JP5403143B2 - Double row ball bearing and vehicle pinion shaft support device - Google Patents

Description

  The present invention relates to a double row ball bearing, and more particularly, to a double row ball bearing suitable for use in supporting a pinion shaft of a differential gear device, a transaxle device, or a transfer device.

  The present invention also relates to a vehicle pinion shaft support device having a vehicle pinion shaft, 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 JP-T-2002-523710 (Patent Document 1).

  This double row angular contact ball bearing has a plurality of first balls arranged between a first raceway groove formed on the outer peripheral surface of the inner ring and a first raceway groove formed on the inner peripheral surface of the outer ring, A plurality of second balls are arranged between the second raceway groove formed on the outer peripheral surface of the inner ring and the second raceway groove formed on the inner peripheral surface of the outer ring.

  In the double row angular contact ball bearing, the lubricating oil flows from one side in the axial direction toward the other side between the inner ring and the outer ring.

In the differential gear device having the above-described configuration, there is a demand for reducing the torque of the double row ball bearing to reduce the fuel consumption of a vehicle having the differential gear device.
Japanese translation of PCT publication No. 2002-523710 (FIG. 2)

  Accordingly, an object of the present invention is to provide a double-row ball bearing with a small torque and a vehicle pinion shaft support device with a low operating cost.

In order to solve the above problems, the double row ball bearing of the present invention is
An outer ring, an inner ring, a first ball and a second ball that are positioned at an interval in the axial direction, a first cage that holds the first ball, and a second ball that holds the second ball A double row ball bearing comprising a cage, wherein the lubricating liquid flows between the outer ring and the inner ring from one axial direction to the other axial direction;
The first retainer is located on the upstream side of the flow of the lubricating liquid from the second retainer,
The inner ring has a first raceway groove and a second raceway groove which is located on the downstream side of the lubricating liquid from the first raceway groove and has an outer diameter larger than the outer diameter of the first raceway groove. And
The first retainer has a liquid inflow suppressing portion that suppresses the lubricating liquid from flowing between the outer ring and the inner ring,
The second retainer has a liquid outflow promoting part that promotes the lubricating liquid to flow out from between the outer ring and the inner ring,
Each of the first cage and the second cage is
A first annular portion;
A second annular portion located downstream of the flow of the lubricating liquid from the first annular portion;
A third annular portion located downstream of the first annular portion in the flow of the lubricating liquid and radially inward of the second annular portion; and a radially outer side of the first annular portion. A plurality of first pillar portions connecting the end portion on one side and the second annular portion;
A plurality of second pillars connecting the radially inner end of the first annular part and the third annular part;
The radial dimension of the first annular part of the first retainer is the radial dimension of the second annular part of the first retainer and the radial direction of the third annular part of the first retainer. It is larger than the value added with the dimensions of
The second pillar portion of the second cage has an inner surface formed of a part of a conical surface whose inner diameter increases as going outward in the axial direction,
The liquid inflow suppressing portion includes an axially outer end surface of the first annular portion of the first retainer,
The liquid outflow promoting part includes the inner surface of the second pillar part of the second cage.

  According to the present invention, in the first retainer and the second retainer, the first retainer located on the upstream side of the flow of the lubricating liquid suppresses the lubricating liquid from flowing between the outer ring and the inner ring. Since the liquid inflow suppressing portion is provided, the liquid inflow suppressing portion can suppress the lubricating liquid from flowing into the bearing. Therefore, the amount of lubricating liquid inside the bearing can be reduced, the stirring resistance of the bearing can be reduced, and the torque can be reduced.

  Further, according to the present invention, in the first retainer and the second retainer, the second retainer located on the downstream side of the flow of the lubricating liquid prevents the lubricating liquid from flowing out between the outer ring and the inner ring. Since the liquid outflow facilitating portion is promoted, the liquid outflow facilitating portion can promote the outflow of the lubricating liquid to the outside of the bearing. Therefore, the amount of lubricating liquid inside the bearing can be reduced, the stirring resistance of the bearing can be reduced, and the torque can be reduced.

  Further, according to the present invention, the opening on the inflow side of the lubricating liquid between the outer ring and the inner ring is provided on the outer end surface in the axial direction of the first annular portion of the first retainer as the liquid inflow suppressing portion. A larger portion can be closed, and the inflow of the lubricating liquid into the bearing can be suppressed.

