JP2006234100A - Double-row angular ball bearing and pinion shaft supporting device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double-row angular ball bearing with long service life and less agitating resistance and a pinion shaft supporting device for a vehicle having the double-row angular ball bearing. <P>SOLUTION: A plurality of balls 45 and 46 are disposed in two rows between two rows of raceway grooves formed in the outer peripheral surface of an inner ring 28 and two rows of raceway grooves formed in the inner peripheral surface of an outer ring 24. The balls 45 disposed between the raceway grooves facing each other on a lubricating oil flow-in side are held by a first cage 47, and the balls 46 disposed between the raceway grooves facing each other on the other side are held by a second cage 48. Each of the first and second cages 47 and 48 is so formed that two annular parts 50, 52, and 55 are connected to each other through a plurality of column parts 52 and 56. The column parts 52 and 56 of the second cages 47 and 48 are formed in a roughly linear shape and extended roughly parallel with the center axis of the inner ring 28. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a double row angular contact ball bearing, and more particularly to a double row angular contact ball bearing suitable for use as a bearing for supporting a pinion shaft of a differential gear device or a transaxle device. The present invention also relates to a pinion shaft support device for a vehicle such as a differential gear device, a transaxle device, and a transfer device.

  Conventionally, as a bearing for supporting a pinion shaft of a differential gear device, there is a double-row angular contact ball bearing described in Japanese Patent Laid-Open No. 2003-314541 (Patent Document 1).

  In this double row angular contact ball bearing, a plurality of balls are arranged in two rows between two rows of raceway grooves formed on the outer peripheral surface of the inner ring and two rows of raceway grooves formed on the inner peripheral surface of the outer ring. Has been placed. The balls arranged between the mutually facing track grooves are held by the first cage, and the balls arranged between the other track grooves facing each other are held by the second cage. Has been.

  The outer diameter of the raceway groove on the lubricating oil inflow side of the inner ring is smaller than the outer diameter of the other raceway groove of the inner ring, and the inner diameter of the raceway groove on the lubricating oil inflow side of the outer ring is smaller than that of the other raceway groove of the outer ring. It is smaller than the inner diameter. Each of the first and second cages has an inner diameter that increases as the inner diameter of the inner circumferential surface increases from the lubricating oil inflow side to the lubricating oil outflow side. Further, the radial gap between the one of the mutually facing raceway grooves and the balls is set to a value different from the radial gap between the other one of the mutually opposing raceway grooves and the balls.

  The conventional double-row angular contact ball bearing, by setting the radial gap between the one of the mutually facing raceway groove and the ball and the radial gap between the other mutually opposite raceway groove and the ball to different values, By appropriately adjusting the load ratio of the load on the one and the other opposing raceway grooves, the life of the inner and outer rings and balls is extended.

  However, in the conventional double row angular contact ball bearing, the inner diameter of the raceway groove on the lubricating oil inflow side of the outer ring is smaller than the inner diameter of the other raceway groove, and further, the first and second cages Since the inner diameter of the inner circumferential surface increases from the lubricating oil inflow side to the lubricating oil outflow side, the lubricating oil outflow side travels along the inner peripheral surface of the first and second cages and the inner peripheral surface of the outer ring. The amount of lubricating oil that moves to the cylinder increases, that is, the pump action of the double-row angular contact ball bearing that attempts to move the lubricating oil to the outflow side becomes very large, and lubrication that passes between the inner ring and the outer ring There is a problem that the amount of oil becomes large.

  Due to this, the amount of foreign matter such as wear powder flowing into the bearing together with the lubricating oil is increased, and the foreign matter is aggressive against the inner and outer rings, the first and second cages, and the ball. There is a problem that the life of the inner and outer rings, the first and second cages, and the balls is short.

Further, since the amount of lubricating oil passing between the inner ring and the outer ring is large, the stirring resistance of the lubricating oil is increased, the rotational torque of the double-row angular ball bearing is increased, and this double-row angular ball bearing is provided. There is a problem that the fuel consumption of automobiles and the like is high.
JP 2003-314541 A (FIG. 2)

  Accordingly, an object of the present invention is to provide a double row angular contact ball bearing having a long life and a small stirring resistance, and a vehicle pinion shaft support device including the double row angular contact ball bearing.

