 16 also extends from the opening edge on the inner diameter side of the cage to the outer diameter side of the cage, and the sectional shape of the inner surface of the recess 16 along the circumferential direction of the cage (that is, perpendicular to the central axis of the cage). The cross-sectional shape obtained by cross-section with a flat surface is an arc having a radius of curvature RCb smaller than the radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 11.

The recessed portion 16 is provided at one location so as to spread from the center OW11 in the cage circumferential direction at the opening edge of the pocket 11 to one side, and the width W16 of the recessed portion 16 is the width W11 of the pocket 11 in the cage circumferential direction. The width is almost the whole. The width W16 of the recess 16 is preferably larger than half of the width W11 of the pocket 11, and more preferably 2/3 or more, or 3/4 or more.
The inner surface shape of the recessed portion 16 is a cylindrical surface shape substantially along the surface of the virtual cylinder VC centered on the straight line LC in the radial direction of the cage 5 as shown in FIG. The virtual cylinder VC may be the surface of a grindstone that processes the recess 16. The recessed portion 16 extends from the opening edge on the cage inner diameter side to the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases, that is, gradually, from the cage inner diameter edge to the ball arrangement pitch circle PCD. The shape is shallow and narrow. In this embodiment, the dent 16 extends just to the ball arrangement pitch circle PCD, but may slightly extend to the outer diameter side of the cage with respect to the ball arrangement pitch circle PCD, or slightly to the ball arrangement pitch circle PCD. You may not reach it.
The depth of the concave portion 16 is such that the distance RCc from the center O11 of the concave spherical surface of the pocket inner surface to the deepest position of the concave portion 16 is 1.05 times or more the radius of the ball 4 (just 1.05 times). Preferably). The radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 11 is slightly larger than the radius of the ball 4 and is less than 1.05 of the radius of the ball 4.

In the single row angular contact ball bearing shown in FIG. 19, the seal groove 7 is formed on the back side of the pocket of the inner ring 2, that is, the left side, and the seal member 6 is provided only at the left end. A locking groove 8 is formed at the left end of the outer ring inner diameter surface corresponding to the left seal groove 7. Further, the counter bore portion forming the inner ring outer diameter surface on the right side of FIG. 19 is formed to have a smaller diameter than the outer diameter portion 2D on the left side of the same figure.
According to the configuration shown in FIG. 19, the grease pushed out from the raceway surface 2 a and the like to the left side of the drawing reduces the amount of grease adhered to the balls 4 by the inner diameter surface 5 d of the cage 5 by the grease scraping suppressing means. . Thereby, grease adhesion to the outer diameter part 2D of the inner ring 2 can be prevented, and grease flow to the seal groove 7 can be prevented. Even if some grease is attached to the outer diameter portion 2D, the grease in the bearing is not leaked by the left seal member 6. The left seal member 6 minimizes the entry of foreign matter from the outside of the bearing.

  Seal members 6 and 6 may be provided on both sides of the inner and outer rings as in the single-row angular ball bearing of FIG. Grease pushed out from the raceway surface 2a and the like to the right side of the figure can be prevented from leaking by the seal member 6 on the right side. With respect to the grease pushed out to the left side of the figure from the raceway surface 2a and the like, the grease scraping suppressing means of the cage 5 reduces the amount of grease adhered to the balls 4 by the inner diameter surface 5d. Therefore, grease flow to the seal groove 7 on the left side of the inner ring 2 can be prevented.

  FIG. 21A shows a sealed double-row angular contact ball bearing, which has an inner ring 2, an outer ring 3, a plurality of balls 4, cages 5, 5, and seal members 6, 6. . The contact angles α1 and α2 of the double row angular contact ball bearing have a substantially “C” -shaped cross section as indicated by a one-dot chain line in FIG. Double rows of balls 4 are interposed between the raceway surfaces 2a and 3a, and cages 5 in each row hold a plurality of balls 4 in each row. The pocket open side of the cages 5 in each row is directed inward in the axial direction, and the back side of the pocket faces the seal member 6 with a slight distance. In other words, it arrange | positions so that the pocket surface of the two holder | retainers 5 and 5 may face each other. Grease is sealed in the bearing space.

In this double row angular contact ball bearing, the use of the seal member 6 and the cage 5 achieves low torque, grease leakage resistance, muddy water resistance, and space saving at the same time and at low cost.
As shown in FIGS. 21A and 21B, circumferential seal grooves 7 and 7 are formed on both sides of the double-row raceway surfaces 2 a and 2 a in the inner ring 2, and the outer ring 3 facing each seal groove 7. The locking grooves 8, 8 are formed on the inner peripheral surface of the. The outer peripheral edge portion 9 of the seal member 6 is press-fitted and fixed in the locking groove 8.
The seal groove 7 is formed of a groove wall 7a on the raceway surface side of the inner ring 2, a bottom surface 7b, and a groove wall 7c on the shoulder 2b side. The groove wall 7c is inclined outward in the axial direction, and is formed continuously with the outer peripheral surface of the shoulder 2b.

