JP2006064056A - Bearing lubricating structure for differential device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve reliability of a first drive pinion bearing by positively feeding lubricating oil into the first drive pinion bearing with a simple structure in a bearing lubricating structure for a differential device for lubricating first and second drive pinion bearings. <P>SOLUTION: In the bearing lubricating structure for the differential device, the lubricating oil splashed up by rotation of a ring gear 21 is guided to the first and second drive pinion bearings 10 and 11 through a lubricating oil supply passage 51, and is returned to the ring gear 21 side through a return passage 53, and thus, the first and the second drive pinion bearings 10 and 11 are lubricated. A lubricating oil guide member 54 having a tilt surface 54a tilted to the axial direction is provided in a differential carrier 5 so that the flowing direction of the lubricating oil turning together with a drive pinion shaft 13 caused by rotation of the drive pinion shaft 13 between the first drive pinion bearing 10 and the second drive pinion bearing 11 is shifted to the first drive pinion bearing 10 side. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a bearing lubrication structure for a differential device that lubricates a bearing that supports a pinion shaft of a differential device on a differential carrier.

  Conventionally, a diff carrier, a pinion shaft having an input portion coupled to the propulsion shaft and a pinion gear for transmitting power, and the diff carrier are arranged in parallel from the propulsion shaft side, and the pinion shaft is connected to the diff carrier. And a ring gear meshed with the pinion gear, and the lubricating oil splashed upward by the rotation of the ring gear. A bearing lubrication structure for a differential device is known in which the first and second bearings are lubricated by guiding the first and second bearings to the first and second bearings via the supply path and then returning to the ring gear side via the return path. . Here, since the first bearing mainly receives the reaction force at the time of backward movement with a small usage ratio, the bearing has a smaller diameter than the second bearing that mainly receives the reaction force at the time of forward movement with a large usage ratio, and is compact. It is configured.

For example, in the bearing lubrication structure for a differential device disclosed in Patent Document 1, an oil seal is provided on the outer periphery of the pinion shaft, the lubricating oil is divided into a first bearing and a second bearing, and a predetermined oil is provided on the first bearing side. The surface level is secured.
Japanese Patent Laid-Open No. 8-326877

  However, the pinion shaft of the differential device is mounted on the first bearing side upward in the vehicle direction, the first bearing is located at a higher position than the second bearing, and the first bearing extends from the ring gear to the second gear. Therefore, the supply of lubricating oil to the first bearing is a severe environment, and according to the observation results of the inventors with the ring gear rotating at a relatively high speed, the first bearing and the first bearing Even if the lubricating oil is sufficiently supplied from the ring gear between the two bearings and the oil level is such that both bearings are immersed, the amount of lubricating oil passing through the first bearing passes through the second bearing. It was found that the amount was significantly less than the amount of lubricating oil. That is, most of the lubricating oil supplied between the first bearing and the second bearing passes through the second bearing having a large diameter, and the amount passing through the first bearing having a small diameter is small and sufficient. Instead, improvements are desirable in terms of wear or seizure. On the other hand, it has been found that the lubricating oil supplied between the first bearing and the second bearing has a strong flow around the pinion shaft.

  The present invention has been made in view of such points, and an object of the present invention is to positively utilize the flow of the lubricating oil that rotates with the pinion shaft with a simple configuration. On the other hand, by increasing the amount of lubricating oil passing through the first bearing, the reliability of the first bearing, such as wear resistance and seizure resistance, is improved.

  In order to achieve the above object, according to the present invention, a lubricating oil guide member is provided in the diff carrier to change the direction of the lubricating oil flow around the pinion shaft generated by the rotation of the pinion shaft to the first bearing side. .

