JP2012132546A - Rolling bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inhibit the sealing performance and service life deterioration of a rolling bearing by changing the flowing direction of lubricating oil discharged between a rolling element and a sealing device of the rolling bearing to prevent the lubricating oil from splashing directly on the sealing device, and to promote the circulation of the lubricating oil by guiding the lubricating oil to an oil discharge hole.SOLUTION: The rolling bearing includes a second inner ring 34, an outer ring 36, the rolling element 62, a second cage 42, and the sealing device 38. The lubricating oil L is supplied from one axial side of the second inner ring 34, and the lubricating oil L is discharged from the oil discharge hole 36e formed closer to the other axial side than a second outer ring raceway 36b of the outer ring 36. Closer to one axial side than the sealing device 38, a shielding plate 48 is further provided between the second inner ring 34 and the outer ring 36. The shielding plate 48 is mounted at the end on the other axial side of a column part 46 of the second cage 42, and the shielding plate 48 is overlapped with the oil discharge hole 36e in the radial direction or located closer to the other axial side than the oil discharge hole 36e.

Description

  The present invention relates to a rolling bearing.

  Conventionally, a differential device and a transfer device are known as devices that transmit driving force from a rotational drive source such as an engine. As these devices, for example, Patent Document 1 discloses a technical disclosure of a transfer device installed in a drive path of a vehicle such as an automobile. As shown in FIG. 6, the basic configuration of the transfer device 110 is configured such that a ring gear 114 and a drive pinion 116 are engaged in a casing 112. The drive pinion 116 has a drive pinion shaft 116a integrally formed at an end thereof, and is rotatably supported by the casing 112 by a rolling bearing fitted and disposed on the drive pinion shaft 116a. Here, the rolling bearing that rotatably supports the drive pinion shaft 116a applies a tapered roller bearing from the viewpoint of high rigidity, or from the viewpoint of reducing the torque and reducing the size of the bearing in view of improving the fuel efficiency of the automobile. In addition, there is known one to which double-row angular ball bearings 130 arranged in double rows in the axial direction are applied.

  As shown in FIG. 6A, the double-row angular contact ball bearing 130 is configured by a pair of two inner rings 132 and 134 having an inner ring raceway. One outer ring 136 having two outer ring raceways is formed corresponding to both inner ring raceways of the pair of inner rings 132 and 134. Further, a plurality of rolling elements 160 and 162 are configured to be able to roll between the inner rings 132 and 134 and the outer ring 136. Moreover, the holder | retainer 140,142 holding this rolling element 160,162 is comprised. A sealing device 138 is defined between the inner ring 134 and the outer ring 136 arranged on the shaft end side of the drive pinion shaft 116a to define a space in which the rolling elements 162 are arranged and an outer space.

  Lubrication of the double-row angular ball bearing 130 configured in this way is not performed by enclosing grease in the bearing, but by the lubricating oil L that lubricates the inside of the casing 112. Here, the inner rings 132 and 134 are configured such that a small diameter shoulder portion having a smaller diameter portion than the inner ring raceway is disposed on the inner end portions facing each other, and the outer end portions on the opposite side to the both small diameter shoulder portions. On the side, a large-diameter shoulder having a larger diameter than the inner ring raceway is arranged and configured. Further, the outer ring 136 has a plurality of holes penetrating in the radial direction in the circumferential direction of the outer ring 136. As shown in FIG. 6B, the hole formed between the outer ring raceways has a lubricating oil supply hole 136d for supplying the lubricating oil L for lubricating the inside of the casing 112 into the bearing. It is configured as. Further, a hole formed between the sealing device 138 and the rolling element 162 is configured as an oil drain hole 136e. The inner circumferential surface of the casing 112 to which the outer ring 136 is fitted is formed with respective communication grooves 112a that allow the lubricating oil supply hole 136d and the oil discharge hole 136e to communicate with each other. The lubricating oil supply hole 136d, the drain oil hole 136e, and the communication groove 112a are combined to supply the lubricating oil L into the bearing to lubricate the bearing. Here, the lubricating oil L supplied into the bearing from the lubricating oil supply hole 136d through the communication groove 112a is rotated by the pumping action by the rotational force of the inner rings 132, 134 when the inner rings 132, 134 are rotated together with the rotation of the drive pinion 116. It is set as the structure which flows toward the large diameter shoulder part from the small diameter shoulder part 132,134.