  According to the present invention, the flow of the lubricating liquid toward the center of the first ball can be blocked on the outer peripheral surface of the first pillar portion and the inner peripheral surface of the second pillar portion of the first cage. Thus, the stirring resistance caused by the first ball stirring the lubricating liquid can be significantly reduced.

  Moreover, according to this invention, the end surface by the side of the 1st holder | retainer of the axial direction of the 1st annular part of the said 2nd retainer, the outer peripheral surface of the 1st pillar part of the said 2nd retainer, and the said 2nd retainer With the inner peripheral surface of the second column portion of the vessel, the flow of the lubricating liquid toward the center of the second ball can be blocked, and the stirring resistance caused by the second ball stirring the lubricating liquid is markedly increased. Can be reduced.

  Further, according to the present invention, the lubricating liquid that has reached the conical surface can be obtained by the pumping effect of the inner surface formed of a part of the conical surface of the second column portion of the second retainer as the liquid outflow promoting portion. It can be smoothly discharged outward in the axial direction along this conical surface.

  Therefore, by reducing the amount of the lubricating liquid in the bearing by the synergistic effect of the plurality of functions and effects, the agitation resistance can be remarkably reduced and the torque can be remarkably reduced.

  In addition, according to the present invention, each cage does not have a component portion between the first column portion and the second column portion in the radial direction, so that the cage is remarkably compared with the conventional case. The weight can be reduced and the material cost of the cage can be reduced. Also, the rotational resistance of the bearing can be reduced because the cage is lightweight.

Moreover, the pinion shaft support device for a vehicle according to 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;
A double row ball bearing of the present invention that rotatably supports the pinion shaft is provided.

  According to the present invention, since the double row ball bearing of the present invention is provided, the torque of the double row ball bearing can be reduced. Therefore, the fuel consumption of the vehicle equipped with the present invention can be reduced.

  According to the double row ball bearing of the present invention, in the first cage and the second cage, the first cage located on the upstream side of the flow of the lubricating liquid has the liquid inflow suppressing portion. The liquid inflow suppressing portion can suppress the lubricating liquid from flowing into the bearing. Therefore, the amount of lubricating liquid inside the bearing can be reduced, the stirring resistance of the bearing can be reduced, and the torque can be reduced.

  Further, according to the double row ball bearing of the present invention, in the first cage and the second cage, the second cage located on the downstream side of the flow of the lubricating liquid has the liquid outflow promoting portion. In this liquid outflow promoting portion, the lubricating liquid can be promoted to flow out of the bearing. Therefore, the amount of lubricating liquid inside the bearing can be reduced, the stirring resistance of the bearing can be reduced, and the torque can be reduced.

  Moreover, according to the vehicle pinion shaft support device of the present invention, since the double row ball bearing of the present invention is provided, the torque of the double row ball bearing can be reduced, and the fuel consumption of the vehicle equipped with the present invention is reduced. can do.

  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.

  The differential gear device includes a pinion shaft 1, a differential mechanism 3, a first double-row angular ball bearing 5 as an example of a double-row ball bearing, and a second double-row angular bearing as an example of a double-row ball bearing. A ball bearing 6 and a case 8 are provided.

  The first double-row angular ball bearing 5 is arranged on the outer periphery of the pinion shaft 1 on the differential mechanism 3 side, while the second double-row angular ball bearing 6 is on the differential mechanism 3 side of the pinion shaft 1. It is arrange | positioned on the outer periphery on the opposite side. The case 8 houses the pinion shaft 1, the differential mechanism 3, and 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. The pinion gear 2 meshes with the 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 27. The annular portion 27 is continuous with the inner peripheral surface of the main body portion 26. The annular portion 27 is disposed in the internal space of the main body portion 26.

  The first double-row angular contact ball bearing 5 includes an inner ring 28, an outer ring 24, a plurality of first balls 30 and a plurality of second balls 31, and the second double-row angular ball bearing 6 includes an inner ring. 29, an outer ring 25, a plurality of first balls 33, and a plurality of second balls 32. As shown in FIG. 1, the plurality of first balls 30 and the plurality of second balls 31 are two 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. The plurality of first balls 33 and the plurality of second balls 32 are arranged in two rows in the axial direction of the inner ring 29 between the inner peripheral surface of the outer ring 25 and the outer peripheral surface of the inner ring 29. Yes.