According to this double row angular contact ball bearing, each crown-shaped cage 5 is provided with a recessed portion 16 as a grease scraping suppressing means, and is arranged so that the pocket surfaces of the two cages 5 and 5 face each other. Therefore, grease leakage from the back side of the cage is suppressed. Thereby, grease adhesion to the outer diameter part 2D of the inner ring 2 can be prevented. Therefore, it is possible to prevent grease from adhering to the seal groove 7 of the inner ring 2, and it is not necessary to change the design of the shape of the seal groove 7, and it is not necessary to provide a space for providing a slinger or the like. Therefore, the number of parts can be made smaller than that described in the above-mentioned patent document, and the manufacturing cost can be reduced.
Further, in the seal member 6, the tip end portion Lmc of the seal lip 6c can be brought into contact with the track-side groove wall 7a at a contact position lower than the upper end position of the shoulder-side groove wall 7c facing the track-side groove wall 7a of the seal groove 7. It becomes possible. Thereby, the scattered muddy water can be prevented from directly hitting the tip end portion Lmc of the seal lip 6c. Therefore, even when used in an environment where muddy water or the like scatters, the tip of the seal lip 6c can be brought into stable contact with the track-side groove wall 7a of the seal groove 7 and the sealing performance of the seal member 6 can be sufficiently secured.

  In the double-row angular contact ball bearing, the above-described cage shape can suppress the grease from adhering to the inner ring outer diameter portion 2D, and the grease leakage from the back surface side of the cage, that is, the anti-pocket side can be suppressed. Further, by using the seal member 6, it is possible to prevent grease leakage in the bearing and to obtain muddy water resistance. Therefore, since it is not necessary to increase the tension of the lip or the like, the torque can be reduced.

The rolling bearing shown in FIG. 22 is a single-row sealed deep groove ball bearing, and is provided with a cage 5C for holding a plurality of balls 4, and both ends of the annular space formed between the inner and outer rings 2 and 3 are respectively shown in FIG. Or it sealed with the sealing member 6 shown in FIG.
The cage 5C will be described with reference to FIGS.
The cage 5C has a crown shape, and each pocket 11 is provided with a pair of claws 14 and 14 as grease scraping suppressing means for suppressing grease from adhering to the outer diameter portion 2D (FIG. 22) of the inner ring 2. ing. Between the pair of claws 14 and 14 of each pocket 11, the distance between the tips of the claw portions 14b and 14b on the outer diameter side of the cage is narrower than the distance between the tips of the claw portions 14a and 14a on the cage inner diameter side. Is set. In this example, the distance between the tips of the pair of claws 14 is gradually reduced from the cage inner diameter side toward the cage outer diameter side. The protruding length L1 of the claw portion 14a on the inner diameter side of the cage is the same as the protruding length of the claw in a general crown-shaped cage. The protruding length L2 of the claw portion 14b on the cage outer diameter side is longer than the protruding length L1 of the claw portion 14a on the cage inner diameter side. Specifically, as shown in FIG. 27 which shows a cross section along the circumferential direction of the cage of the claw 14 (cross section along the pitch circle PCD of the ball arrangement), the front end of the claw portion 14a from the pocket center O11 and the holding The angles θa and θb with respect to the circumferential direction of the cage facing the tip of the claw portion 14b on the outer diameter side of the device are preferably set as follows. That is, the angle θb that faces the tip of the claw portion 14b on the outer diameter side of the cage is set to be 1.5 times or more (θb ≧ 1.5θa) of the angle θa that faces the tip of the claw portion 14a on the cage inner diameter side. Is preferred.

  The width in the cage radial direction of the claw portion 14b on the cage outer diameter side is desirably set as shown in FIG. That is, when the total width (pocket width) of the claw 14 projected onto the straight line N in the cage radial direction passing through the center of the cage 11 in the circumferential direction of the pocket 11 is It, the outer diameter side of the cage projected onto the straight line N is assumed. The width Ie of the claw portion 14b is preferably set to 2/3 or less (Ie ≦ 2 / 3It) of the full width It.

  In general, the assembly of a ball bearing using a crown-shaped cage is performed by inserting the cage into the inner and outer rings and then incorporating the cage. When the crown-shaped cage is made of resin, if the distance between the tips of the pair of claws in the pocket is smaller than 90% of the ball diameter, an excessive force is applied to the nails when the cage is assembled to the ball, The possibility of whitening or damage at the base of the nail increases. In this embodiment, the distance between the tips of the claw portions 14 b on the cage outer diameter side is narrower than 90% of the diameter of the balls 4. For this reason, after putting the ball 4 in the ball bearing 1, it is difficult to incorporate the finished product of the cage.

  Therefore, in this embodiment, the cage 5C is manufactured by the steps shown in FIGS. 25A, the claw component 14ba having a claw tip portion projecting from the claw portion 14a on the cage inner diameter side of the claw portion 14b on the cage outer diameter side of the claw 14 as shown in FIG. The cage body 5A is formed separately. Then, after the cage body 5A is incorporated into the inner and outer rings 2, 3 (FIG. 22) and the ball 4 of the ball bearing 1, the claw component 14ba is bonded to the cage body 5A as shown in FIG. Weld by hot press or fit. As a result, it is possible to avoid whitening or breakage at the base of the nail 14 during assembling. The claw component 14ba is not limited to the claw tip portion protruding from the claw portion 14a, but may be the most or the whole claw portion 14b on the cage outer diameter side.