In order to solve the above problems, the double-row angular contact ball bearing of the present invention is
In a double row angular contact ball bearing having an outer ring, an inner ring, a ball and a cage, and a lubricating liquid flowing between one inner side and the other outer side in the axial direction between the inner ring and the outer ring,
The retainer has a shape that suppresses the flow of the lubricating liquid.

  In this specification, the double row means that the outer ring has two rows of raceway grooves on the inner peripheral surface, and the inner ring has two rows of raceway grooves on the outer peripheral surface. And

  According to the present invention, since the cage has a shape that suppresses the flow of the lubricating liquid, the flow of the lubricating liquid (lubricating oil, cleaning liquid, etc.) passing between the inner ring and the outer ring is reduced. The flow rate can be suppressed, and the lubricating liquid flowing into the bearing can be reduced. Therefore, since the amount of foreign matter such as wear powder entering the bearing together with the lubricating liquid can be suppressed, the aggressiveness of the foreign matter to the inner and outer rings, the cage and the ball can be reduced. For example, it is possible to mitigate damage to the inner and outer rings and balls due to the biting of foreign matter. Therefore, the lifetimes of the inner and outer rings and balls can be significantly increased, and the durability performance of the bearing can be improved.

  Further, according to the present invention, since the lubricating liquid flowing into the bearing can be reduced, the agitation resistance of the bearing can be reduced, and the rotational torque of the bearing can be reduced. Therefore, the fuel consumption of an automobile or the like equipped with the bearing of the present invention can be significantly reduced.

  In the double-row angular contact ball bearing of one embodiment, the cage has a column portion substantially parallel to the axial direction of the inner ring and the outer ring.

  According to the embodiment, the pillar portion of the cage has a substantially linear shape extending substantially parallel to the axial direction of the inner ring and the outer ring, and the inner diameter of the inner peripheral surface of the pillar portion of the cage is such that the lubricating liquid flows out. Since it does not become large as it goes to the side which carries out, the flow of the lubricating liquid which flows out of a bearing along the inner peripheral surface of the pillar part of the above-mentioned cage can be controlled. Therefore, the flow rate of the lubricating liquid flowing into the bearing (between the inner ring and the outer ring) can be suppressed, the durability of the bearing can be improved, and the rotational torque of the bearing can be reduced.

  Further, the double row angular contact ball bearing of one embodiment includes a first retainer in which the retainer retains the balls disposed between raceway grooves on the inflow side of the lubricating liquid of the outer ring and the inner ring, and the outer ring. And a second cage that holds a ball disposed between the other raceway groove of the inner ring, and the first cage suppresses the flow of the lubricating liquid to the end portion on the side into which the lubricating liquid flows. It has a flow suppression part.

  According to the embodiment, since the first retainer has the flow suppressing portion that suppresses the flow of the lubricating liquid at the end portion on the side where the lubricating liquid flows, the amount of the lubricating liquid flowing into the bearing Can be greatly suppressed. Therefore, the amount of foreign matter can be remarkably reduced, and the durability performance of the bearing can be remarkably improved. Further, since the amount of the lubricating liquid flowing into the bearing can be greatly suppressed, the rotational torque of the bearing can be significantly reduced.

  In the double row angular contact ball bearing of one embodiment, the inner diameter of the raceway groove on the inflow side of the lubricating liquid of the outer ring is smaller than the inner diameter of the other raceway groove of the outer ring. In this specification, the maximum inner diameter of the outer ring raceway groove is defined as the inner diameter of the outer ring raceway groove, and the minimum outer diameter of the inner ring raceway groove is defined as the outer diameter of the inner ring raceway groove.

  According to the above embodiment, the inner diameter of the raceway groove on the inflow side of the lubricating liquid of the outer ring is smaller than the inner diameter of the other raceway groove of the outer ring. The flow of the lubricating liquid flowing out is promoted, and the amount of the lubricating liquid flowing out from the bearing is increased. However, according to the above embodiment, since the cage has a shape that suppresses the flow of the lubricating liquid, the amount of the lubricating liquid flowing out from the bearing does not increase. As a result, the durability of the bearing can be greatly improved and the rotational torque of the bearing can be greatly reduced.

In addition, the vehicle pinion shaft support device of the present invention includes:
Case and
A differential mechanism provided in the case;
A pinion shaft having a pinion gear meshing with the ring gear of the differential mechanism;
The double-row angular contact ball bearing according to any one of claims 1 to 4, wherein the pinion shaft is rotatably supported.