  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.

  In the above configuration, the differential gear device is configured to drive the differential mechanism 3 by transmitting the power of the drive shaft to the differential mechanism 3 via the pinion shaft 1. And the rotational speed difference of the wheel shaft (not shown) connected with each of the coupling arrange | positioned at the side of the both sides of the said differential mechanism 3 is adjusted suitably.

  Further, the differential gear device splashes up the lubricating oil as the lubricating liquid stored at the level L along with the rotation of the ring gear 11 during operation, and passes through the lubricating oil lubricating path 37 in the case 8. 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 double-row angular ball bearing are circulated in the order of arrows a, b, c, d and e. 5 and the second double-row angular contact ball bearing 6 are circulated to prevent seizure of the plurality of gears and the first and second double-row angular contact ball bearings 5 and 6. .

  FIG. 2 is an enlarged sectional view of the first double-row angular contact ball bearing 5 in the axial direction.

  Although not described in detail, the second double row angular ball 6 has the same configuration as the first double row angular ball bearing 5. The description of the second double-row angular ball bearing 6 will be omitted with the first double-row angular ball bearing 5. In FIG. 2, arrows f and g indicate the direction of the lubricating oil flow.

  The first double-row angular ball bearing 5 includes an inner ring 28, an outer ring 24, a plurality of balls 30, a plurality of balls 31, an annular first retainer 40, and an annular second retainer 41.

  The inner ring 28 has an angular first raceway groove 50 and an angular second raceway groove 51 on the outer peripheral surface thereof. The first raceway groove 50 is located at an interval in the axial direction with respect to the second raceway groove 51. The outer diameter of the track bottom of the first track groove 50 is smaller than the outer diameter of the track bottom of the second track groove 51. On the outer peripheral surface of the inner ring 28, a portion located between the first raceway surface 50 and the second raceway surface 51 is a tapered surface. The outer diameter of the tapered surface increases in the axial direction from the first raceway groove 50 to the second raceway groove 51.

  The outer ring 24 has an angular first raceway groove 60 and an angular second raceway groove 61 on the inner peripheral surface thereof. The first track groove 60 is located at an axial distance from the second track groove 61. The inner diameter of the track bottom of the first track groove 60 is smaller than the inner diameter of the track bottom of the second track groove 61. On the inner peripheral surface of the outer ring 22, a portion located between the first raceway surface 60 and the second raceway surface 61 is a tapered surface. The inner diameter of the tapered surface increases in the axial direction from the first track groove 60 to the second track groove 61.

  The first cage 40 includes a first annular part 80, a second annular part 81, and a plurality of identical column parts 83. Each of the column parts 83 connects the first annular part 80 and the second annular part 81. The plurality of column parts 83 are arranged at intervals in the circumferential direction of the first annular part 80.

  The outer peripheral surfaces of the first and second annular portions 80 and 81 and the outer surfaces of the respective column portions 83 are located at a slight radial distance from the inner peripheral surface of the outer ring 24. Each of the outer peripheral surfaces of the first and second annular portions 80 and 81 and the outer surface of each column portion 83 has a shape corresponding to the shape of the inner peripheral surface of the outer ring 24.

  Further, the inner peripheral surfaces of the first and second annular portions 80 and 81 and the inner surfaces of the column portions 75 are positioned with a slight radial distance from the outer peripheral surface of the inner ring 28. Yes. Each of the inner peripheral surfaces of the first and second annular portions 80 and 81 and the inner surface of each column portion 75 has a shape corresponding to the shape of the outer peripheral surface of the inner ring 28.

  At each position in the axial direction, the radial thickness t of the first annular portion 80, the second annular portion 81 or each column portion 83 is equal to the inner peripheral surface of the outer ring 24 and the outer peripheral surface of the inner ring 28 at the axial position. And t ≧ 0.65 at the track portion and t ≧ 0.75δ at the shoulder portion.

  Thus, by increasing the thickness of the first retainer 40 on the inflow side of the lubricating oil and reducing the radial gap between the first retainer 40 and the race rings 24 and 28, the lubricating oil is reduced. The space that can exist is reduced to prevent the lubricating oil from flowing into the bearing, thereby reducing the stirring resistance of the lubricating oil.