  26A, the claw tip portion 14ba of the claw 14 on the outer diameter side of the cage that protrudes from the claw portion 14a on the inner diameter side of the cage is completed as shown in FIG. The cage semi-finished product 5B having an open posture away from the pocket center O11 is manufactured. Then, after incorporating the cage semi-finished product 5B into the inner and outer rings 2, 3 (FIG. 22) and the ball 4 of the ball bearing 1, the claw tip portion 14ba is placed on the surface of the ball 4 as shown in FIG. In the closed position along it, it is bent while applying heat to cause thermal deformation or secondary processing. As a result, it is possible to avoid whitening or breakage at the base of the nail 14 during assembly.

  The grease behavior in the ball bearing provided with the cage 5C will be described with reference to FIG. As shown in FIG. 6A, the grease from the outer ring 3 is scraped off by the outer diameter portion of the claw portion 14b on the outer diameter side of the cage, and the grease does not adhere to the inner ring 2. Grease from the inner ring 2 is also scraped off at the inner diameter portion of the claw portion 14b on the outer diameter side of the cage, and the amount of grease adhering to the balls 4 is reduced, as shown in FIG. It is suppressed. Since the scraped grease is located far from the inner ring outer diameter surface 2D, the scraped grease does not adhere to the inner ring outer diameter surface 2D.

FIGS. 30 and 31 show a grease leakage test for the cage 5C of this embodiment by changing the angle θb (FIG. 27) and the width Ie (FIG. 28) of the claw portion 14b on the cage outer diameter side of the claw 14. It is a graph which shows the result of having performed. Table 1 shows the test conditions in this case.

In FIG. 30, the vertical axis represents the ratio of grease leakage, and the horizontal axis represents the ratio of the angle θb of the cage outer diameter side claw 14b to the angle θa of the cage inner diameter claw 14a (corresponding to a conventional claw). Represents. In this test, the width Ie of the claw portion 14b on the outer diameter side of the cage in FIG. 28 is set to 1/2 (Ie = 1 / 2It) of the total width (pocket width) It of the claw 14.
From the test results shown in FIG. 30, it can be seen that when the protrusion length L2 of the claw portion 14b on the cage outer diameter side is short, the grease adhering to the balls 4 cannot be scraped off sufficiently.

In FIG. 31, the vertical axis represents the ratio of grease leakage, and the horizontal axis represents the ratio of the width Ie of the claw portion 14b on the cage outer diameter side to the total width (pocket width) It of the claw 14. In this test, the angle θb in FIG. 27 of the claw portion 14b on the cage outer diameter side is 1.67 times (θb = 1.67θa) the angle θa of the claw portion 14a on the cage inner diameter side.
From the test results shown in FIG. 31, the larger the width Ie of the claw portion 14b on the cage outer diameter side, the closer the inner diameter portion of the claw portion 14b approaches the outer diameter surface 2D of the inner ring 2 (FIG. 22). The grease scraped from the inner ring 2 side as shown in (B) adheres directly to the outer diameter surface of the inner ring 2.
From the above test results, as described above, as the shape of the claw 14 effective in suppressing grease leakage, the angle θb of the claw portion 14b on the cage outer diameter side in FIG. 27 is set to the claw portion 14a on the cage inner diameter side. The angle θa is preferably 1.5 times or more. In addition, the width Ie of the claw portion 14b on the cage outer diameter side in FIG. 28 is preferably set to 2/3 or less of the full width (pocket width) It of the claw 14.

  32 and 33 show test results for confirming the grease adhesion state. In this test, a ball bearing in which a cage 5C was incorporated and grease was sealed was compared with a ball bearing in which a general crown-shaped cage was sealed and grease was operated under the same conditions. As operating conditions, an axial load was applied to the inner ring in the direction perpendicular to the paper surface, and the outer ring was rotated in the direction of the arrow in FIG. FIG. 32 shows the grease adhesion state of a ball bearing using the cage 5C of the embodiment, and FIG. 33 shows the grease adhesion state of a ball bearing using a general crown-shaped cage.

  From the test results, in a ball bearing incorporating a general crown-shaped cage (Fig. 33), grease adheres to the outer diameter part of the inner ring, and grease also adheres to the surface of the ball. It can be seen that it is formed. In the ball bearing (FIG. 32) incorporating the cage 5C, the grease is scraped off by the claw portion 14b on the cage outer diameter side, so that the grease does not adhere to the outer diameter portion 2D of the inner ring 2 and the surface of the ball 4 The grease cap is not formed.