  According to the present invention, since the double-row angular contact ball bearing of the present invention is adopted as a bearing that rotatably supports the pinion shaft, the life of the bearing that supports the pinion shaft can be significantly prolonged. .

  Further, according to the present invention, since the bearing that supports the pinion shaft is the double-row angular contact ball bearing of the present invention, the rotational torque of the bearing that supports the pinion shaft can be significantly reduced, and the vehicle pinion shaft of the present invention The fuel consumption of an automobile or the like equipped with a support device can be significantly reduced.

  According to the double row angular contact ball bearing of the present invention, since the cage has a shape that suppresses the flow of the lubricating liquid, the flow rate of the lubricating liquid flowing between the inner ring and the outer ring The lubricating liquid flowing into the bearing can be reduced. Accordingly, since the amount of foreign matter such as wear powder that enters the bearing together with the lubricating liquid can be suppressed, the aggressiveness of the foreign matter against the inner and outer rings, the cage, and the balls can be mitigated, and the life of the inner and outer rings and balls can be reduced. The length can be significantly increased, and the durability of the bearing can be improved.

  Further, according to the present invention, since the lubricating liquid flowing into the bearing can be reduced, the agitation resistance of the bearing can be reduced, and the rotational torque of the bearing can be reduced. Can be reduced.

  Hereinafter, the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view of a differential gear device according to an embodiment of the present invention that includes the double-row angular ball bearing of the first embodiment of the present invention.

  The differential gear device includes a pinion shaft 1, a differential mechanism 3, and a double-row angular contact ball bearing (hereinafter referred to as a first row angular contact ball bearing) according to a first embodiment of the present invention disposed on the outer periphery of the pinion shaft 1 on the differential mechanism 3 side. 1 and a double row angular contact ball bearing (hereinafter referred to as a second row angular contact ball bearing) of the first embodiment of the present invention disposed on the outer periphery of the pinion shaft 1 opposite to the differential mechanism 3 side. (Referred to as a double-row angular ball bearing) 6, a pinion shaft 1, a differential mechanism 3, and a case 8 housing the first and second double-row angular ball bearings 5 and 6.

  A pinion gear 2 is formed at one end of the pinion shaft 1 on the differential mechanism 3 side, and the pinion gear 2 meshes with a ring gear 11 of the differential mechanism 3. On the other hand, a flange joint 12 is arranged at the other end of the pinion shaft 1 so that a drive shaft (not shown) can be connected.

  The case 8 includes a main body portion 26 that defines an inner region of the differential gear device, and a substantially cylindrical annular portion that is connected to the inner peripheral surface of the main body portion 26 and is an inner portion disposed in the inner space of the main body portion 26. 27.

  The first double-row angular ball bearing 5 includes an inner ring 28, an outer ring 24 and a plurality of balls 30, and the second double-row angular ball bearing 6 includes an inner ring 29, an outer ring 25 and a plurality of balls 31. As shown in FIG. 1, the balls 30 are arranged in two rows in the axial direction of the inner ring 28 between the inner peripheral surface of the outer ring 24 and the outer peripheral surface of the inner ring 28. Two rows are arranged in the axial direction of the inner ring 29 between the inner circumferential surface and the outer circumferential surface of the inner ring 29.

  The inner circumferential surface of the inner ring 28 of the first double-row angular ball bearing 5 is fitted and fixed to the outer circumferential surface of the pinion shaft 1, while the outer circumferential surface of the outer ring 24 is fitted to the inner circumferential surface of the annular portion 27. It is fixed. The inner peripheral surface of the inner ring 29 of the second double-row angular ball bearing 6 is fitted and fixed to the pinion shaft 1, while the outer peripheral surface of the outer ring 25 is fitted and fixed to the inner peripheral surface of the main body 26. ing. The first and second double-row angular ball bearings 5 and 6 support the pinion shaft 1 rotatably at a predetermined position.

  In the above configuration, the differential gear device transmits the power of the drive shaft to the differential mechanism 3 via the pinion shaft 1 to drive the differential mechanism 3. And the rotational speed difference of the two wheel shafts (not shown) connected with each of the joints arranged on both sides of the differential mechanism 3 is appropriately adjusted.

  Further, this differential gear device splashes up the lubricating oil as the lubricating liquid stored at the level L when the operation is stopped, along with the rotation of the ring gear 11 during the operation, so that the lubricating oil lubricating path in the case 8 is obtained. 1, the pinion gear 2, the ring gear 11 of the differential mechanism 3, the side gear (not shown) of the differential mechanism 3, and the first gear are circulated in the order of arrows a, b, c, d and e in FIG. The double row angular ball bearing 5 and the second double row angular ball bearing 6 are circulated so as to pass through the plurality of gears and the first and second double row angular ball bearings 5 and 6 during operation. I try to prevent seizure.