  Specifically, in the first invention, a diff carrier, a pinion shaft having an input portion to which power is input at one end and a pinion gear for transmitting power to the other end, and the diff carrier from the one end side. A small-diameter first bearing that supports the pinion shaft on a diff carrier, a second bearing that is larger in diameter than the first bearing, and a ring gear meshed with the pinion gear. The lubricating oil splashed upward by the rotation of the ring gear is guided to the first and second bearings through the supply path extending between the first bearing and the second bearing, and the ring gear side through the return path. The bearing lubrication structure for a differential device that lubricates the first and second bearings by reverting to the above is intended.

  In the diff carrier, an axial direction for changing the direction of the flow of the lubricating oil accompanying the pinion shaft generated by the rotation of the pinion shaft between the first and second bearings to the first bearing side. A lubricating oil guide member having a surface inclined with respect to the projection is projected.

  In the above configuration, when power is input to one end of the pinion shaft, the ring gear is rotated by the pinion gear at the other end, and the lubricating oil in the diff carrier is splashed upward. The lubricating oil passes through a supply path extending between the first bearing and the second bearing, and is then guided to the first and second bearings. At this time, since the first bearing has a smaller diameter than the second bearing, the clearance in the bearing is small, and the lubricating oil does not flow sufficiently to the return side through the bearing. However, according to the present invention, the lubricating oil flowing so as to rotate around the pinion shaft by the rotation of the pinion shaft between the first and second bearings is caused by the lubricating oil guiding member provided in the diff carrier. The direction of the flow is forcibly changed so as to flow along a surface inclined with respect to the direction, and the first bearing is lubricated by flowing toward the first bearing. And the lubricating oil which lubricated the 1st bearing returns to the ring gear side through a return path.

  In the second invention, the rotation of the pinion shaft is the rotation when the vehicle moves forward.

  That is, the lubricating oil flow of the first bearing is forcibly sent to the first bearing by using the rotational force of the pinion shaft when the vehicle travels longer than when the vehicle is traveling backward. The amount can be increased to improve the reliability of the first bearing.

  In a third aspect of the invention, the lubricating oil guide member is provided on the side from the lower side to the upper side where the flow of lubricating oil generated by the rotation of the pinion shaft and accompanying the pinion shaft is generated.

  That is, if the lubricating oil flow around the pinion shaft generated by the rotation of the pinion shaft is provided on the side from the upper side to the lower side, the direction of the lubricating oil flow around the pinion shaft Because the direction of gravity and the direction of gravity are almost the same direction, even if the direction of flow is changed by the lubricating oil guiding member, the lubricating oil tends to flow down early due to the resultant force of gravity and the rotational force of the pinion shaft. Therefore, it is difficult to smoothly flow into the first bearing side. However, according to the above configuration, the lubricating oil whose direction of flow is changed from the lower side to the upper side by the lubricating oil guiding member on the side from the lower side to the upper side of the lubricating oil that moves around the pinion shaft is It flows smoothly toward the bearing side. Therefore, the lubricating oil that rotates with the pinion shaft by the rotation of the pinion shaft is forcibly fed to the first bearing side by effectively using the rotational force and gravity of the pinion shaft.

  In the fourth invention, the lubricating oil guide member is provided at substantially the same position as the pinion shaft in a side view and protrudes toward the pinion shaft.

  According to the above configuration, since the core of the diff carrier mold can be extracted toward the axial center side of the pinion shaft, the shape of the core becomes simple. Further, since the lubricating oil that rotates around the pinion shaft is smoothly fed to the first bearing side before the momentum is weakened by gravity, the rotational force and gravity of the pinion shaft are effectively used.

  In the fifth invention, the lubricating oil guide member is constituted by a rib whose one end side is higher than the other end side in a side view formed integrally with the inner surface of the diff carrier.

  According to the above configuration, the lubricating oil guide member is formed with a simple configuration. The lubricating oil whose direction of flow is changed so as to incline upward toward the first bearing side by the lubricating oil guiding member can be smoothly changed in the downward direction due to the influence of gravity, and is directed toward the first bearing. Flowing.

  In the sixth invention, the inclination angle of the lubricating oil guide member in a side view is larger than 20 ° and smaller than 30 ° with respect to the axis of the pinion shaft.

