JP2014145409A - Lubrication structure of power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lubrication structure of a power transmission device, which enables supply of a sufficient amount of lubricating oil to necessary parts in reverse traveling of a vehicle with a simple structure.SOLUTION: A lubrication structure of a power transmission device has a pinion gear 4 connected to a propeller shaft, a ring gear, a differential case rotating integrally with the ring gear, and a pair of bearings supporting the differential case at both ends in an axial direction, which are built in a carrier, and supplies lubricating oil stored in a bottom of the carrier to one of the bearings. An inner wall face of a front carrier 2A is formed with a groove-shaped lubricating oil flow passage 21 for reverse travel which has a downstream end facing an axial outside of the one bearing and supplies the lubricating oil, which is scooped up by the pinion gear 4 rotating in a reverse travel rotation direction Q, to the one bearing.

Description

  The present invention relates to a lubricating structure for a power transmission device.

  Examples of a power transmission device that includes a pinion gear and a ring gear and in which both gears are orthogonally engaged include a final reduction device for driving a rear wheel of a vehicle, an auxiliary transmission device for driving a four wheel, and the like. The final reduction gear supports the pinion shaft connected to the propulsion shaft (propeller shaft), the ring gear orthogonally meshing with the pinion shaft, the differential case as a rotating body that rotates integrally with the ring gear, and the axial ends of the differential case. In general, a configuration including a pair of bearings and a case (hereinafter referred to as a carrier) in which the above-described components are built-in is provided.

  Since the gears and the bearings generate heat due to high-speed rotation, the bottom of the carrier is filled with lubricating oil to cool them. Lubricating oil is swept up by a rotating ring gear and supplied to a necessary part such as a bearing. As a means for efficiently supplying the lubricating oil, an oil collecting member that collects the lubricating oil swirled by the ring gear is attached in the carrier, and the lubricating oil collected by the oil collecting member is attached to the inner wall of the carrier. A technique for leading to a necessary part through the formed passage is mentioned (for example, see Patent Documents 1 and 2).

JP 2001-180313 A JP 2012-159185 A

  However, the techniques described in Patent Documents 1 and 2 are for collecting the lubricating oil that has been lifted up when the ring gear rotates in the rotation direction when the vehicle moves forward, and the ring gear moves in the rotation direction when the vehicle moves backward. Lubricating oil that is swept up when turning cannot be collected. Although it is conceivable to add an oil collecting member for backward traveling of the vehicle, this is also difficult in the limited internal space of the carrier, and there is a problem that the number of parts increases.

  The present invention was devised to solve such problems, and has a simple structure and a lubricating structure for a power transmission device capable of supplying a sufficient amount of lubricating oil to a necessary part when the vehicle is moving backward. The purpose is to provide.

  In order to solve the above-described problems, the present invention provides a pinion gear connected to a propulsion shaft, a ring gear orthogonally meshing with the pinion gear, a rotating body that rotates integrally with the ring gear, and the rotating body supported at both ends in the axial direction. And a pair of bearings built in the carrier, and a lubricating structure for a power transmission device that supplies lubricating oil stored in the bottom of the carrier to the bearing. A groove-like reverse lubricating oil flow path is formed, which faces the outside of the bearing in the axial direction and supplies the lubricating oil pumped up by the reversely rotating pinion gear to the one bearing.

  According to the present invention, a sufficient amount of lubricating oil can be supplied to the bearing when the vehicle is moving backward with a simple structure by using the pinion gear that rotates backward.

  Further, the present invention provides a projecting piece, which is located above the pinion gear on the inner wall surface of the carrier and guides the lubricating oil that is lifted up when the ring gear rotates when the vehicle moves forward to the one bearing. The backward lubricating oil flow path is formed below the projecting piece.

  According to the present invention, the lubricating oil that is lifted up by the pinion gear can enter the backward lubricating oil flow path without being blocked by the projecting piece provided for the lubricating structure when the vehicle moves forward.

  Further, according to the present invention, the reverse lubricating oil passage is substantially horizontally extended at a position substantially the same height as the upper end of the pinion gear and at a position on the reverse rotation direction side of the pinion gear from the upper end of the pinion gear. It is characterized by.

  According to the present invention, the lubricating oil can be efficiently allowed to enter the backward lubricating oil flow path.