As can be seen from the test results, in the ball bearing provided with the cage 5C, the claw portion on the outer diameter side of the cage is larger than the distance between the tips of the claw portions 14a on the cage inner diameter side of the pair of claws 14 of each pocket 11. By reducing the distance between the tips of 14b, the grease adhering to the balls 4 is not brought close to the outer diameter portion 2D of the inner ring 2 from the outer ring 3 side, and the grease from the inner ring 2 side is also the outer diameter portion 2D of the inner ring 2. Can be scraped off by the claw portion 14b on the outer diameter side of the cage away from the cage, and as a result, grease leakage from the ball bearing 1 can be prevented.
Further, as shown in FIG. 22, the ball bearing 1 is provided with an inner peripheral surface Lmb (FIG. 3) facing the seal groove 7 on the main lip Lm (FIG. 3) in the seal member 6 and the labyrin slip Lb. By forming the inclined surface Lba on the inner periphery, the tip end portion Lmc (FIG. 3) of the main lip Lm, which is a contact seal, is moved from the upper end position of the shoulder side groove wall 7c facing the track side groove wall 7a of the seal groove 7. Further, it can be brought into contact with the track-side groove wall 7a of the seal groove 7 at a low contact position. Therefore, it is possible to prevent the scattered muddy water from directly hitting the tip end portion Lmc of the seal lip 6c. Therefore, even if this bearing is used in an environment where muddy water or the like is scattered, the tip Lmc of the seal lip 6c is stably brought into contact with the raceway-side groove wall 7a of the seal groove 7 to sufficiently secure the sealing performance of the contact seal. can do. That is, by using the seal member 6, it is possible to prevent grease leakage in the bearing and to obtain muddy water resistance. Therefore, since it is not necessary to increase the tension of the lip or the like, the torque can be reduced. In this case, a space for providing a slinger or the like is not necessary, and the manufacturing cost can be reduced without increasing the number of parts.

In the above embodiment, an example has been shown in which the protrusion length of the claw portion 14a on the cage inner diameter side and the claw portion 14b on the cage outer diameter side changes stepwise. As long as the protrusion length L2 of the tip of the claw on the outer diameter side of the cage is long, the shape of the claw 14 may be any shape as long as it is not in contact with the inner and outer rings 2, 3 and the contact seal 6.
FIG. 34 shows another example of the shape of the claw 14 in the cage 5C of the ball bearing of this embodiment. In this example, the interval between the tips of the pair of claws 14, 14 of each pocket 11 is infinitely narrowed from the cage inner diameter side toward the cage outer diameter side.

In the example of FIG. 35, the tips on the cage inner diameter side of the pair of claws 14 and 14 of each pocket 11 are opened, and the tips on the cage outer diameter side are connected. In this example, in the pair of claws 14 and 14 of the cage 5C shown in FIG. 24, the opposing claw portions 14b and 14b on the outer diameter side of the cage are further extended to be connected to each other.
FIG. 36 shows a manufacturing method of the cage 5C having the claw shape shown in FIG. In this manufacturing method, as shown in FIG. 36 (A), the retainer outer diameter side claw portion 14b connected between the pair of claws 14, 14, and the cage circumferential direction from both ends of the claw portion 14b. A claw component 14A having a connecting portion 14c that extends and a fitting projection 14d that protrudes from the connecting portion 14c toward the back side of the cage pocket is formed separately from the cage body 5A. The claw component 14 </ b> A has an annular shape that extends across the plurality of pockets 11, and has a plurality of claw portions 14 b corresponding to the plurality of pockets 11. In the cage body 5A, a fitting hole 13a into which the fitting projection 14d of the claw component 14A is fitted is formed in the connecting portion 13 of the annular body 12. Then, after the cage body 5A is incorporated into the inner and outer rings 2, 3 (FIG. 22) and the ball 4, the fitting projection 14d of the claw component 14A is fitted into the cage body 5A as shown in FIG. It fits in the joint hole 13a. Thus, if one claw component 14A has a shape having a plurality of claw portions 14b corresponding to a plurality of pockets 11, the claw portion 14b on the outer diameter side of the cage can be covered with a smaller number of parts than the number of pockets. Can be assembled easily, and the manufacturing cost can be reduced.

In the cage 5C shown in FIGS. 37 and 38, in the embodiment shown in FIG. 24, a plurality of recesses 16 extending from the pocket opening edge on the cage inner diameter side to the cage outer diameter side are further formed on the inner surface of the pocket 11. The recessed part 16 similar to FIG. 6 (A), (B) is provided. By providing the recess 16, the amount of grease adhering to the ball 4 is scraped off from the inner diameter surface of the cage 5C, and the adhesion of grease to the outer diameter 2D (FIG. 22) of the inner ring 2 is prevented. To do.
In the example of FIG. 39, in the embodiment of FIG. 38, the cross-sectional shape (cross-sectional shape along the circumferential direction of the cage) of the recessed portion 16 is a polygonal shape instead of an arc shape. Other configurations in this embodiment are the same as those in the example of FIG.
In the example of FIG. 40, the recesses 16 provided on the inner surface of the pocket 11 are provided at two positions on both sides of the center OW11 in the cage circumferential direction at the opening edge of the pocket 11. Although it is the same as that of embodiment, each recessed part 16 is extended to the cage | basket outer-diameter edge vicinity.