  FIG. 2 is a cross-sectional view of a portion above the lubricating oil surface L of the first double-row angular ball bearing 5. In FIG. 2, an arrow d is an arrow indicated by d in FIG. 1, and is an arrow indicating a direction in which the lubricating oil flows. Although not described, the second double-row angular ball bearing 6 also has the same structure as the first double-row angular ball bearing 5.

  As shown in FIG. 2, the outer ring 24 of the first double-row angular ball bearing 5 has two rows of raceway grooves on the inner peripheral surface, and the inner ring 28 faces the raceway groove of the outer ring 24 on the outer peripheral surface. There are two rows of track grooves at the position.

  Further, the plurality of balls 30 are disposed between the raceway groove on the inner peripheral surface of the outer ring 27 on the side into which the lubricating oil flows and the raceway groove on the outer peripheral surface of the inner ring 28 on the side on which the lubricant oil flows. The first ball 45 includes a second ball 46 disposed between the other raceway groove of the outer ring 27 and the other raceway groove of the inner ring 28.

  The first ball 45 is held by a first holder 47, and the second ball 46 is held by a second holder 48. Specifically, the first retainer 47 is connected to the first annular portion 50, the second annular portion 51, and the first annular portion 50 and the second annular portion 51 at predetermined intervals in the circumferential direction. The second retainer 48 includes a first annular portion 54, a second annular portion 55, and a predetermined circumferential direction between the first annular portion 54 and the second annular portion 55. It has a plurality of pillar parts 56 connected for every interval. The first ball 45 is accommodated in a pocket formed between the column portions 52 adjacent in the circumferential direction, and the second ball 46 is formed between the column portions 56 adjacent in the circumferential direction. Housed in a pocket.

  As shown in FIG. 2, the inner diameter of the raceway groove on the inflow side of the lubricating oil of the outer ring 24 is smaller than the inner diameter of the other raceway groove of the outer ring 24. The outer diameter is smaller than the outer diameter of the other raceway groove of the inner ring 28.

  The column portions 52 and 56 of the first and second cages 47 and 48 have a substantially linear shape, and extend substantially parallel to the central axis of the inner ring 28 (the central axis of the outer ring 24). The second cages 47 and 48 have a shape that suppresses the flow of the lubricating oil.

  That is, the column portions 52 and 56 of the first and second cages 47 and 48 are substantially linear and extend substantially parallel to the central axis of the inner ring 28 (the central axis of the outer ring 24). Since the inner diameter of the inner peripheral surface of the pillar portion of the cage does not increase as the lubricating liquid flows out as in the conventional cage, the pillar portions 52 and 56 of the first and second cages 47 and 48 are not increased. The flow of the lubricating liquid flowing out of the bearing along the inner peripheral surface of the bearing can be suppressed.

  According to the double-row angular contact ball bearing of the first embodiment, the first and second cages 47 and 48 have a shape that suppresses the flow of the lubricating oil, and therefore between the inner ring 28 and the outer ring 24. The flow rate of the lubricating oil passing through the bearing can be suppressed, and the lubricating oil flowing into the bearing can be reduced. Accordingly, since the amount of foreign matter such as wear powder entering the bearing together with the lubricating oil can be suppressed, the aggressiveness of the foreign matter to the inner and outer rings 24, 28, the first and second cages 47, 48, and the ball 30 is reduced. it can. For example, damage to the inner and outer rings 24 and 28 and the ball 30 due to the biting of foreign matter can be alleviated. Therefore, the lifetimes of the inner and outer rings 24 and 28, the balls 30 and the like can be significantly increased, and the durability performance of the bearing can be improved.

  Further, according to the double-row angular contact ball bearing of the first embodiment, since the lubricating oil flowing into the bearing can be reduced, the stirring resistance of the bearing can be reduced, and the rotational torque of the bearing can be reduced. Therefore, the fuel consumption of an automobile or the like provided with the bearing of the first embodiment can be significantly reduced.