  In other words, if the angle of inclination of the lubricating oil guiding member in a side view is 30 ° or more, the direction of the lubricating oil is changed to the lower side at an early stage due to the influence of gravity, so that the direction toward the first bearing is smooth. It does n’t flow. On the other hand, if it is 20 ° or less, the lubricating oil flowing into the second bearing increases, and the lubricating oil flowing into the first bearing decreases. However, according to the above configuration, the lubricating oil flows toward the first bearing while being smoothly changed in direction without being flowed toward the lower side early due to the influence of gravity.

  As described above, according to the first aspect of the present invention, in the bearing lubrication structure for a differential device, the lubricating oil guide member having a surface inclined with respect to the axial direction is provided in the differential carrier so as to protrude. The direction of the flow of the lubricating oil accompanying the pinion shaft generated by the rotation of the pinion shaft between the two bearings is changed to the first bearing side. For this reason, with a simple configuration, the lubricating oil can be actively fed to the first bearing using the rotational force of the pinion shaft, and the amount of the lubricating oil in the first bearing can be increased to improve its reliability. it can.

  According to the second aspect of the invention, the rotation of the pinion shaft is the rotation when the vehicle moves forward. For this reason, since the lubricating oil can be actively fed to the first bearing when the vehicle travels longer than when the vehicle is traveling backward, the amount of the lubricating oil in the first bearing is increased and the reliability is further improved. Can be made.

  According to the third aspect of the invention, the lubricating oil guiding member is provided on the side from the lower side to the upper side so that the lubricating oil flow around the pinion shaft generated by the rotation of the pinion shaft is provided. For this reason, the lubricating oil that rotates around the pinion shaft by the rotation of the pinion shaft is smoothly fed to the first bearing side by effectively using the rotational force and gravity of the pinion shaft, so the first is more effective. The amount of lubricating oil in the bearing can be increased to further improve its reliability.

  According to the fourth aspect of the invention, the lubricating oil guide member is provided so as to protrude toward the pinion shaft at substantially the same position as the pinion shaft in a side view. For this reason, since the shape of the core of the mold for molding the differential carrier can be simplified, a bearing lubrication structure for a differential device that can increase the amount of lubricating oil of the first bearing is manufactured at low cost. Can do.

  According to the fifth aspect of the invention, the lubricating oil guiding member is constituted by the rib whose one end formed integrally with the inner surface of the diff carrier is higher than the other end. For this reason, since the lubricating oil smoothly flows toward the first bearing while being influenced by gravity by the lubricating oil guiding member having a simple configuration, the lubricating oil for the first bearing is more effectively reduced at a low cost. The amount can be increased to improve its reliability.

  According to the sixth aspect of the invention, the inclination angle of the lubricating oil guiding member in a side view is larger than 20 ° and smaller than 30 ° with respect to the axis of the pinion shaft. For this reason, the lubricating oil flows toward the first bearing while smoothly changing the direction without flowing toward the lower side at an early stage due to the influence of gravity, so the amount of lubricating oil in the first bearing is increased, The reliability can be further improved.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, the following embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or a use. In the present embodiment, left and right refer to the left and right viewed from the driver in the driver's seat.

  FIG. 1 shows a differential device 1 for a rear wheel of a four-wheel drive vehicle having a bearing lubrication structure for a differential device according to an embodiment of the present invention. A propeller shaft (not shown) to which driving force from the engine is transmitted is connected to the front side of the differential device 1.

  The differential device 1 is covered with a substantially T-shaped differential carrier 5 in plan view, which includes a front side portion 5a extending in the longitudinal direction of the vehicle body and a rear side portion 5b extending in the vehicle width direction. The diff carrier 5 is molded by a mold (not shown) formed using a core, a front hollow portion 6 is formed inside the front side portion 5a, and the rear carrier portion 6 is connected to the rear end of the front side hollow portion 6. A rear hollow portion 7 is formed inside the side portion 5b. The rear end of the rear hollow portion 7 is opened, and the opening is covered with the rear cover 8. A predetermined amount of lubricating oil is stored on the bottom side of the front hollow portion 6 and the rear hollow portion 7. In FIG. 1 to FIG. 3, the arrows indicate the flow of the lubricating oil.