The cage 5C of FIG. 42 is obtained by deleting the pocket back side of the inner diameter surface of the connecting portion 13 in the embodiment shown in FIGS. Thereby, in the pocket 11, the back side of the pocket becomes a shape surrounded by the arc-shaped shell portion 11a.
In the embodiment shown in FIGS. 38 to 40, although the amount of grease scraped off the ball 4 by the inner surface of the cage 5C can be reduced by the dent 16, If the amount of accumulation increases, it will lead to grease leakage. That is, in this case, grease adheres to the inner diameter surface of the connecting portion 13 and the grease in this portion can move only in the axial direction. When the axial range of the connecting portion 13 overlaps with the region where the outer diameter portion 2D of the inner ring 2 is present, that is, when the inner diameter surface of the connecting portion 13 is located closer to the bearing end surface than the raceway surface 2a of the inner ring 2 The grease leaks out of the bearing from the inner diameter surface of the connecting portion 13. Therefore, as shown in FIG. 42, when the pocket back side of the inner diameter surface of the connecting portion 13 is deleted, it is possible to prevent the grease from leaking out of the bearing from the inner diameter surface of the connecting portion 13.

In the embodiment of FIG. 42, an example is shown in which the connecting portion 13 is deleted from the inner surface to the outer surface on the back side of the pocket, but when the strength of the cage 5 is considered, the amount of deletion is small. Is desirable. In order to suppress the adhesion of grease to the outer diameter portion 2D of the inner ring 2, it is also effective to increase the distance between the outer diameter surface of the inner ring 2 and the inner diameter surface of the cage 5, so that only the inner diameter side of the connecting portion 13 is used. May be deleted to leave a conventional wall surface on the outer diameter side. That is, in the cross-section at the circumferential center position of the connecting portion 13 between the adjacent pockets 11, 11, the axial position of the end point on the back side of the pocket of the inner diameter surface that is left without being deleted of the connecting portion 13 is defined as the inner ring 2. In order to prevent grease leakage, it is important to locate the center of the raceway surface 2a from the shoulder of the raceway surface 2a. This is shown in FIG. 45 as a schematic diagram of the positional relationship in the axial direction Y, with the sectional view of the inner ring 2 indicated by the phantom line superimposed on the cage 5C of FIG. In the drawing, the axial position Yb of the connecting portion 13 may be on the center side (Yb <Ya) of the raceway surface 2a with respect to the axial position Ya of the shoulder portion of the raceway surface 2a of the inner ring 2.
The position of Yb in the figure is a position on the back side of the pocket where the inner diameter surface of the connecting portion 13 may exist, and extends to the same position as the axial position on the back side of the pocket at the center of the pocket 11 on the outer diameter side. There may be an outer wall surface. Similarly, the shape in which the axial thickness of the connecting portion 13 gradually or gradually increases from the Yb position toward the outer diameter side toward the pocket rear surface side may be used.

In this embodiment, a recess 26 is also provided on the outer surface of the shell portion 11a of the pocket 11 to reduce the area of the inner diameter surface of the pocket 11, reducing the amount of grease deposited on the inner diameter surface of the cage 5C, and the cage. It is possible to achieve both strength improvement of a single substance.
In order to reduce the area of the inner diameter surface of the cage 5C, the recessed portion 16 on the inner surface of the pocket 11 may be enlarged as shown in a partially enlarged perspective view in FIG.
As shown in a partially enlarged perspective view in FIG. 44, the annular body 12 has a shape in which the axial thickness on the inner diameter side is thin and gradually increases toward the outer diameter side. The area may be reduced. The axial thickness of the annular body 12 may be increased stepwise from the inner diameter side to the outer diameter side.

  In the ball bearing cage 5C of FIGS. 37 to 44, the inner surface of each pocket 11 is attached to the ball 4 by providing a recess 16 extending from the pocket opening edge on the cage inner diameter side to the cage outer diameter side. The amount of grease scraped off by the inner surface of the cage 5C is reduced. This effect and the above-described effect of the claw shape can be combined to effectively prevent the adhesion of grease to the outer diameter portion 2D of the inner ring 2. Further, by using the seal member 6, the tip end Lmc of the seal lip 6 c can be stably brought into contact with the track-side groove wall 7 a of the seal groove 7 even when this bearing is used in an environment where muddy water or the like is scattered. The sealing performance of the seal can be sufficiently ensured. Therefore, grease leakage in the bearing can be prevented and muddy water resistance can be obtained. Therefore, since it is not necessary to increase the tension of the lip or the like, the torque can be reduced.

A grease leakage prevention structure of a conventional cage in which the radius from the cage center of the inner diameter of the circumferential portion with the pocket is larger than the radius from the cage center of the inner diameter of the circumferential portion between the pockets, When applied to a crown-shaped cage, it is necessary to partially delete the shape of the central bottom of the pocket. For this reason, the strength reduction of the cage is large, and it is difficult to put it into practical use. Specifically, when the centrifugal force due to the rotation of the cage acts, distortion at the center bottom of the pocket is large, and this portion is broken or the amount of displacement of the connecting portion between adjacent pockets toward the outer diameter side is increased. Increases and causes contact with the outer ring.
On the other hand, since the recessed portion 16 in the cage 5C is not located at the bottom of the pocket 11, the strength reduction of the cage 5C can be reduced and can be practically used.