  The end surface 70 of the first cage 40 on the inflow side of the lubricating oil, the outer peripheral surface 71 of the first annular portion 80, the outer surface 72 of each column portion 83, the outer peripheral surface 73 of the second annular portion 81, the first annular shape The inner peripheral surface 74 of the part 80, the inner surface 74 of each column part, and the inner peripheral surface 76 of the second annular part 81 constitute a liquid inflow suppressing part.

  The second cage 41 has a first annular portion 90, a second annular portion 91, and a plurality of identical column portions 93. Each of the pillar portions 93 connects the first annular portion 90 and the second annular portion 91. The plurality of column portions 93 are arranged at intervals in the circumferential direction of the first annular portion 90. In each of the column portions 93, the portion 97 positioned axially outward from the track bottom of the second raceway groove 51 of the inner ring 28 in the axial direction has a radial thickness as going outward in the axial direction. It is getting smaller.

  The radial thickness of the second annular portion 91 of the second cage 41 is smaller than the radial thickness of the first annular portion 80 of the first cage 40. The radial interval (gap) between the second annular portion 91 of the second cage 41 and the outer ring 24 is the radial interval (gap) between the first annular portion 80 of the first cage 40 and the outer ring 24. ) Is larger than. Further, the radial interval (gap) between the second annular portion 91 of the second cage 41 and the inner ring 28 is the radial interval between the first annular portion 80 of the first cage 40 and the inner ring 28. It is larger than (gap).

  The plurality of first balls 30 are spaced from each other in the circumferential direction while being held by the first cage 40 between the first raceway groove 50 of the inner ring 28 and the first raceway groove 60 of the outer ring 24. Is placed. The plurality of second balls 31 are held in the circumferential direction while being held by the second cage 41 between the second raceway groove 51 of the inner ring 28 and the second raceway groove 61 of the outer ring 24. They are spaced from each other. The pitch circle diameter formed by the centers of the plurality of first balls 30 is smaller than the pitch circle diameter formed by the centers of the plurality of second balls 31.

  In the outer peripheral surface and inner peripheral surface of the second annular portion 91 of the second retainer 41, and in each column portion 93, a portion 97 positioned axially outward from the track bottom of the second track groove 51 of the inner ring 28. The outer peripheral surface and the inner peripheral surface form a liquid outflow promoting portion.

  According to the first double-row angular contact ball bearing 5, the radial thickness of the first annular portion 80 of the first cage 40 is equal to the radial thickness of the second annular portion 91 of the second cage 41. Therefore, a larger portion of the opening on the inflow side of the lubricating oil between the outer ring 24 and the inner ring 28 on the outer end surface 70 in the axial direction of the first annular portion 80 of the first retainer 40. On the other hand, the lubricating oil in the bearing 5 is allowed to flow between the peripheral surface (the outer peripheral surface and the inner peripheral surface) of the second annular portion 91 of the second cage 31 and the race rings (the outer ring 24 and the inner ring 28). It is possible to efficiently flow out through the space. Therefore, the amount of the lubricating liquid inside the bearing 5 can be reduced, the stirring resistance of the bearing 5 can be reduced, and the torque can be reduced.

  Further, according to the first double-row angular contact ball bearing 5, the radial thickness t of the first annular portion 80, the second annular portion 81, or each column portion 83 is the axis thereof at each axial position. With respect to the radial distance δ between the inner circumferential surface of the outer ring 24 and the outer circumferential surface of the inner ring 28 at the position in the direction, t ≧ 0.6δ at the track portion and t ≧ 0.7575 at the shoulder (brim) portion. Since the first cage 40 occupies most of the region on the inflow side of the lubricant between the outer ring 24 and the inner ring 28, there is almost no space for the lubricant to enter the region on the inflow side. The amount of lubricating oil present in the bearing 5 can be remarkably reduced. Therefore, the stirring resistance of the lubricating oil can be remarkably reduced.

  Although the first and second double-row angular ball bearings 5 and 6 are employed as bearings for supporting the pinion shaft 1 of the differential gear device, the double-row angular ball bearing of the present invention is used as a transaxle device or a drainage device. You may use as a bearing which supports this pinion shaft.

  FIG. 3 is an enlarged cross-sectional view in the axial direction of a double row angular ball bearing 105 which is a double row ball bearing according to an embodiment of the present invention.

  The double-row angular ball bearing 105 of one embodiment is different from the angular ball bearing 5 only in the shape of the first cage 140 and the shape of the second cage 141.