  Further, in the present invention, the inner wall surface of the carrier has a side wall surface facing the teeth of the pinion gear, and a bearing fitting hole surface formed continuously to the side wall surface and into which the one bearing is fitted, The reverse lubricating oil passage is formed across the side wall surface and the bearing fitting hole surface.

  According to the present invention, the shape of the backward lubricating oil passage on the inner wall surface of the carrier can be a simple shape without being complicated.

  In the present invention, the rotating body is a differential case, and the carrier is a carrier of a final reduction gear.

  According to the present invention, a sufficient amount of lubricating oil can be supplied to the bearing for supporting the differential case when the vehicle is moving backward with a simple structure in the final reduction gear.

  Furthermore, the present invention is characterized in that the rotating body is a ring gear shaft connected to a transaxle, and the carrier is a carrier of an auxiliary transmission device that houses the ring gear shaft.

  According to the present invention, in the auxiliary transmission, a sufficient amount of lubricating oil can be supplied to the bearing for supporting the ring gear shaft when the vehicle moves backward with a simple structure.

  According to the present invention, a sufficient amount of lubricating oil can be supplied to the bearing when the vehicle is moving backward with a simple structure by using the pinion gear that rotates backward.

It is a side view of a final reduction gear. It is a plane sectional view of a final reduction gear. It is the back front view of the final reduction gear in the state where the rear part carrier was removed. It is a back front view of a front carrier simple substance. It is AA sectional drawing in FIG. It is BB sectional drawing in FIG. It is an operation view of the present invention, and is a rear front view of the front carrier in a state where the pinion gear and the garter are assembled. It is an operation view of the present invention, and is a perspective view of a front carrier in a state where a pinion gear is assembled.

  Hereinafter, the form which applied the lubrication structure concerning the present invention to the final reduction gear for rear-wheel drive is explained. In FIG. 1, the final reduction gear 1 includes a carrier 2 as a housing. The carrier 2 is divided into a front carrier 2A on the front side and a rear carrier 2B on the rear side with a plane along the axis O of the built-in ring gear 5 (FIG. 2) as a split surface S. The front carrier 2A and the rear carrier 2B are fastened and fixed to each other by bolts 20.

  In FIG. 2, the carrier 2 includes a rotation around the rear end of the pinion shaft 3, a pinion gear 4 formed at the rear end of the pinion shaft 3, a ring gear 5 orthogonally meshed with the pinion gear 4, and a rotation that rotates integrally with the ring gear 5. A differential case 6 as a body, a right bearing 7A and a left bearing 7B for supporting the differential case 6 at both ends in the axial direction are incorporated.

"Differential case 6"
The differential case 6 constitutes a gear housing chamber 9 and is formed at a substantially spherical shell-shaped shell portion 10 that rotates around the axis O of the ring gear 5 and at both ends in the left-right direction of the shell portion 10. It consists of a shape provided with a pair of boss portions 11 forming a shape. A pinion shaft 12 is disposed in the gear storage chamber 9 along a plane orthogonal to the axis O. The pinion shaft 12 is integrated with the shell portion 10 by inserting both ends thereof into shaft attachment holes 13 formed in the shell portion 10.

  A pinion gear 14 is rotatably attached to the pinion shaft 12 near both ends of the pinion shaft 12. A drive shaft (not shown) is inserted into each boss portion 11, and is attached to the end of the drive shaft (not shown) in the gear storage chamber 9 so as to rotate integrally with the drive shaft and slide along the axis O by spline connection. The side gear 15 meshes with the pinion gear 14. A thrust washer 16 is interposed between the back surface of the side gear 15 and the inner surface of the gear storage chamber 9. A spiral groove 17 is formed on the inner peripheral surface of the boss portion 11 to guide the lubricating oil on the surface of the drive shaft to the gear housing chamber 9 side when the drive shaft rotates in the forward rotation direction.

  A ring gear 5 that rotates around the axis O together with the differential case 6 is attached to one side of the shell portion 10 of the differential case 6 in the direction of the axis O. Specifically, a flange portion 18 extending in the radially outward direction is formed near one side of the shell portion 10 in the axial center O direction, and the ring gear 5 is fastened and fixed to the flange portion 18 by a bolt 19. The ring gear 5 is a gear having a larger diameter than the pinion gear 4.