  In each of the above-described embodiments, the preferred position of the recess 16 on the inner surface of the pocket 11 is the position indicated by the symbol P in FIG. In other words, the position in the bearing axial direction of the recess 16 is a place that substantially coincides with the shoulder of the inner ring raceway surface 2 a when the cage 5 </ b> C is incorporated into the ball bearing 1. This is because a large amount of grease accumulates on the inner diameter surface of the cage 5C due to contact between the balls 4 and the inner ring raceway surface 2a and in the vicinity of the axial position that coincides with the shoulder portion of the raceway surface.

The ball bearing retainer 5C in FIG. 46 is obtained by replacing the two recessed portions 16 provided on the inner surface of the pocket 11 with one recessed portion 16 in the embodiment of FIGS. . The recess 16 also extends from the opening edge on the inner diameter side of the cage to the outer diameter side of the cage, and the sectional shape of the inner surface of the recess 16 along the circumferential direction of the cage (that is, perpendicular to the central axis of the cage). The cross-sectional shape obtained by cross-section with a flat surface is an arc having a radius of curvature RCb smaller than the radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 11.
In each embodiment shown in FIGS. 37 to 46, the grease leakage countermeasure by the claw shape in the embodiment shown in FIGS. 22 to 36 and the grease leakage countermeasure on the back side of the cage pocket by the recessed portion 16 formed on the inner surface of the pocket 11 are used. Therefore, in the single row ball bearing, it is possible to provide a bearing in which grease leakage does not occur. Further, by using the seal member 6, it is possible to prevent grease leakage in the bearing and to obtain muddy water resistance.

47 and 48 show still another embodiment. In the cage according to each of the embodiments described above, a cylindrical small protrusion 15 may be provided on the side surface of each connecting portion 13. 47A shows a case where a plurality of small protrusions 15 are provided in the cage of FIG. 6A, and FIG. 47B shows a case where a plurality of small protrusions 15 are provided in the holder of FIG. is there. FIG. 48A shows a case in which a plurality of small protrusions 15 are provided in the cage of FIG. 38A, and FIG. 48B shows a case in which a plurality of small protrusions 15 are provided in the holder of FIG. 46B. is there.
A cylindrical small protrusion 15 that protrudes a predetermined small distance in the axial direction may be provided on the side surface of each connecting portion 13 on the pocket opening side. These small protrusions 15 are for guiding the balls 4 to a predetermined position when the cage 5 is incorporated into the ball bearing 1. Since each small protrusion 15 is present, it is possible to prevent a part of the plurality of balls 4 arranged at appropriate intervals in the circumferential direction from fitting into the stepped portion 13a on the side surface of the connecting portion 13 on the pocket opening side. Therefore, it is possible to reduce the number of steps for assembling the bearing. In addition, a cylindrical small protrusion is formed on the side surface of each connecting portion 13 of the cage of FIGS. 11, 14 to 17, 23, 28, 34, 35, 39, 40, and 42 to 44. 15 may be provided.