  In the double-row angular ball bearing 105 of one embodiment, the same reference numerals are assigned to the same components as those of the first double-row angular ball bearing 5, and the description thereof will be omitted. In the double-row angular contact ball bearing 105 of one embodiment, the description of the operation and effect common to the first double-row angular contact ball bearing 5 is omitted, and the first double-row angular contact ball bearing 5 Only different configurations, operational effects, and modifications will be described.

  In the double-row angular contact ball bearing 105 of one embodiment, the first retainer 140 on the inflow side of the lubricating oil includes a first annular portion 150, a second annular portion 151, a third annular portion 152, and a plurality of first It has a pillar part 153 and a plurality of second pillar parts 154.

  The first annular part 150 is located upstream of the second annular part 151 and the third annular part 152 in the flow of the lubricating oil. The first annular portion 150 has a hollow disk shape and extends substantially in the radial direction of the inner ring 28. The second annular portion 151 is located radially outward from the third annular portion 152.

  The radial dimension of the first annular part 150 of the first cage 140 is the radial dimension of the second annular part 151 of the first cage 140 and the diameter of the third annular part 152 of the first cage 140. It is larger than the value obtained by adding the dimension in the direction.

  Each of the first pillar portions 153 connects the end portion in the radial direction of the first annular portion 150 and the second annular portion 151. As shown in FIG. 3, each first pillar portion 153 has a linear shape in the axial cross section. Each of the first pillar portions 153 has an outer surface 156 made of a part of a conical surface and an inner surface 157 made of a part of the conical surface. The outer diameter of the outer surface 156 increases uniformly as it goes downstream of the lubricating oil flow, and the inner diameter of the inner surface 157 increases uniformly as it goes downstream of the lubricating oil flow. The plurality of first pillar portions 153 are located at intervals in the circumferential direction of the first annular portion 150.

  Each of the second column portions 154 connects the end portion in the radial direction of the first annular portion 150 and the second annular portion 152. As shown in FIG. 3, each second pillar portion 154 has a linear shape in the axial cross section. Each of the second columnar portions 154 has an outer surface 166 that is a part of a conical surface and an inner surface 167 that is a part of the conical surface. The outer diameter of the outer surface 166 increases uniformly as it goes downstream of the flow of lubricating oil, and the inner diameter of the inner surface 167 increases uniformly as it goes downstream of the flow of lubricating oil. The plurality of first pillar portions 154 are located at intervals in the circumferential direction of the first annular portion 150.

  Similarly, the second retainer 141 on the lubricant outflow side includes a first annular portion 170, a second annular portion 171, a third annular portion 172, a plurality of first pillar portions 173, and a plurality of A second pillar portion 174.

  The first annular part 170 is located upstream of the second annular part 171 and the third annular part 172 in the flow of the lubricating oil. The first annular portion 170 has a hollow disk shape and extends substantially in the radial direction. The second annular portion 171 is located radially outward from the third annular portion 172.

  The radial dimension of the first annular part 170 of the second retainer 141 is the same as the radial dimension of the second annular part 171 of the first retainer 141 and the diameter of the third annular part 172 of the second retainer 141. It is larger than the value obtained by adding the dimension in the direction.

  Each of the first column portions 173 connects between the radial upper end of the first annular portion 170 and the second annular portion 171. As shown in FIG. 3, each first pillar portion 173 has a linear shape in the axial cross section. Each of the first pillar portions 173 has an outer surface 176 that is a part of a conical surface, and an inner surface 177 that is a part of the conical surface. The outer diameter of the outer surface 176 increases uniformly as it goes downstream of the flow of lubricating oil, and the inner diameter of the inner surface 177 increases uniformly as it goes downstream of the flow of lubricating oil. The plurality of first pillar portions 173 are located at intervals in the circumferential direction of the first annular portion 170.

  Each of the second pillar portions 174 connects the end portion of the first annular portion 170 in the radial direction and the second annular portion 172. As shown in FIG. 3, each second column portion 174 has a linear shape in the axial cross section. Each said 2nd pillar part 174 has the outer surface 186 which consists of a part of conical surface, and the inner surface 187 which consists of a part of conical surface. The outer diameter of the outer surface 186 increases uniformly as it goes downstream of the flow of lubricating oil, and the inner diameter of the inner surface 187 increases uniformly as it goes downstream of the flow of lubricating oil. The plurality of second pillar portions 174 are located at intervals in the circumferential direction of the first annular portion 170.