"Internal configuration of front carrier 2A"
Referring to FIGS. 2 to 6, the front carrier 2 </ b> A has a transmission mechanism portion accommodation space 31 that has a substantially rectangular shape as an internal space, and a left and right sides from both sides of the transmission mechanism portion accommodation space 31. The substantially semi-cylindrical differential case support portion receiving spaces 32A and 32B extending outward in the direction, and the pinion shaft receiving space having a substantially cylindrical shape extending in the front-rear direction near the front of the transmission mechanism portion receiving space 31 33.

  As shown in FIG. 2, the periphery of the pinion shaft 3 is accommodated in the pinion shaft accommodation space 33 and supported by the front carrier 2 </ b> A via bearings 8 and 8. The front end of the pinion shaft 3 is connected to the propulsion shaft, for example, via a viscous joint (not shown). Reference symbol O ′ denotes the axis of the pinion shaft 3 along the vehicle longitudinal direction, that is, the axis of the pinion gear 4.

  The transmission mechanism housing space 31 accommodates the entire pinion gear 4 and the front half of the ring gear 5 and the differential case 6. With reference to FIGS. 4 to 6, the inner wall surface of the front carrier 2 </ b> A constituting the transmission mechanism housing space 31 is mainly formed along a substantially rectangular front wall surface 34 along a plane orthogonal to the front-rear direction. And an upper surface 35, side wall surfaces 36 and 37, and a bottom surface 38 respectively extending rearward from the edge portion of the front wall surface 34.

  A circular opening 39 communicating with the pinion shaft housing space 33 is formed in the front wall surface 34. In addition, a plate-like projecting piece 40 is provided above the circular opening 39 in the front wall surface 34 so as to incline downward as it goes to the right. The projecting piece 40 is formed over the front wall surface 34 and the side wall surface 36 and is located above the pinion gear 4. As will be described in detail later, a garter 41 for collecting the lubricating oil that is lifted up when the ring gear 5 (FIG. 3) rotates when the vehicle moves forward is placed and fixed on the projecting piece 40. A lubricating oil collection space 49 is formed above the garter 41. The lubricating oil adhering to the inner wall of the lubricating oil collecting space 49 flows along the upper surface of the garter 41 to the upper surface of the projecting piece 40, and is guided by the upper surface of the projecting piece 40 to be described later. It flows to 42. In the present invention, the garter 41 is a member that does not fall within the spirit of the present invention, and a description of a specific shape is omitted. Further, in some cases, without providing the garter 41, it is also possible to cause the lubricating oil that has been lifted up when the ring gear 5 (FIG. 3) rotates when the vehicle moves forward to flow directly from the lubricating oil collecting space 49 onto the protruding piece 40. Absent.

  Of the left and right side wall surfaces 36, 37, the left side wall surface 37 constitutes a side surface facing the flange portion 18 of the differential case 6, and the right side wall surface 36 constitutes a side surface facing the teeth of the pinion gear 4. On the side wall surface 36, a groove-shaped first lubrication for forward advancement extending substantially horizontally to supply the lubricating oil collected by the garter 41 and flowing on the protruding piece 40 to the right bearing 7A. An oil passage 42 is formed.

  Next, bearing fitting hole surfaces 43A and 43B into which the front half of the bearings 7A and 7B are fitted are formed on the inner wall surfaces constituting the differential case support portion accommodating spaces 32A and 32B. Bearing pressure contact walls 24 and 25 are provided on the outer sides of the bearing fitting hole surfaces 43A and 43B in the axial direction so as to suppress the outer surfaces of the bearings 7A and 7B. In addition, the code | symbol 26 shown in FIG. 2 is a shim interposed between the bearings 7A and 7B and the bearing press-contact walls 24 and 25. The bearing fitting hole surfaces 43A and 43B are formed so as to be substantially perpendicular to the side wall surfaces 36 and 37, respectively.

  In the right differential case support portion receiving space 32A, a groove-like advancement groove extending substantially horizontally so as to communicate with the advancement first lubricating oil passage 42 is formed in a part of the bearing fitting hole surface 43A. A second lubricating oil passage 44 is formed. The downstream end of the forward second lubricating oil passage 44 is positioned so as to face outward in the axial direction of the bearing 7 </ b> A by forming a notch 27 in a part of the bearing pressure-contact wall 24. Further, in the left differential case support portion receiving space 32B, a groove-like forward / backward lubricating oil passage 45 extending substantially horizontally is formed in a part of the bearing fitting hole surface 43B. The downstream end of the forward / reverse lubricating oil passage 45 is positioned so as to face the axially outward direction of the bearing 7 </ b> B by forming a notch 28 in a part of the bearing pressure contact wall 25.