It is a partial expanded sectional view of the angular ball bearing concerning one embodiment of this invention. It is sectional drawing which shows the state before incorporating the sealing member of the angular ball bearing into a bearing. It is sectional drawing which expands and shows the principal part of FIG. It is sectional drawing which expands and shows the principal part of FIG. It is a graph which shows the result of a foreign material penetration test. (A) is a partial enlarged perspective view of an example of the cage, and (B) is a perspective view showing a state in which a virtual cylinder is added to the perspective view. It is a perspective view of the holder | retainer of the bearing concerning the modification which changed the embodiment of this invention partially. It is explanatory drawing of the relationship of the axial direction position between the pocket of the holder | retainer, and an inner ring raceway surface. (A) is explanatory drawing of the result of the grease leak test of the ball bearing incorporating the cage | basket of the structure shown in FIG. 7, (B) is the elements on larger scale of (A). (A) is explanatory drawing of the result of the grease leak test of the ball bearing incorporating the general crown-shaped cage, (B) is the elements on larger scale of (A). (A) is a partial enlarged perspective view of another example of the cage, (B) is a perspective view showing a state in which a virtual polygonal column is added to the perspective view. (A) is a partial enlarged perspective view of still another example of the cage, and (B) is a perspective view showing a state in which a virtual ring is added to the perspective view. It is explanatory drawing which shows the relationship between the pocket of the holder | retainer, and a virtual ring in a cross section. It is a perspective view of the holder | retainer concerning further another embodiment of this invention. It is a partial expansion perspective view of the holder concerning other embodiments of this invention. It is a partial expansion perspective view of the holder concerning other embodiments of this invention. It is a partial expansion perspective view of the holder concerning other embodiments of this invention. (A) is a partial expanded perspective view of the holder | retainer concerning further another embodiment of this invention, (B) is a perspective view which shows the state which added the virtual cylinder to the perspective view. It is a partial expanded sectional view of the angular ball bearing concerning further another embodiment of this invention. It is a partial expanded sectional view of the angular ball bearing concerning further another embodiment of this invention. (A) is a partial expanded sectional view of the double row angular contact ball bearing concerning other embodiment of this invention, (B) is a sectional view showing the state before incorporating the seal member of the double row angular contact ball bearing in a bearing. is there. It is a partial expanded sectional view of the rolling bearing concerning further another embodiment of this invention. It is a perspective view of the retainer of the bearing. It is a partial expansion perspective view of the holder. It is explanatory drawing of the manufacturing method of the same holder | retainer. It is explanatory drawing of the other manufacturing method of the holder | retainer. It is explanatory drawing of the angle from the pocket center of the nail | claw tip of the holder | retainer. It is explanatory drawing of the width | variety of the nail | claw of the holder | retainer. It is explanatory drawing of the grease behavior by the cage. It is a graph which shows the test result of the relationship between the angle from the pocket center of the nail | claw part front-end | tip of the holder | retainer outer diameter side of the holder | retainer, and a grease leak rate. It is a graph which shows the test result of the relationship between the width | variety of the nail | claw part of the cage | basket outer-diameter side of this cage, and a grease leak rate. It is explanatory drawing of the result of the grease leak test of the ball bearing incorporating the same cage. It is explanatory drawing of the result of the grease leak test of the ball bearing incorporating a general crown-shaped cage. It is a side view which shows the other example of a shape of the nail | claw of the holder | retainer in the ball bearing of this invention. It is a side view which shows the other example of a shape of the nail | claw of a holder | retainer. It is explanatory drawing of the manufacturing method of the holder | retainer of FIG. It is a perspective view of the holder | retainer of other embodiment of this invention. (A) is a partial enlarged perspective view of an example of the cage, and (B) is a perspective view showing a state in which a virtual cylinder is added to the perspective view. (A) is a partial enlarged perspective view of another example of the cage, (B) is a perspective view showing a state in which a virtual polygonal column is added to the perspective view. (A) is a partial enlarged perspective view of still another example of the cage, and (B) is a perspective view showing a state in which a virtual ring is added to the perspective view. It is explanatory drawing which shows the relationship between the pocket of the holder | retainer, and a virtual ring in a cross section. It is a perspective view of the holder | retainer concerning further another embodiment of this invention. It is a partial expansion perspective view of the holder concerning other embodiments of this invention. It is a partial expansion perspective view of the holder concerning other embodiments of this invention. It is explanatory drawing of the relationship of the axial direction position between the pocket of a holder | retainer, and an inner ring raceway surface. (A) is a partial expanded perspective view of the holder | retainer concerning further another embodiment of this invention, (B) is a perspective view which shows the state which added the virtual cylinder to the perspective view. (A) Partial expansion perspective view of the holder | requirement concerning further another embodiment of this invention, (B) The partial expansion perspective view of the holder | requirement concerning further another embodiment of this invention. (A) Partial expansion perspective view of the holder | requirement concerning further another embodiment of this invention, (B) The partial expansion perspective view of the holder | requirement concerning further another embodiment of this invention. It is a schematic perspective view of the holder | retainer concerning a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Ball bearing 2 ... Inner ring 3 ... Outer ring 4 ... Ball 5 ... Cage 6 ... Seal member 6a ... Core metal 6b ... Elastic member 7 ... Seal groove 7a ... Track side groove wall 7c ... Shoulder side groove wall 11 ... Pocket 12 ... Ring shape Body 14 ... Claw 16 ... Recessed portion Ds ... Stepped portion Lb ... Labyrin slip Lba ... Inclined surface Lm ... Main lip Lmb ... Inner peripheral surface

Claims (15)