  In the front hollow portion 6, first and second drive pinion bearings 10 and 11 as first and second bearings are arranged in order from the front side. The first drive pinion bearing 10 has a smaller outer diameter than the second drive pinion bearing 11.

  A drive pinion shaft 13 is rotatably supported on the front side of the differential carrier 5 by the first and second drive pinion bearings 10 and 11. The drive pinion shaft 13 is formed with a spline portion 41 as an input portion to which power is input at one end, and a drive pinion gear 15 as a pinion gear for transmitting power is provided at the other end. The spline portion 41 is spline-coupled to the flange portion 30 to which the propeller shaft is connected. A screw portion 42 is provided at the tip of the spline portion 41, and the flange portion 30 is fastened to the screw portion 42 to preload the first and second drive pinion bearings 10 and 11 in the axial direction. And a lock nut 31 for positioning the both is fastened. An annular oil seal 32 is provided between the flange portion 30 and the tip of the differential carrier 5. The oil seal 32 seals the flange 30 and the differential carrier 5 in an oil-tight manner while allowing the flange 30 to rotate.

  A ring gear 21 having an axis extending in the vehicle width direction is rotatably disposed in the rear hollow portion 7 of the differential carrier 5. The drive pinion shaft 13 is arranged to be offset downward with respect to the axis of the ring gear 21, and the drive pinion gear 15 and the ring gear 21 are engaged with each other. As a result, the rotation speed and torque from the propeller shaft are converted and transmitted to the ring gear 21 while changing the direction in the perpendicular direction.

  Although not shown in detail, a differential gear case is coupled to the ring gear 21 by a bolt 25 extending in the vehicle width direction. The differential gear case is rotatably supported by left and right side bearings provided on the differential carrier 5. In the differential gear case, left and right side gears are arranged, and the side gears are connected to drive shafts for driving the left and right wheels, respectively. The left and right side gears mesh with a differential pinion gear connected to a differential pinion shaft. Thus, when a difference in rotation occurs between the left and right wheels, a differential is applied to the left and right drive shafts to prevent tire slip.

  The first drive pinion bearing 10 is arranged between the spline portion 41 and the drive pinion gear 15 in the drive pinion shaft 13 in order from the spline portion 41 side and having a diameter larger than that of the spline portion 41. A first bearing contact surface 44 and a second bearing contact surface 45 having a diameter larger than that of the first bearing contact surface 44 and on which the second drive pinion bearing 11 is disposed are formed.

  Inner races 10a and 11a of the first and second drive pinion bearings 10 and 11 are fitted to the first and second bearing contact surfaces 44 and 45, respectively. On the other hand, the outer races 10b and 11b of the first and second drive pinion bearings 10 and 11 are inserted and fixed on the inner surface of the wall portion forming the front hollow portion 6 of the differential carrier 5, respectively. A tapered roller 10c is disposed between the inner race 10a and the outer race 10b of the first drive pinion bearing 10 so that the large diameter side thereof faces the front side of the vehicle. The lubricating oil flows to the front side through the gaps between the respective tapered rollers 10c, whereby the first drive pinion bearing 10 is lubricated and the oil seal 32 is also lubricated. Further, a tapered roller 11c is disposed between the inner race 11a and the outer race 11b of the second drive pinion bearing 11 so that the large diameter side thereof faces the vehicle rear side. The lubricating oil flows into the rear side through the gaps between the respective tapered rollers 11c, whereby the second drive pinion bearing 11 is lubricated.

  A distance piece (plastic region spacer) 12 is provided between the first drive pinion bearing 10 and the second drive pinion bearing 11. The distance piece 12 is a plastically deformed spacer and is configured to generate a repulsive force with a small displacement (return amount). Both end portions in the axial direction of the distance piece 12 are in contact with the inner races 10a, 11a of the first and second drive pinion bearings 10, 11.