JP 2006-009929 A

  Here, the lubricating oil L that has lubricated the bearing on the side where the ring gear 114 is configured returns to the lubricating oil chamber that stores the lubricating oil L configured on the ring gear 114 side. On the other hand, in the bearing on the side where the sealing device 138 is disposed, the discharged lubricating oil L tends to stay in the annular space between the rolling element 162 and the sealing device 138 and is difficult to circulate through the oil drain hole 136e. . Therefore, there is a problem that the lubricating oil L becomes sludge and becomes sludge and becomes sludge having deteriorated lubrication performance, which adheres to the sealing device 138 and impairs the sealing performance. Moreover, since the lubricating oil L discharged | emitted by the pumping effect | action applies directly to the sealing device 138, there exists a concern that sealing performance and lifetime may fall.

  Therefore, as a result of intensive studies, the inventor has focused on the direction in which the lubricating oil discharged into the annular space between the rolling element and the sealing device flows. That is, if the flow direction of the lubricating oil discharged into the annular space between the rolling element and the sealing device can be changed, the lubricating oil can be prevented from being applied directly to the sealing device, and the reduction in sealing performance and life can be suppressed. Also, by guiding the lubricating oil discharged to the annular space between the rolling element and the sealing device to the oil draining hole, circulation of the lubricating oil can be promoted to prevent stagnation and adhesion of sludge due to deterioration of the lubricating oil can be suppressed. .

  Thus, the present invention was devised in view of the above points, and the problem to be solved by the present invention is that the lubricating oil discharged between the rolling elements and the sealing device in the rolling bearing flows. By changing the direction, the lubricating oil is prevented from being directly applied to the sealing device, and the deterioration of the sealing performance and life is suppressed. Further, the lubricating oil is guided to the oil drain hole to promote the circulation of the lubricating oil.

In order to solve the above problems, the rolling bearing of the present invention takes the following means.
First, the first invention is formed on an inner ring raceway, a small diameter shoulder portion having a smaller diameter than the inner ring raceway formed on one side in the axial direction of the inner ring raceway, and on the other side in the axial direction of the inner ring raceway. In addition, an inner ring having a larger diameter shoulder than the inner ring raceway, an outer ring having an outer ring raceway, and a plurality of rolling elements disposed so as to be rollable between the inner ring raceway and the outer ring raceway. And an annular part disposed on one axial side of the plurality of rolling elements, and a plurality of pillar parts extending from the other axial side of the annular part and separating the plurality of rolling elements in the circumferential direction; A sealing device that is disposed between the outer ring and the large-diameter shoulder portion of the inner ring, and that defines a space in which the plurality of rolling elements are disposed and an external space, Lubricating oil is supplied from one side in the axial direction of the inner ring, and the shaft is more axial than the outer ring raceway of the outer ring. The lubricating oil is discharged from an oil drain hole formed on the other side, and a shield having an annular disc portion disposed between the inner ring and the outer ring on one axial side of the sealing device. The shield plate is further provided, and the shield plate is attached to an end on the other axial side of the pillar portion of the cage, and the shield plate overlaps the oil drain hole in the radial direction or is more axial than the oil drain hole. It is located in the other direction.

According to the first aspect of the present invention, the rolling bearing further includes a shielding plate having an annular disc portion disposed between the inner ring and the outer ring on one axial side of the sealing device. This shielding board is attached to the edge part of the axial direction other side of the pillar part of a holder | retainer. That is, the shielding plate is arranged and configured between the rolling elements and the sealing device. For this reason, the lubricating oil supplied from one side in the axial direction of the inner ring passes through the rolling elements and then hits the shielding plate. Therefore, it is possible to prevent the lubricating oil from being applied directly to the sealing device, and to suppress the reduction in sealing performance and life.
In addition, since the shielding plate is disposed on the oil drain hole in the radial direction or on the other axial side of the oil drain hole, the lubricating oil hitting the shield plate is guided to the oil drain hole. Therefore, the circulation of the lubricating oil can be promoted.