  Further, according to the double-row angular contact ball bearing of the first embodiment, the column portions 52 and 56 of the first and second cages 47 and 48 are in the axial direction of the inner ring 28 and the outer ring 24 (the central axis of the inner ring 28). Since the inner diameters of the inner peripheral surfaces of the column portions 52 and 56 of the first and second cages 47 and 48 do not increase toward the side from which the lubricating oil flows out, 1. The flow of the lubricating oil flowing out of the bearing along the inner peripheral surfaces of the column portions 52 and 56 of the second cages 47 and 48 can be suppressed. Therefore, the flow rate of the lubricating oil flowing into the bearing (between the inner ring 24 and the outer ring 28) can be suppressed, and the durability of the bearing can be improved and the rotational torque of the bearing can be reduced.

  Further, according to the double-row angular contact ball bearing of the first embodiment, the inner diameter of the raceway groove on the inflow side of the lubricating oil of the outer ring 24 is smaller than the inner diameter of the other raceway groove of the outer ring 24. The flow of the lubricating oil flowing out of the bearing along the inner peripheral surface 24 is promoted, and the amount of the lubricating liquid flowing out from the bearing increases. However, according to the first embodiment, since the first and second cages 47 and 48 have a shape that suppresses the flow of the lubricating oil, the amount of the lubricating oil flowing out from the bearing may increase. Absent. As a result, the durability of the bearing can be greatly improved and the rotational torque of the bearing can be greatly reduced.

  Further, according to the differential gear device of the above embodiment, the double-row angular ball bearings 5 and 6 of the present invention are adopted as bearings for rotatably supporting the pinion shaft 1, so that the bearing for supporting the pinion shaft 1 is adopted. The lifespan of can be greatly increased.

  Further, according to the differential gear device of the above embodiment, since the double-row angular ball bearings 5 and 6 of the present invention are provided, the fuel consumption of an automobile or the like provided with the differential gear device of the above embodiment can be significantly reduced. it can.

  In the double-row angular contact ball bearing of the first embodiment, the outer diameter of the raceway groove on the lubricating oil inflow side of the inner ring 28 is smaller than the outer diameter of the other raceway groove, Although the inner diameter of the inflow side raceway groove is smaller than the inner diameter of the other raceway groove, in this invention, the outer diameter of the inflow side raceway groove of the inner ring is the same as the outer diameter of the other raceway groove. The inner diameter of the raceway groove on the inflow side of the outer ring lubricating oil may be the same as or larger than the inner diameter of the other raceway groove.

  Further, in the double row angular contact ball bearing of the first embodiment, the column parts 52 and 56 of the first and second cages 47 and 48 are substantially linear and are substantially parallel to the central axis of the inner ring 28. However, only the column portion of one of the first cage and the second cage may be a straight line substantially parallel to the central axis of the inner ring.

  In the double-row angular contact ball bearing of the first embodiment, the column parts 52 and 56 of the first and second cages 47 and 48 are substantially linear and substantially parallel to the central axis of the inner ring 28. However, according to the present invention, the inner diameter of the inner peripheral surface may be reduced as the shape of at least one of the pillars of the first and second cages 47 moves in the direction in which the lubricant flows.

  In the above embodiment, the double-row angular contact ball bearings 5 and 6 of the first embodiment of the present invention are adopted as bearings for supporting the pinion shaft 1 of the differential gear device. However, the double-row angular contact ball bearing of the present invention is used. Of course, it may be adopted as a bearing for supporting the pinion shaft of the transaxle device.

  FIG. 3 is an axial sectional view of a double row angular contact ball bearing according to a second embodiment of the present invention.

  The double row angular contact ball bearing of the second embodiment is disposed on the pinion shaft of the differential gear device, similarly to the double row angular contact ball bearing of the first embodiment. The double-row angular contact ball bearing of the second embodiment is that the annular portion 61 on the lubricating oil inflow side of the first cage 57 is thicker in the radial direction only in the double-row angular contact bearing of the first embodiment. Different from ball bearings.

  In the double-row angular contact ball bearing of the second embodiment, the same reference numerals are given to the same components as those of the double-row angular contact ball bearing of the first embodiment, and the description thereof will be omitted. In the double row angular contact ball bearing of the second embodiment, the description of the operation and effect common to the double row angular contact ball bearing of the first embodiment is omitted, and the double row angular contact of the first embodiment is omitted. Only configurations, operational effects, and modifications different from the ball bearing will be described.