  On the inner surface of the upper wall portion that forms the rear hollow portion 7 of the diff carrier 5, an upper rib portion 50 that hangs downward extends in the left-right direction. A part of the lubricating oil splashed upward by the rotation of the ring gear 21 collides with the upper rib portion 50, and the colliding lubricating oil falls in a drop shape toward the left and right side bearings. .

  A hollow lubricating oil supply passage 51 extending from the upper side of the rear hollow portion 7 toward the front hollow portion 6 is provided on the upper side of the differential carrier 5. Specifically, the tip of the lubricating oil supply passage 51 is connected between the first drive pinion bearing 10 and the second drive pinion bearing 11 in the front hollow portion 6. The lubricating oil splashed upward by the rotation of the ring gear 21 flows through the lubricating oil supply passage 51 into the front hollow portion 6.

  Of the wall portion of the differential carrier 5 that partitions the lubricating oil supply passage 51 and the front hollow portion 6, the second drive pinion bearing 11 is flipped upward at the rear end of the upper wall portion by the rotation of the ring gear 21. A return preventing projection 52 is provided so as to protrude upward so that the lubricating oil that has flown into the lubricating oil supply passage 51 does not return to the ring gear 21 side.

  On the lower side of the front hollow portion 6, a hollow return path 53 having a front opening communicating with the front end of the front hollow portion 6 and a rear opening communicating with the rear hollow portion 7 is provided. The lubricating oil flowing into the first drive pinion bearing 10 is returned to the rear hollow portion 7 through the return path 53.

  As shown in FIGS. 2 and 3, on the inner surface of the front hollow portion 6 of the differential carrier 5, the flow of lubricating oil accompanying the drive pinion shaft 13 generated by the rotation of the drive pinion shaft 13 (white) A lubricating oil guide member 54 is integrally provided to change the direction of the first drive pinion bearing 10 to the direction of the first drive pinion bearing 10.

  As shown in FIG. 3, the lubricating oil guide member 54 is provided on the side where the flow of lubricating oil accompanying the drive pinion shaft 13 generated by the rotation of the drive pinion shaft 13 when the vehicle moves forward is directed from the lower side to the upper side (that is, the vehicle On the right). A substantially central portion in the front-rear direction of the lubricating oil guide member 54 is provided at substantially the same position as the axis of the drive pinion shaft 13. That is, the lubricating oil guide member 54 protrudes to the left in the vehicle width direction so that the extending direction is horizontal when cut along a plane perpendicular to the drive pinion shaft 13. The direction in which the lubricating oil guiding member 54 extends is the same as the direction in which the core is removed when the mold of the differential carrier 5 is manufactured.

  As shown in FIG. 2, in a side view, the lubricating oil guiding member 54 has an inclined surface 54 a that is inclined with respect to the axial direction so that the front side is higher than the rear side. The inclination angle of the inclined surface 54a is greater than 20 ° and smaller than 30 ° with respect to the axis of the drive pinion shaft 13, and is preferably 25 °.

-Driving action-
Next, the operation of the bearing lubrication structure for a differential device according to the embodiment of the present invention will be described.

  When the engine of the vehicle is driven, the driving force is transmitted to the propeller shaft, and is transmitted from the propeller shaft to the drive pinion shaft 13 via the flange portion 30.

  Next, the ring gear 21 meshed with the drive pinion gear 15 rotates. At this time, the lubricating oil splashed to the upper part in the differential carrier 5 by the ring gear 21 passes through the lubricating oil supply passage 51 and is guided between the first and second drive pinion bearings 10 and 11 in the front hollow portion 6. It is burned. As a result, the lubricating oil is sufficiently supplied into the front hollow portion 6 and the oil level becomes such that the first and second drive pinion bearings 10 and 11 are immersed.