  Next, according to a second invention, in the first invention, the shielding plate has the annular disc portion and a plurality of protrusions extending from the annular disc portion to one axial side. The plurality of projecting portions are fixed to the column portion.

  According to the second invention, the shielding plate has an annular disc portion and a plurality of projecting portions extending from the annular disc portion to one side in the axial direction. The plurality of protrusions are configured to be fixed to the pillar portion of the cage. Therefore, the shielding plate can be fixed to the cage without complicating the shape.

  Next, according to a third invention, in the first or second invention, the sealing device is sealed by a seal lip portion that is fitted to the outer ring and is in sliding contact with the large-diameter shoulder portion of the inner ring. The surface on the other side in the axial direction of the annular disc portion of the shielding plate facing the seal lip portion of the sealing device in the axial direction is radially outward at a plurality of locations in the circumferential direction. And a fin portion that is continuously projected radially and is inclined to the rear in the rotational direction.

  According to the third aspect of the invention, the fin portion is formed on the surface on the other side in the axial direction of the annular disc portion of the shielding plate facing the seal lip portion of the sealing device in the axial direction. The fin portions are formed at a plurality of locations in the circumferential direction of the annular disk portion so as to project radially outwardly and incline backward in the rotational direction. Thereby, the lubricating oil around the seal lip portion is scraped up radially outward by the fin portion. Therefore, the accumulation of the lubricating oil around the seal lip portion can be further prevented, and the sludge adhesion due to the deterioration of the lubricating oil can be suppressed.

  By taking the measures of the above inventions, the present invention changes the flow direction of the lubricating oil discharged between the rolling elements in the rolling bearing and the sealing device, and prevents the lubricating oil from being applied directly to the sealing device. A decrease in performance and lifetime can be suppressed. Further, the lubricating oil can be guided to the oil drain hole to promote the circulation of the lubricating oil.

It is sectional drawing which shows an example of the transfer apparatus provided with the rolling bearing which concerns on Example 1. FIG. It is the fragmentary sectional view which expanded and showed the rolling bearing which concerns on Example 1. FIG. It is the fragmentary sectional view which expanded and showed the III section of FIG. It is the perspective view which showed the holder | retainer of the rolling bearing which concerns on Example 1 from the axial direction one side. It is the perspective view which showed the holder | retainer of the rolling bearing which concerns on Example 1 from the axial direction other side. It is sectional drawing which shows an example of the transfer apparatus provided with the conventional rolling bearing. FIG. 2A is a cross-sectional view showing an entire transfer device provided with a conventional rolling bearing. (B) The figure is an expanded sectional view which expanded B section in A figure.

  EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated using drawing.

A first embodiment of the present invention will be described with reference to FIGS.
The rolling bearing according to the first embodiment of the present invention will be described by exemplifying the configuration of the transfer device 10 to which a double-row angular ball bearing (rolling bearing) 30 is applied.
As shown in FIG. 1, the basic configuration of the transfer device 10 is configured such that a ring gear 14 and a drive pinion 16 mesh with each other in a casing 12. The drive pinion 16 has a drive pinion shaft 16a integrally formed at the end thereof, and is rotated to the casing 12 by a double-row angular ball bearing (rolling bearing) 30 fitted and disposed on the drive pinion shaft 16a. Supported as possible. Here, the double-row angular ball bearing (rolling bearing) 30 is applied from the viewpoint of reducing the torque and reducing the size of the bearing in view of improving the fuel efficiency of the automobile. The drive pinion 16 is engaged with the ring gear 14, and the drive pinion shaft 16a is connected to a propeller shaft (not shown) so that the driving force configured in the vehicle is transmitted.

  As shown in FIG. 2, the double-row angular ball bearing (rolling bearing) 30 is roughly configured as follows. First, a pair of first inner ring 32 and second inner ring 34 are configured. One outer ring 36 is formed corresponding to the first inner ring 32 and the second inner ring 34. In addition, a plurality of balls 60 and 62 (rolling elements) are arranged between the first inner ring 32, the second inner ring 34, and the outer ring 36 so as to be capable of rolling. Moreover, the 1st holder | retainer 40 and the 2nd holder | retainer 42 which hold | maintain these balls 60 and 62 (rolling body) are comprised. A sealing device 38 is defined between the second inner ring 34 disposed on the shaft end side of the drive pinion shaft 16a and the outer ring 36 to define a space in which the balls 62 (rolling elements) are disposed and an outer space. Has been.