"Internal configuration of rear carrier 2B"
In FIG. 2, the rear carrier 2 </ b> B is extended outwardly in the left-right direction from the transmission mechanism portion accommodation space 46 having a substantially rectangular shape as an internal space, and from both front sides of the transmission mechanism portion accommodation space 46. It is formed so as to have a substantially semi-cylindrical differential case support space 47A, 47B. In the transmission mechanism accommodating space 46, the rear half of the ring gear 5 and the differential case 6 are accommodated. Bearing fitting hole surfaces 48A and 48B into which the rear halves of the bearings 7A and 7B are fitted are formed on the inner wall surfaces constituting the differential case support portion accommodating spaces 47A and 47B, respectively.

  In the final reduction gear 1 having the above configuration, lubricating oil is stored at the bottom in the carrier 2 in which the front carrier 2A and the rear carrier 2B are assembled. In FIG. 3, the symbol L indicates the level of the lubricating oil, and the level L is at a height that allows the periphery of the lower end of the ring gear 5 and the lower end of the pinion gear 4 to be immersed in the lubricating oil.

  Here, the lubrication oil supply path to the left and right bearings 7A and 7B when the vehicle moves forward will be described. When the vehicle moves forward, the ring gear 5 rotates clockwise when viewed from the right side in FIG. Fry. On the bearing 7B side, since the left side wall surface 37 of the front carrier 2A is positioned in the vicinity of the ring gear 5, a relatively large amount of lubricating oil adheres to the side wall surface 37 as droplets. Accordingly, a part of the lubricating oil falling along the side wall surface 37 reaches the outside of the bearing 7B in the axial direction as a sufficient amount through the forward / backward moving lubricating oil passage 45 and the notch 28. A part of the lubricating oil that has reached the outside in the axial direction of the bearing 7B is supplied for lubricating the bearing 7B, and the rest is supplied to the gear housing chamber 9 of the differential case 6 through the spiral groove 17 in FIG. Is done.

  Further, in FIG. 3, a part of the lubricating oil swept up by the ring gear 5 is collected in the lubricating oil collecting space 49 and flows down to the upper surface of the projecting piece 40 that forms the lower surface of the lubricating oil collecting space 49. , A part flows down to the upper surface of the projecting piece 40 via the upper surface of the garter 41, flows into the forward advance first lubricating oil passage 42, and passes through the forward advance second lubricating oil passage 44 and the notch 27. It reaches the outside of the bearing 7A in the axial direction. A part of the lubricating oil that has reached the outside in the axial direction of the bearing 7A is supplied for lubricating the bearing 7A, and the rest is supplied to the gear housing chamber 9 of the differential case 6 through the spiral groove 17.

  On the other hand, when the vehicle moves backward, the ring gear 5 rotates counterclockwise as viewed from the right side of FIG. On the bearing 7B side, since the left side wall surface 37 of the front carrier 2A is positioned close to the ring gear 5 as described above, a relatively large amount of lubrication is provided on the side wall surface 37 regardless of the rotational direction of the ring gear 5. Oil adheres. Therefore, a sufficient amount of lubricating oil is supplied to the outside of the bearing 7B in the axial direction even when the vehicle is moving backward.

  However, since the ring gear 5 rotating in the reverse rotation direction does not lift up the lubricating oil toward the lubricating oil collecting space 49, a sufficient amount of lubricating oil does not enter, so that the lubricating oil is supplied to the bearing 7A. The amount is in short supply. It is advisable to provide the rear carrier 2B on the rear carrier 2B side in accordance with the garter 41, the forward first lubricating oil passage 42, and the forward forward second lubricating oil passage 44 as the number of parts increases. is not.