  As shown in FIG. 3, the radial position of the upper end of the first annular portion 170 of the second cage 141 and the radial position of the second annular portion 151 of the first cage 140 are: The radial position of the lower end portion of the first annular portion 170 of the second retainer 141 and the radial position of the third annular portion 152 of the first retainer 140 are substantially equal. ing. The first annular portion 170 of the second retainer 141 is positioned at an axial distance from each of the first and second annular portions 151 and 152 of the first retainer 140.

  FIG. 4 is a view showing the first annular portion 150 and the first ball 30 when the double-row angular ball bearing 105 is viewed from the upstream side of the lubricating oil in the axial direction of the first cage 140. 5 shows the second annular portion 151, the third annular portion 152, and the first ball 30 when the double row angular ball bearing 105 is viewed from the downstream side of the lubricating oil in the axial direction of the first cage 140. FIG.

  Although not described, the second retainer 141 also has the same structure as the first retainer 140 (the size, for example, the outer diameter and the inner diameter of the first, second, and third annular portions is the first retainer 140. And the second cage 141).

  As shown in FIGS. 4 and 5, the radial thickness of the first annular portion 150 is larger than the radial thickness of the second annular portion 151 and the radial thickness of the third annular portion 152. Is bigger than. The central axis of the second annular portion 151 substantially coincides with the central axis of the third annular portion 152.

  The outer end surface (upstream side) of the first annular portion 150 of the first retainer 140 in the axial direction constitutes a liquid inflow suppressing portion. Further, the outer surfaces 156, 176 of the first pillar portions 153, 173 and the inner surfaces 167, 187 of the second pillar portions 154, 174 constitute a liquid outflow promoting portion.

  In the double row angular contact ball bearing 105 of the above-described embodiment, as described above, in each of the first retainer 140 and the second retainer 141, the first column portions 153 and 173 are disposed on the downstream side from the upstream side in the axial direction. The outer surfaces 156 and 176 whose outer diameters are uniformly increased as they go to step (b). Further, in each of the first retainer 140 and the second retainer 141, the inner surfaces 167, 187 in which the inner diameters of the second pillar portions 154, 174 increase uniformly from the upstream side to the downstream side in the axial direction. have. Further, in each of the first retainer 140 and the second retainer 141, the first annular portions 150 and 170 are arranged at the upstream end in the axial direction with the first pillar portions 153 and 173 and the second pillar portion 154, respectively. , 174 and the radial direction are closed. Further, as shown in FIG. 3, the first pillar portion 153 of the first retainer 140 and the first pillar portion 173 of the second retainer 141 are located on substantially the same straight line in the axial section. The 2nd pillar part 154 of the 1st holder | retainer 140 and the 2nd pillar part 174 of the 2nd holder | retainer 141 are located on the substantially identical straight line.

  Therefore, the large flow of the lubricating oil can be limited to the following two flows by the plurality of configurations.

  That is, due to the centrifugal force of the first column parts 153 and 173, the lubricating oil is supplied between the first column parts 153 and 173 of the first and second cages 140 and 141 and the inner peripheral surface of the outer ring 24. As indicated by arrows h and i in FIG. 3, the fluid can flow along the inner peripheral surface of the outer ring 24. Further, due to the above-described plurality of configurations and the centrifugal force of the inner ring 28, the lubricating oil is supplied to the second pillar portions 154 and 174 of the first and second cages 140 and 141 as indicated by arrows j and k in FIG. It can be made to flow along the inner surface.

  Therefore, since the flow of the lubricating oil toward the center of the first ball 30 can be blocked in this way, the stirring resistance caused by the first ball 30 stirring the lubricating oil can be significantly reduced. . Similarly, since the flow of the lubricating oil toward the center of the second ball 31 can be blocked, the stirring resistance due to the second ball 31 stirring the lubricating oil can be significantly reduced.

  Further, according to the double-row angular contact ball bearing 105 of the above-described embodiment, the centrifugal force of the first column portions 153 and 173 and the inner ring 28, the inner peripheral surface of the outer ring 28, and the inner surfaces 167 and 187 of the second column portions. Due to the pumping action of the inner surface of the oil, the lubricating oil can be efficiently and smoothly discharged outward in the axial direction.