  At this time, since the first drive pinion bearing 10 has a smaller diameter than the second drive pinion bearing 11, a gap between the respective tapered rollers 10c in the bearing is small, and the lubricating oil passes through the inside of the bearing and returns to the return path. It is difficult to sufficiently flow toward the 53 side, and more lubricating oil flows toward the second drive pinion bearing 11 side with less resistance. However, according to the present embodiment, the lubricating oil that flows from the lower side to the upper side around the drive pinion shaft 13 due to the rotation of the drive pinion shaft 13 is forced to flow by the lubricating oil guiding member 54 of the differential carrier 5. The direction is changed and the air flows to the first drive pinion bearing 10 side on the front side.

  The direction in which the lubricating oil flows is such that the lubricating oil whose direction has been changed by the inclined surface 54a is pushed back by gravity, that is, obliquely upward and then gradually downward. It flows to the bearing 10 for a motor.

  The lubricating oil that has passed between the respective tapered rollers 10c of the first drive pinion bearing 10 and lubricated the first drive pinion bearing 10 returns to the rear hollow portion 7 via the return path 53, and the second The lubricating oil that has passed between the tapered rollers 11 c of the drive pinion bearing 11 and lubricated the second drive pinion bearing 11 returns directly to the rear hollow portion 7.

-Effect of the embodiment-
In the differential device bearing lubrication structure, a lubricant guide member 54 having an inclined surface 54a inclined with respect to the axial direction is provided in the differential carrier 5 so as to protrude between the first and second drive pinion bearings 10 and 11. The direction of the flow of the lubricating oil that rotates around the drive pinion shaft 13 generated by the rotation of the drive pinion shaft 13 is changed to the first drive pinion bearing 10 side. For this reason, with a simple configuration, the lubricating oil is positively sent to the first drive pinion bearing 10 by using the rotational force of the drive pinion shaft 13, and the amount of the lubricating oil in the first drive pinion bearing 10 is increased. The reliability can be improved.

  In the present embodiment, the rotation of the drive pinion shaft 13 is the rotation at the time of forward movement of the vehicle. For this reason, since the lubricating oil can be positively fed into the first drive pinion bearing 10 when the vehicle travels longer than when the vehicle is traveling backward, the amount of lubricating oil in the first drive pinion bearing 10 is increased, The reliability can be further improved.

  Further, in the present embodiment, the lubricating oil guide member 54 is provided on the side from the lower side to the upper side where the lubricating oil flows around the drive pinion shaft 13 generated by the rotation of the drive pinion shaft 13. For this reason, the lubricating oil that rotates around the drive pinion shaft 13 by the rotation of the drive pinion shaft 13 is smoothly sent to the first drive pinion bearing 10 side by effectively using the rotational force and gravity of the drive pinion shaft 13. Therefore, the amount of lubricating oil in the first drive pinion bearing 10 can be increased more effectively, and the reliability can be further improved.

  Further, in the present embodiment, the lubricating oil guide member 54 protrudes horizontally from the inner surface of the differential carrier 5 when viewed from the side of the drive pinion shaft 13 and in the axial direction of the drive pinion shaft 13. It is provided as follows. For this reason, since the shape of the core of the mold for molding the differential carrier 5 can be simplified, a bearing lubrication structure for a differential device that can increase the amount of lubricating oil in the first drive pinion bearing 10 is manufactured at low cost. be able to.

  In the present embodiment, the lubricating oil guiding member 54 is constituted by a rib whose one end formed integrally with the inner surface of the diff carrier 5 is higher than the other end. For this reason, the lubricating oil guide member 54 having a simple configuration allows the lubricating oil to smoothly flow toward the first drive pinion bearing 10 while being affected by gravity, so that the first drive can be more effectively performed at low cost. The amount of lubricating oil in the pinion bearing 10 can be increased to improve its reliability.