  Here, in FIG. 7, the pinion gear 4 rotates counterclockwise (forward rotation direction P) when the vehicle moves forward, and rotates clockwise (reverse rotation direction Q) when the vehicle moves backward. Accordingly, a part of the lubricating oil swept up by the pinion gear 4 rotating in the reverse rotation direction Q is blown toward the side wall surface 36, and the forwardly moved lubricating oil is formed on the side wall surface 36. If it can efficiently enter the one lubricating oil flow path 42, the problem of insufficient lubricating oil for the bearing 7A should be solved. However, since the projecting piece 40 is located above the pinion gear 4, there is a problem that the skipped lubricating oil is blocked by the projecting piece 40 and cannot enter the forward first lubricating oil flow path 42. .

  With respect to the above problems, in the present invention, as shown in FIG. 7, the lubricating oil is swept up by the pinion gear 4 that rotates backward, with the downstream end facing the axially outer side of the bearing 7A on the inner wall surface of the front carrier 2A. Is formed in the groove-like reverse lubricating oil passage 21. The reverse lubricating oil passage 21 is formed below the protruding piece 40. The reverse lubricating oil passage 21 extends substantially horizontally, for example, at a position substantially the same as the upper end 4A of the pinion gear 4 and at a position closer to the reverse rotation direction Q side of the pinion gear 4 than the upper end 4A of the pinion gear 4. ing. “Position of the pinion gear 4 in the reverse rotation direction Q side with respect to the upper end 4A of the pinion gear 4” means the upper end 4A generated when the pinion gear 4 rotates in the reverse rotation direction Q within the tangential direction passing through the upper end 4A of the pinion gear 4. 7 is a position on the right side of the upper end 4A in the tangential direction passing through the upper end 4A in FIG.

  The reverse lubricating oil passage 21 of the present embodiment is a groove-like reverse reversely extending groove extending substantially horizontally on the side wall surface 36 of the front carrier 2A at the same height as the upper end 4A of the pinion gear 4. 1st lubricating oil flow path 22 and the 2nd lubrication for reverse traveling in the shape of a groove that communicates with the first lubricating oil flow path 22 for reverse travel and extends substantially horizontally to the bearing fitting hole surface 43A of the front carrier 2A. An oil flow path 23 is provided. The downstream end of the reverse second lubricating oil passage 23 is positioned so as to face the outside in the axial direction of the bearing 7 </ b> A by forming a notch 29 in a part of the bearing pressure-contact wall 24. The reverse first lubricating oil flow path 22 is formed below the forward moving first lubricating oil flow path 42 on the side wall surface 36, and the reverse moving second lubricating oil flow path 23 is formed on the bearing fitting hole surface 43A. 2 formed below the lubricating oil passage 44.

"Action"
The operation of supplying lubricating oil to the bearing 7A when the vehicle is moving backward will be described. When the vehicle reverses, the pinion gear 4 rotates in the reverse rotation direction Q, whereby a part of the lubricating oil adhering to the teeth of the pinion gear 4 is blown toward the side wall surface 36, and the first reverse gear formed on the side wall surface 36. The lubricating oil flow path 22 is entered. Specifically, the lubricating oil adhering to the teeth of the pinion gear 4 is blown along all tangential directions of the pinion gear 4, but at the portion where the tangential direction and the side wall surface 36 intersect at right angles, that is, at the side wall surface 36. By forming the reverse first lubricating oil passage 22 at a portion substantially at the same height as the upper end 4 </ b> A of the pinion gear 4, the lubricating oil can be efficiently allowed to enter the reverse first lubricating oil passage 22. . Further, the lubricating oil blown toward the lower surface of the projecting piece 40 also travels along the lower surface of the projecting piece 40 and enters the reverse first lubricating oil flow path 22.

  The lubricating oil that has entered the reverse first lubricating oil passage 22 flows into the reverse second lubricating oil passage 23 while being guided by the groove shape of the reverse first lubricating oil passage 22. The lubricating oil passes through the second lubricating oil passage 23 for reverse travel, passes through the outer peripheral surface of the bearing 7A in the axial direction, and reaches the outside of the bearing 7A in the axial direction through the notch 29. The lubricating oil that has reached the outside in the axial direction of the bearing 7A is supplied for lubricating the bearing 7A.

  As described above, the grooved reverse lubrication that supplies the bearing 7A with the lubricating oil swept up by the pinion gear 4 that rotates backward, with the downstream end facing the inner wall surface of the front carrier 2A in the axial direction of the bearing 7A. When the oil passage 21 is provided, a sufficient amount of lubricating oil can be supplied to the bearing 7A even when the vehicle is moving backward.