  Accordingly, the area of the outer end surface in the axial direction of the first annular portion 150 that is the liquid inflow suppressing portion is large, and the amount of lubricating liquid in the bearing can be reduced by the synergistic effect that the inflow of lubricating oil can be suppressed by this end surface. Can be remarkably reduced, the stirring resistance can be remarkably reduced, and the torque can be remarkably reduced.

  Further, according to the double-row angular ball bearing 105 of the above-described embodiment, the cages 140 and 141 are configured between the first column portions 153 and 173 and the second column portions 154 and 174 in the radial direction. Since there is no portion, the cages 140 and 141 can be remarkably reduced in weight and the material cost of the cages 140 and 141 can be reduced compared to the conventional case. Also, the rotational resistance of the bearing 105 can be reduced because the cages 140 and 141 are lightweight.

It is sectional drawing of a differential gear apparatus. It is an expanded sectional view of the axial direction of the 1st double row angular contact ball bearing. It is an expanded sectional view of the axial direction of the double row angular contact ball bearing which is a double row ball bearing of one embodiment of the present invention. In one Embodiment, it is a figure which shows a 1st annular part and a 1st ball | bowl when a double row angular contact ball bearing is seen from the upstream of the lubricating oil of the axial direction of a 1st holder | retainer. In one Embodiment, it is a figure which shows a 2nd annular part, a 3rd annular part, and a 1st ball when a double row angular contact ball bearing is seen from the downstream of the lubricating oil of the axial direction of a 1st holder | retainer.

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 Outer ring 28 Inner ring 30 1st ball 31 2nd ball 40,140 1st retainer 41 , 141 Second cage 50 First raceway groove of inner ring 51 Second raceway groove of inner ring 60 First raceway groove of outer ring 61 Second raceway groove of outer ring 80 First annular portion of first cage 81 First cage portion of first cage Second annular portion 83 First annular portion pillar portion 90 Second retainer first annular portion 91 Second retainer second annular portion 93 Second annular portion pillar portion 105 Double-row angular contact ball bearing 150 First retention First annular portion 151 of the cage first annular portion 151 of the first cage 152 third annular portion of the first cage 153 first pillar portion 154 of the first cage 154 second pillar portion 170 of the first cage 170 second holding portion First annular part 171 second annular of second cage Part 172 Third annular part of second cage 173 First pillar part of second cage 174 Second pillar part of second cage

Claims (2)

An outer ring, an inner ring, a first ball and a second ball that are positioned at an interval in the axial direction, a first cage that holds the first ball, and a second ball that holds the second ball A double row ball bearing comprising a cage, wherein the lubricating liquid flows between the outer ring and the inner ring from one axial direction to the other axial direction;
The first retainer is located on the upstream side of the flow of the lubricating liquid from the second retainer,
The inner ring has a first raceway groove and a second raceway groove which is located on the downstream side of the lubricating liquid from the first raceway groove and has an outer diameter larger than the outer diameter of the first raceway groove. And
The first retainer has a liquid inflow suppressing portion that suppresses the lubricating liquid from flowing between the outer ring and the inner ring,
The second retainer has a liquid outflow promoting part that promotes the lubricating liquid to flow out from between the outer ring and the inner ring,
Each of the first cage and the second cage is
A first annular portion;
A second annular portion located downstream of the flow of the lubricating liquid from the first annular portion;
A third annular portion located downstream of the first annular portion in the flow of the lubricating liquid and radially inward of the second annular portion; and a radially outer side of the first annular portion. A plurality of first pillar portions connecting the end portion on one side and the second annular portion;
A plurality of second pillars connecting the radially inner end of the first annular part and the third annular part;
The radial dimension of the first annular part of the first retainer is the radial dimension of the second annular part of the first retainer and the radial direction of the third annular part of the first retainer. It is larger than the value added with the dimensions of
The second pillar portion of the second cage has an inner surface formed of a part of a conical surface whose inner diameter increases as going outward in the axial direction,
The liquid inflow suppressing portion includes an axially outer end surface of the first annular portion of the first retainer,
The liquid outflow promoting portion includes the inner surface of the second pillar portion of the second retainer. 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 ball bearing according to claim 1, wherein the pinion shaft rotatably supports the pinion shaft.

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