First, the pair of first inner ring 32 and second inner ring 34 will be described.
As shown in FIG. 2, two pairs of a first inner ring 32 and a second inner ring 34 are formed in the axial direction on the outer peripheral surface of the drive pinion shaft 16a. Here, the first inner ring 32 is arranged on the side meshing with the ring gear 14, and the second inner ring 34 is arranged on the shaft end side of the drive pinion shaft 16 a. The first inner ring 32 has a first inner ring raceway 32a formed on the outer peripheral surface, a first small diameter shoulder portion 32b having a smaller diameter portion than the first inner ring raceway 32a, and a larger diameter than the first inner ring raceway 32a. 1st large diameter shoulder part 32c. Further, the second inner ring 34 has a second inner ring raceway 34a formed on the outer peripheral surface, a second small diameter shoulder portion 34b having a smaller diameter portion than the second inner ring raceway 34a, and a second inner ring raceway 34a. A large-diameter second large-diameter shoulder portion 34c. Here, the first inner ring 32 and the second inner ring 34 are disposed on the outer peripheral surface of the drive pinion shaft 16a so that the end surfaces of the first small-diameter shoulder portion 32b and the second small-diameter shoulder portion 34b abut against each other. They are mated together. The position where the end surfaces of the first small-diameter shoulder portion 32b and the second small-diameter shoulder portion 34b abut against each other corresponds to “one axial direction side” in the present invention. Also, the outer end side of the first small diameter shoulder portion 32b and the second small diameter shoulder portion 34b opposite to the small diameter shoulder portions is larger in diameter than the first inner ring raceway 32a and the second inner ring raceway 34a. A first large-diameter shoulder portion 32c and a second large-diameter shoulder portion 34c are arranged and configured. The positions of the first large-diameter shoulder portion 32c and the second large-diameter shoulder portion 34c correspond to “the other side in the axial direction” in the present invention.

Next, the outer ring 36 will be described.
As shown in FIG. 2, one outer ring 36 corresponding to the first inner ring 32 and the second inner ring 34 is configured in common. The outer ring 36 has two outer ring raceways, a first outer ring raceway 36a and a second outer ring raceway 36b. The first outer ring raceway 36a is formed on the side that meshes with the ring gear 14, and is a drive pinion shaft. A second outer ring raceway 36b is formed on the shaft end side of 16a. Further, a cylindrical portion 36c extending in the axial direction is formed on the shaft end side of the drive pinion shaft 16a further than the second outer ring raceway 36b.
The outer ring 36 has a plurality of holes penetrating in the radial direction in the circumferential direction of the outer ring 36. There are two types of holes, and the hole formed between the first outer ring raceway 36a and the second outer ring raceway 36b supplies lubricating oil L for lubricating the inside of the casing 12 in the double-row angular ball bearing (rolling bearing) 30. This is configured as a lubricating oil supply hole 36d to be supplied to. The hole formed in the cylindrical portion 36c is configured as an oil drain hole 36e. In the inner peripheral surface of the casing 12 to which the outer ring 36 is fitted, each communication groove 12a that connects the lubricating oil supply hole 36d and the drain oil hole 36e is formed. The lubricating oil supply hole 36d, the drainage hole 36e, and the communication groove 12a are combined to supply the lubricating oil L into the double row angular ball bearing (rolling bearing) 30 for lubrication.

Next, the balls 60 and 62 (rolling elements) will be described.
As shown in FIG. 2, a ball 60 is disposed between the first inner ring raceway 32 a of the first inner ring 32 and the first outer ring raceway 36 a of the outer ring 36 so as to be able to roll. A ball 62 is disposed between the second inner ring raceway 34 a of the second inner ring 34 and the second outer ring raceway 36 b of the outer ring 36 so as to be able to roll.