In the angular ball bearing in which a plurality of balls intervening between the inner and outer rings are held in a cage, and a seal member that closes the bearing space between the inner ring and the outer ring is provided in the outer ring,
A shoulder is formed between a seal groove formed on a side of the race of the inner ring and an end of the inner ring, and the seal member is attached to an inner peripheral surface of the outer ring facing the seal groove, Provided on the inner periphery of the seal member is a main lip that contacts the raceway groove wall of the seal groove, and a labyrinth slip that protrudes above the shoulder,
The main lip and the labyrinth slip are provided at the inner circumferential tip of the seal member, the inner lip is provided on the main lip so as to face the seal groove, and the labyrin slip is formed on the inner circumference of the labyrin slip. Form an inclined surface that gradually expands toward the tip,
The retainer is a crown shape having pockets that are partially opened on one side surface of the annular body and hold balls therein at a plurality of locations in the circumferential direction of the annular body,
An angular contact ball bearing characterized in that a grease scraping suppressing means for suppressing the grease adhering to the balls from being scraped off at the inner diameter surface of the cage is provided in the cage. An outer ring having a double row raceway surface on the inner periphery, an inner ring having a double row raceway surface facing the raceway surface on the outer periphery, a double row ball interposed between the raceways of the inner ring and the outer ring, and each row In a double row angular contact ball bearing comprising two cages for holding the ball and seal members on both sides provided in the outer ring and closing the bearing space between the inner ring and the outer ring,
A shoulder is formed between a seal groove formed on a side of the race of the inner ring and an end of the inner ring, and the seal member is attached to an inner peripheral surface of the outer ring facing the seal groove, Provided on the inner periphery of the seal member is a main lip that contacts the raceway groove wall of the seal groove, and a labyrinth slip that protrudes above the shoulder,
The main lip and the labyrinth slip are provided at the inner circumferential tip of the seal member, the inner lip is provided on the main lip so as to face the seal groove, and the labyrin slip is formed on the inner circumference of the labyrin slip. Form an inclined surface that gradually expands toward the tip,
The retainer has a crown shape in which a part of one side portion of the annular body is opened to hold a ball inside the annular body at a plurality of circumferential positions of the annular body, and two cages It is arranged so that the pocket faces face each other,
A double-row angular contact ball bearing, wherein each retainer is provided with grease scraping restraining means for restraining the grease adhering to the balls from being scraped off at the inner diameter surface of the retainer.   3. The double-row angular contact ball bearing according to claim 2, wherein the grease scraping suppressing means is provided with a concave portion extending from a pocket opening edge on the inner diameter side of the cage toward the outer diameter side of the cage on the inner surface of each pocket.   4. The double-row angular contact ball bearing according to claim 2, wherein an inclination angle of the inclined surface of the labyrin slip is set to 10 degrees or more and 40 degrees or less with respect to the outer peripheral surface of the shoulder portion.   5. The stepped portion according to claim 2, wherein the inclined surface of the labyrinth slip is provided with a stepped portion projecting toward a shoulder side groove wall of the seal groove at an axially inner end portion thereof. A double-row angular contact ball bearing continuously provided on the inner peripheral surface of the main lip.   6. The double-row angular contact ball bearing according to claim 2, wherein the sealing member is an elastic body reinforced with a cored bar.   7. The double-row angular contact ball bearing according to claim 6, wherein the elastic body of the seal member is hydrogenated nitrile rubber or ester acrylic rubber.   The double-row angular contact ball bearing according to any one of claims 2 to 7, wherein a concave portion extending from a cage inner diameter edge to a cage outer diameter side on a back surface of each pocket of the cage is provided. In a rolling bearing in which a plurality of balls interposed between the inner and outer rings are held by a cage, and a seal member that closes a bearing space between the inner ring and the outer ring is provided in the outer ring,
A shoulder is formed between a seal groove formed on a side of the race of the inner ring and an end of the inner ring, and the seal member is attached to an inner peripheral surface of the outer ring facing the seal groove, Provided on the inner peripheral portion of the seal member is a main lip that contacts the raceway-side groove wall of the seal groove, and a labyrinth slip protruding above the shoulder,
The main lip and the labyrinth slip are provided at the inner circumferential tip of the seal member, the inner lip is provided on the main lip so as to face the seal groove, and the labyrin slip is formed on the inner circumference of the labyrin slip. Form an inclined surface that gradually expands toward the tip,
The retainer is a crown shape having pockets that are partially opened on one side surface of the annular body and hold balls therein at a plurality of locations in the circumferential direction of the annular body,
A rolling bearing according to claim 1, wherein a grease scraping suppressing means that suppresses the grease adhering to the balls from being scraped by the inner diameter surface of the cage is provided in the cage. In claim 9, the grease scraping suppressing means is provided with a recessed portion extending from the pocket opening edge on the inner diameter side of the cage to the outer diameter side of the cage on the inner surface of each pocket.
A pair of claws facing in the circumferential direction are provided on the open side of each pocket so as to protrude in the axial direction, and the outer diameter of the cage is larger than the distance between the tips on the inner diameter side of the pair of claws of each pocket. Rolling bearing with a narrower distance between tip ends. In Claim 9 or Claim 10, on the open side of each pocket in the cage, a pair of claws facing the circumferential direction are provided protruding in the axial direction,
The rolling bearing which open | released between the front-end | tips of the holder inner diameter side of a pair of nail | claw of each said pocket, and connected between the front-end | tips on the outer diameter side of a holder | retainer.   The rolling bearing according to claim 9, wherein the distance between the tips of the pair of claws of each pocket is gradually reduced from the inner diameter side of the cage toward the outer diameter side of the cage.   The rolling bearing according to claim 9, wherein the interval between the tips of the pair of claws of each pocket is steplessly narrowed from the cage inner diameter side toward the cage outer diameter side.   The holding outer diameter of the nail projected on the straight line according to claim 11 or 12, wherein the total width of the claw projected onto a straight line in the radial direction of the cage passing through the center in the circumferential direction of the cage in the pocket is defined as It. A rolling bearing in which the width of the claw portion on the outer diameter side of the cage is set so that the width Ie of the claw portion on the side is 2/3 It or less.   The claw tip on the cage inner diameter side and the cage outer diameter side from the position corresponding to the pocket center in the cross-section along the circumferential direction of the cage of the claw according to any one of claims 10, 12 to 14. A rolling bearing in which the angle of the claw tip with respect to the cage circumferential direction is set so that the angle of the claw tip on the cage outer diameter side is 1.5 times or more of the angle of the claw tip on the cage inner diameter side.

Images