  In the present embodiment, the inclination angle of the lubricating oil guiding member 54 in a side view is greater than 20 ° and smaller than 30 ° with respect to the axis of the drive pinion shaft 13. Therefore, the lubricating oil flows toward the first drive pinion bearing 10 while smoothly changing the direction without flowing toward the lower side at an early stage due to the influence of gravity, so that the lubrication of the first drive pinion bearing 10 is performed. The amount of oil can be increased to further improve its reliability.

(Other embodiments)
The present invention may be configured as follows with respect to the above embodiment.

  In the above-described embodiment, the differential device 1 for the rear wheel of the four-wheel drive vehicle in which the spline portion 41 of the drive pinion shaft 13 is disposed on the front side of the vehicle has been described, but the spline portion 41 of the drive pinion shaft 13 is located on the rear side of the vehicle. The present invention can also be applied to a four-wheel drive vehicle disposed in the vehicle. Also in this case, the lubricating oil may be forced to flow into the first drive pinion bearing 10 side where the load increases when the vehicle moves forward.

  In the above embodiment, the first and second drive pinion bearings 10 and 11 are tapered roller bearings, but the present invention can be applied to other types of bearings.

  As described above, the present invention is useful for a differential device bearing lubrication structure for lubricating a bearing that supports a pinion shaft of a differential device used in a four-wheel drive vehicle or the like on a differential carrier.

It is a side sectional view of a differential device provided with a bearing lubrication structure for a differential device according to an embodiment of the present invention. It is a sectional side view of a diff carrier. It is the III-III sectional view taken on the line of FIG.

Explanation of symbols

5 Diff carrier 10 First drive pinion bearing (first bearing)
11 Bearing for second drive pinion (second bearing)
13 Drive pinion shaft 15 Drive pinion gear (pinion gear)
21 Ring gear 41 Spline part (input part)
51 Lubricating oil supply path (supply path)
53 Return path 54 Lubricating oil guiding member 54a Inclined surface (inclined surface)

Claims (6)

A differential carrier, a pinion shaft having an input portion for inputting power to one end and a pinion gear for transmitting power to the other end, and the differential carrier are arranged in parallel from the one end side, and the pinion shaft is A first bearing having a small diameter supported by the differential carrier, a second bearing having a larger diameter than the first bearing, and a ring gear meshed with the pinion gear;
Lubricating oil splashed upward by the rotation of the ring gear is guided to the first and second bearings through a supply path extending between the first bearing and the second bearing, and the ring gear side through the return path. A bearing lubrication structure for a differential device that lubricates the first and second bearings by returning to
In the differential carrier, an axial direction that changes the direction of the flow of lubricating oil accompanying the pinion shaft generated by the rotation of the pinion shaft between the first and second bearings to the first bearing side. A bearing lubrication structure for a differential device, characterized in that a lubricating oil guide member having an inclined surface is provided in a protruding manner. In the bearing lubrication structure for a differential device according to claim 1,
A bearing lubrication structure for a differential device, wherein the rotation of the pinion shaft is rotation at the time of forward movement of the vehicle. In the bearing lubrication structure for a differential device according to claim 1 or 2,
A bearing lubrication structure for a differential device, wherein the lubricating oil guide member is provided on a side from a lower side to an upper side where a flow of lubricating oil generated by rotation of the pinion shaft and accompanying the pinion shaft is provided. In the bearing lubrication structure for a differential device according to claim 3,
A bearing lubrication structure for a differential device, wherein the lubricating oil guide member is provided at substantially the same position as the pinion shaft in a side view and protrudes toward the pinion shaft. In the bearing lubricating structure for a differential device according to claim 3 or 4,
A bearing lubrication structure for a differential device, wherein the lubricating oil guide member is constituted by a rib whose one end side is higher than the other end side in a side view formed integrally with the inner surface of the differential carrier. The bearing lubrication structure for a differential device according to claim 5,
A bearing lubrication structure for a differential device, wherein an inclination angle of the lubricating oil guide member in a side view is larger than 20 ° and smaller than 30 ° with respect to the axis of the pinion shaft.

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