Next, the sealing device 38 will be described.
As shown in FIG. 3, the sealing device 38 includes a plurality of balls 62 (rolling elements) between the second inner ring 34 disposed on the shaft end side of the drive pinion shaft 16 a (see FIG. 2) and the outer ring 36. ) Is defined and an external space is defined to prevent leakage of the lubricating oil L in the bearing and prevent foreign matters from being mixed in. The sealing device 38 is integrally provided with a metal core 38a and a seal lip portion 38b. The metal core 38a is formed with an annular member having a substantially L-shaped cross section by stamping, plastic working or the like of a metal plate (steel plate or the like), and the outer peripheral surface of the annular member is a cylindrical portion of the outer ring 36. It is press-fitted and fixed to 36c. The seal lip 38b is formed in an annular shape by an elastic body (soft resin, rubber, etc.), and is integrally joined to the inner diameter side end of the cored bar 38a. Thereby, the seal lip portion 38b of the sealing device 38 slides on the outer peripheral surface of the second large-diameter shoulder portion 34c of the second inner ring 34 with respect to the rotation of the second inner ring 34 fixed to the drive pinion shaft 16a. Are configured to be in contact with each other and sealed.
The outline of the sealing device 38 is a cross section in which the second inner ring 34 fixed to the drive pinion shaft 16a slides and contacts the outer peripheral surface of the second large-diameter shoulder 34c of the second inner ring 34 with respect to the rotation. A slope having a substantially triangular seal lip portion 38b and having a so-called pumping action for returning the lubricating oil L which is about to leak from the sliding contact portion to the outer peripheral surfaces of the seal lip portion 38b and the second large diameter shoulder portion 34c into the bearing. An oil seal having ribs (not shown).
The seal lip portion 38b is provided with inclined ribs (not shown) that are inclined with respect to the central axis at a plurality of locations around the atmosphere-side seal lip slope 38c. This inclined rib (not shown in the figure) is formed by the lubricating oil L existing in the annular space 39 between the ball 62 and the sealing device 38 from the sliding contact portion with the second large diameter shoulder 34c of the rotating second inner ring 34 from the atmosphere. In the case of leaking to the side, it functions to return the leaked lubricating oil L to the annular space 39 side with the rotation of the second large-diameter shoulder 34c of the second inner ring 34. At this time, the returned lubricating oil L is pumped by the centrifugal force of the second large-diameter shoulder 34c of the rotating second inner ring 34 in a state along the side wall surface on one side of each inclined rib (not shown). Is guided to the annular space 39 side. This pumping action is determined by the number of inclined ribs, the protruding dimensions of the inclined ribs, the inclination angle with respect to the central axis of the inclined ribs, and the like.
In FIG. 3, the illustration of the sealing lip portion 38b having a substantially triangular cross section before the sealing device 38 is omitted is omitted, and the mounting state of the sealing device 38, that is, the sealing lip portion 38b is the second large-diameter shoulder. The state which slidably contacted with the outer peripheral surface of the part 34c, was elastically deformed, and was crushed is shown.
Further, as shown in FIG. 2, a stepped tightening nut 18 for fixing the first inner ring 32 and the second inner ring 34 is fastened to the shaft end of the drive pinion shaft 16a. An annularly formed slinger 20 is fitted into the outer shape of the small diameter portion 18a of the stepped tightening nut 18. The surface of the slinger 20 is in sliding contact with the sealing member 38. Further, the outer end portion of the slinger 20 is disposed opposite to the end portion of the cylindrical portion 36c of the outer ring 36 with a slight gap to form a labyrinth seal.