  As shown in FIG. 3, in the second embodiment, the radial thickness of the annular portion 61 on the lubricating oil inflow side of the first retainer 57 arranged on the lubricating oil inflow side is thick, The annular portion 61 on the lubricating oil inflow side of the first retainer 57 has a disk shape that closes the opening on the lubricating oil inflow side of the gap between the outer ring 24 and the inner ring 28. The disc-shaped annular part 61 of the first cage 57 constitutes a flow suppressing part.

  According to the double row angular contact ball bearing of the second embodiment, the annular portion 61 on the lubricating oil inflow side of the first retainer 57 closes the opening on the lubricating oil inflow side in the gap between the outer ring 24 and the inner ring 28. Since it has a disk shape, the amount of the lubricating oil flowing into the bearing can be greatly suppressed by the annular portion 61 on the inflow side of the lubricating oil. Therefore, the amount of foreign matter can be remarkably reduced, and the durability performance of the bearing can be remarkably improved. Further, since the amount of lubricating oil flowing into the bearing can be greatly suppressed, the rotational torque of the bearing can be significantly reduced.

  In the double-row angular contact ball bearing of the second embodiment, the annular portion 61 on the lubricating oil inflow side of the first retainer 57 blocks the opening on the lubricating oil inflow side in the gap between the outer ring 24 and the inner ring 28. On the other hand, the annular portion on the inflow side of the lubricating oil of the second cage 48 had a normal shape while being in a disc shape.

  However, in this invention, the annular portion on the inflow side of the lubricating oil of the first retainer has a disk shape that closes the opening on the inflow side of the lubricating oil in the gap between the outer ring and the inner ring, and the second retainer The annular portion on the inflow side of the lubricating oil may have a disk shape that blocks the gap between the outer ring and the inner ring similar to the annular portion on the inflow side of the lubricating oil of the first cage, An end portion on the outflow side of at least one of the first cage and the second cage may have a shape (for example, a disc shape) that blocks a gap between the outer ring and the inner ring. In these cases, the inflow of lubricating oil into the bearing can be further suppressed, the durability of the bearing can be further improved, and the rotational torque of the bearing can be further improved. In addition, although the said Example demonstrated the case where it applied to a double row angular ball bearing, the holder | retainer of this invention is applicable also to a single row ball bearing.

It is sectional drawing of the differential gear apparatus of one Embodiment of this invention provided with the double row angular contact ball bearing of 1st Embodiment of this invention. It is sectional drawing of the part above the lubricating oil surface L of the 1st double row angular contact ball bearing which the said differential gear apparatus has. It is sectional drawing of the axial direction of the double row angular contact ball bearing of 2nd Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Pinion shaft 2 Pinion gear 3 Actuation mechanism 5 1st double row angular contact ball bearing 6 2nd double row angular contact ball bearing 11 Ring gear 24,25 Outer ring 28,29 Inner ring 45 First ball 46 Second ball 47,57 First 1 cage 48 2nd cage 50, 51, 54, 55, 61 Annular part 52, 55 Column

Claims (5)

In the double-row angular contact ball bearing having an outer ring, an inner ring, a ball and a cage, and a lubricating liquid flows between one inner side and the other outer side in the axial direction between the inner ring and the outer ring
The retainer has a shape that suppresses the flow of the lubricating liquid, and a double-row angular contact ball bearing. In the double row angular contact ball bearing according to claim 1,
The retainer has a column portion substantially parallel to the axial direction of the inner ring and the outer ring, and a double-row angular contact ball bearing. In the double row angular contact ball bearing according to claim 1 or 2,
The retainer is disposed between a first retainer that holds the balls disposed between the raceway grooves on the inflow side of the lubricating liquid of the outer ring and the inner ring, and the other raceway groove of the outer ring and the inner ring. A second cage that holds the ball.
The double cage angular contact ball bearing, wherein the first retainer has a flow suppressing portion that suppresses the flow of the lubricating liquid at an end portion on a side into which the lubricating liquid flows. In the double row angular contact ball bearing according to any one of claims 1 to 3,
A double row angular contact ball bearing, wherein an inner diameter of a raceway groove on the inflow side of the lubricating liquid of the outer ring is smaller than an inner diameter of the other raceway groove of the outer ring. Case and
A differential mechanism provided in the case;
A pinion shaft having a pinion gear meshing with the ring gear of the differential mechanism;
A pinion shaft support device for a vehicle, comprising: the double row angular ball bearing according to any one of claims 1 to 4, wherein the pinion shaft rotatably supports the pinion shaft.

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