Next, the 1st holder | retainer 40 and the 2nd holder | retainer 42 are demonstrated.
As shown in FIG. 2, the balls 60 disposed between the first inner ring raceway 32 a of the first inner ring 32 and the first outer ring raceway 36 a of the outer ring 36 are held in a rollable manner. This is a cage 40 (the side meshing with the ring gear 14). The second retainer 42 holds the balls 62 disposed between the second inner ring raceway 34a of the second inner ring 34 and the second outer ring raceway 36b of the outer ring 36 in a rollable manner (drive). The shaft end side of the pinion shaft 16a). In addition, both the 1st holder | retainer 40 and the 2nd holder | retainer 42 are common about the structure which hold | maintains the balls 60 and 62 so that rolling is possible. Therefore, a common configuration will be described with the same reference numeral. The first retainer 40 and the second retainer 42 are made of synthetic resin and are formed by injection molding. As shown in FIGS. 2, 4, and 5, the first retainer 40 and the second retainer 42 are of a single-sided support that supports the bearing from only one direction in the axial direction of the bearing. The first retainer 40 and the second retainer 42 are generally configured to hold the balls 60 and 62 by supporting the balls 60 and 62 from the circumferential direction by the annular portion 44 and the column portion 46.
The annular portion 44 is disposed on the first small-diameter shoulder portion 32b and the second small-diameter shoulder portion 34b side (on the one side in the axial direction) with respect to the plurality of balls 60 and 62, and faces the plurality of balls 60 and 62 from the circumferential direction. It is configured to support. Further, the plurality of column portions 46 are arranged so that the first large-diameter shoulder portion 32c and the second large-diameter shoulder portion 34c are disposed on the side of the annular portion 44 (on the other side in the axial direction). It extends toward the first large-diameter shoulder portion 32c and the second large-diameter shoulder portion 34c, separates the balls 60 and 62 in the circumferential direction, and is supported by the surface from the circumferential direction.

As shown in FIGS. 4 and 5, the second retainer 42 further changes the flow direction of the lubricating oil L discharged into the annular space 39 between the ball 62 and the sealing device 38 to change the lubricating oil L. Is directly applied to the sealing device 38, and a shielding plate 48 for guiding the lubricating oil L to the oil drain hole 36e is formed. The shielding plate 48 is made of the same synthetic resin as the second cage 42 and is formed integrally with the second cage 42. The shielding plate 48 is an annular disc portion 49 that can be disposed between the second inner ring 34 and the outer race 36 (see FIG. 2), and extends from the annular disc portion 49 toward the annular portion 44. The plurality of protruding portions 50 are integrally fixed to the plurality of column portions 46 of the second retainer 42. Here, as illustrated in FIG. 3, the disc portion 49 and the protruding portion 50 of the shielding plate 48 are as follows when the second retainer 42 is mounted between the second inner ring 34 and the outer ring 36. Such an arrangement positional relationship is obtained. The disc portion 49 is between the ball 62 and the sealing device 38, that is, on the second small diameter shoulder 34 b side (one axial direction side) of the second inner ring 34 with respect to the sealing device 38, and is second from the ball 62. It is arranged and configured on the large diameter shoulder 34c side (the other side in the axial direction). When this arrangement position is seen in relation to the outer ring 36, the disc portion 49 of the shielding plate 48 overlaps the oil drain hole 36e in the radial direction or is closer to the second large diameter shoulder 34c side than the oil drain hole 36e ( (The other side in the axial direction). Further, the protruding portion 50 extends from the disc portion 49 to the second small diameter shoulder portion 34 b side (one axial direction side) of the second inner ring 34.
Further, as shown in FIG. 5, the disk portion 49 is radially continuous outwardly in a plurality of locations in the circumferential direction on the surface opposite to the surface on which the protruding portion 50 is formed. The fin portion 52 is formed so as to protrude in the radial direction of the outer diameter and to be inclined rearward in the rotational direction of the second cage 42.
As shown in FIG. 3, when the second retainer 42 is mounted between the second inner ring 34 and the outer ring 36, the fin portion 52 of the shielding plate 48 is formed on the seal lip 38 b of the sealing device 38. The position of the second inner ring 34 is opposed to the second large-diameter shoulder 34c and the portion that slides in the axial direction.

Lubrication of the double-row angular ball bearing (rolling bearing) 30 configured in this way is performed not by enclosing grease in the bearing but by lubricating oil L that lubricates the inside of the casing 12. As shown in FIGS. 2 and 3, the lubricating oil L is supplied from the lubricating oil supply hole 36 d through the communication groove 12 a to the first small diameter shoulder portion 32 b of the first inner ring 32 and the second inner ring 34. 2 is supplied to the position of the small diameter shoulder 34b. When the first inner ring 32 and the second inner ring 34 are rotated along with the rotation of the drive pinion 16, the large diameter shoulders 32b, 34b of the inner rings 32, 34 are pumped by the rotational force of the inner rings 32, 34. It is set as the structure which flows toward the parts 32c and 34c.
Here, the lubricating oil L discharged into the annular space 39 between the ball 62 and the sealing device 38 hits the shielding plate 48 formed in the second cage 42 and changes the direction of flowing radially outward. Therefore, the oil is introduced into the oil drain hole 36e arranged on the radially outer side of the valve 48.
Further, both the first cage 40 and the second cage 42 of the double row angular ball bearing (rolling bearing) 30 rotate around the drive pinion shaft 16 a as the balls 60 and 62 roll. Therefore, the shielding plate 48 integrally formed with the second cage 42 also rotates. When the second retainer 42 is mounted between the second inner ring 34 and the outer ring 36, the fin portion 52 of the shielding plate 48 slides with the second inner ring 34 of the seal lip 38 b of the sealing device 38. The fin portion 52 is formed to be inclined rearward in the rotation direction of the second cage 42. Therefore, the lubricating oil L is scraped up radially outward by the fin portion 52.

  According to the rolling bearing having such a configuration, the double-row angular ball bearing (rolling bearing) 30 is closer to the second small diameter shoulder portion 34b side (one axial direction side) of the second inner ring 34 than the sealing device 38. A shielding plate 48 having an annular disc portion 49 disposed between the inner ring 34 and the outer ring 36 is further provided. The shielding plate 48 is attached to an end portion of the column portion 46 of the second cage 42 on the side where the second large-diameter shoulder portion 34c is disposed (the other side in the axial direction). That is, the shielding plate 48 is arranged between the ball 62 and the sealing device 38. Therefore, the lubricating oil L supplied from the second small-diameter shoulder portion 34 b side (one axial side) of the second inner ring 34 passes through the balls 62 and then hits the shielding plate 48. Therefore, it is possible to prevent the lubricating oil L from being applied directly to the sealing device 38, and to suppress a decrease in sealing performance and life. Further, the shielding plate 48 is disposed at a position that overlaps the oil drain hole 36e in the radial direction or is located on the second large diameter shoulder 34c side (the other side in the axial direction) from the oil drain hole 36e, that is, on the sealing device 38. Therefore, since the lubricating oil L that hits the shielding plate 48 is guided to the oil drain hole 36e, the circulation of the lubricating oil L can be promoted.

  Further, the shielding plate 48 includes an annular disc portion 49 and a plurality of protrusions 50 extending from the annular disc portion 49 to the second small diameter shoulder portion 34b side (one axial direction side). The plurality of projecting portions 50 are configured to be fixed to the column portion 46 of the second retainer 42. Therefore, the shielding plate 48 can be fixed to the second holder 42 without complicating the shape.

  Further, the disc portion 49 of the shielding plate 48 facing the seal lip portion 38b of the sealing device 38 in the axial direction has a fin portion 52 on the surface opposite to the surface on which the protruding portion 50 is formed. The fin portion 52 is formed at a plurality of locations in the circumferential direction of the annular disc portion 49 so as to project radially outwardly and incline backward in the rotational direction. Thereby, the lubricating oil L around the seal lip portion 38 b is scraped up radially outward by the fin portion 52. Therefore, the accumulation of the lubricating oil L around the seal lip portion 38b can be further prevented, and sludge adhesion due to the deterioration of the lubricating oil L can be suppressed.

As mentioned above, although embodiment of this invention was described in Example 1, the rolling bearing of this invention is not limited to this Embodiment, It can implement with other various forms.
For example, in the rolling bearing in the first embodiment described above, the disk portion 49 and the protruding portion 50 of the shielding plate 48 are configured to be integrally formed with the second cage 42. However, it is not limited to this, The disc part of a shielding board may be comprised separately from a holder | retainer, and the structure attached to the pillar part of a holder | retainer may be sufficient.

Moreover, although what showed the fin part 52 in the disc part 49 of the shielding board 48 was shown, this fin part 52 may not be comprised.
Moreover, although the double row angular contact ball bearing (rolling bearing) 30 was demonstrated as a rolling bearing in Example 1, a tapered roller bearing may be sufficient as an aspect of a rolling bearing.

The double-row angular ball bearing (rolling bearing) 30 in the first embodiment has been described as one outer ring 36 corresponding to the first inner ring 32 and the second inner ring 34 in common, but without being limited thereto, The inner ring may correspond to the outer ring. In this case, the drive pinion may be rotatably supported in a state of being spaced apart from the configuration in which the inner ring is in contact with the inner ring.
In addition, the lubricating oil supply path has been described with respect to the casing 12 having the communication groove 12a. However, the lubricating oil supply path is not limited to this, and various known examples can be applied. The lubricating oil is supplied to the small-diameter shoulder portion (one axial side) of the inner ring, and the lubricating oil is directed from the small-diameter shoulder portion (one axial direction) of the inner ring toward the large-diameter shoulder portion (the other axial direction). Requires a flowing configuration.

DESCRIPTION OF SYMBOLS 10 Transfer apparatus 12 Casing 12a Communication groove 14 Ring gear 16 Drive pinion 16a Drive pinion shaft 18 Stepped tightening nut 18a Small diameter part 20 Slinger 30 Double row angular contact ball bearing (rolling bearing)
32 1st inner ring 32a 1st inner ring track 32b 1st small diameter shoulder part 32c 1st large diameter shoulder part 34 2nd inner ring 34a 2nd inner ring track 34b 2nd small diameter shoulder part 34c 2nd large diameter shoulder part 36 Outer ring 36a 1st outer ring Track 36b Second outer ring raceway 36c Cylindrical portion 36d Lubricating oil supply hole 36e Oil drain hole 38 Sealing device 38a Core metal 38b Seal lip portion 38c Atmospheric side seal lip portion 39 Annular space 40 First cage 42 Second cage 44 Annular portion 46 Pillar part 48 Shielding plate 49 Disc part 50 Projection part 52 Fin part 60 Ball (rolling element)
62 balls (rolling elements)
L Lubricating oil

Claims (3)

An inner ring raceway, a small diameter shoulder portion having a smaller diameter than the inner ring raceway formed on one axial side of the inner ring raceway, and a larger diameter than the inner ring raceway formed on the other axial side of the inner ring raceway. An inner ring having a large-diameter shoulder,
An outer ring having an outer ring raceway;
A plurality of rolling elements arranged to be rollable between the inner ring raceway and the outer ring raceway;
An annular part disposed on one axial side of the plurality of rolling elements, and a plurality of pillar parts extending from the other axial side of the annular part and separating the plurality of rolling elements in the circumferential direction, A cage having;
A sealing device disposed between the outer ring and the large-diameter shoulder portion of the inner ring, and defining a space in which the plurality of rolling elements are disposed and an external space;
With
Lubricating oil is supplied from one axial side of the inner ring, and the lubricating oil is discharged from an oil drain hole formed on the other axial side of the outer ring raceway of the outer ring,
On one side in the axial direction from the sealing device,
A shielding plate having an annular disc portion disposed between the inner ring and the outer ring;
The shield plate is attached to an end portion on the other side in the axial direction of the pillar portion of the cage,
The rolling bearing according to claim 1, wherein the shielding plate overlaps the oil drain hole in the radial direction or is positioned on the other axial side of the oil drain hole. The rolling bearing according to claim 1,
The shielding plate has the annular disc portion and a plurality of projecting portions extending from the annular disc portion to one axial side, and the plurality of projecting portions are fixed to the column portion. A rolling bearing characterized by that. The rolling bearing according to claim 1 or 2,
The sealing device is configured to be sealed by a seal lip portion that is fitted to the outer ring and is in sliding contact with the large-diameter shoulder portion of the inner ring,
The surface on the other side in the axial direction of the annular disk portion of the shielding plate facing the seal lip portion of the sealing device in the axial direction is radially continuous outward at a plurality of locations in the circumferential direction. A rolling bearing characterized in that it is provided with a fin portion that protrudes and tilts backward in the rotational direction.

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