  Further, when a projecting piece 40 is provided at a position above the pinion gear 4 to guide the lubricating oil lifted up when the ring gear 5 rotates when the vehicle moves forward to the bearing 7A, the backward lubricating oil flow By forming the path 21 below the projecting piece 40, the lubricating oil that is lifted up by the pinion gear 4 can enter the backward lubricating oil flow path 21 without being blocked by the projecting piece 40.

  Further, the reverse lubricating oil passage 21 extends substantially horizontally at a position substantially the same height as the upper end 4A of the pinion gear 4 and closer to the reverse rotation direction Q side of the pinion gear 4 than the upper end 4A of the pinion gear 4. If it is set as the structure to perform, lubricating oil can be efficiently made to enter into the backward lubricating oil flow path 21.

  Further, if the reverse lubricating oil passage 21 is formed across the side wall surface 36 of the carrier 2 and the bearing fitting hole surface 43A, the shape of the reverse lubricating oil passage 21 on the inner wall surface of the carrier 2 becomes complicated. Simple shape is sufficient.

  The preferred embodiment of the present invention has been described above. The present invention is not limited to the application to the final reduction gear device 1 for driving the rear wheels, but includes a pinion gear connected to the propulsion shaft, a ring gear orthogonally meshed with the pinion gear, a rotating body that rotates integrally with the ring gear, The present invention can be applied to any power transmission device as long as it has a structure in which a pair of bearings that support the body at both ends in the axial direction are built in the carrier.

  For example, a four-wheel drive sub-transmission device is a device that distributes power so that power output from a transaxle for driving front wheels is also output to a rear wheel, and is generally connected to a propulsion shaft. A pinion gear, a ring gear orthogonally meshing with the pinion gear, a ring gear shaft as a rotating body that rotates integrally with the ring gear and connected to the transaxle, and a pair of bearings that support the ring gear shaft at both ends in the axial direction, These are built in the carrier and have a structure in which lubricating oil is stored at the bottom of the carrier. Therefore, the present invention can be easily applied to a four-wheel drive auxiliary transmission.

1 Final reduction gear (power transmission device)
2 carrier 2A front carrier 2B rear carrier 3 pinion shaft 4 pinion gear 4A upper end of pinion gear 5 ring gear 6 differential case (rotating body)
7A, 7B Bearing 21 Reverse lubricating oil passage 22 Reverse first lubricating oil passage 23 Reverse second lubricating oil passage 31 Transmission mechanism housing space 32A, 32B Differential case support housing space 33 Pinion shaft housing space 34 Wall surface 36, 37 Side wall surface 40 Projection piece 41 Garter 42 First forward lubricating oil passage 43A, 43B Bearing fitting hole surface 44 Second forward lubricating oil passage 45 Forward forward lubricating oil passage P Forward rotation direction Q Reverse rotation direction

Claims (6)

A carrier includes a pinion gear connected to the propulsion shaft, a ring gear that is orthogonally engaged with the pinion gear, a rotating body that rotates integrally with the ring gear, and a pair of bearings that support the rotating body at both ends in the axial direction. A lubricating structure of a power transmission device that supplies lubricating oil stored in a bottom portion of the carrier to the bearing,
A groove-like reverse lubricating oil passage for supplying the one bearing with lubricating oil that is swept up by the pinion gear rotating in the reverse direction with the downstream end facing the outer axial direction of one bearing on the inner wall surface of the carrier. A lubrication structure for a power transmission device, characterized by being formed. On the inner wall surface of the carrier, a projecting piece is provided so as to guide the lubricating oil, which is located above the pinion gear and lifted when the ring gear rotates when the vehicle moves forward, to the one bearing,
2. The lubricating structure for a power transmission device according to claim 1, wherein the reverse lubricant flow path is formed below the protruding piece. 3. The reverse lubricant flow path is
3. The vehicle according to claim 1, wherein the pinion gear extends substantially horizontally at a position that is substantially the same height as the upper end of the pinion gear and is closer to the reverse rotation direction side of the pinion gear than the upper end of the pinion gear. A lubricating structure of the power transmission device described. The inner wall surface of the carrier has a side wall surface that faces the teeth of the pinion gear, and a bearing fitting hole surface that is formed continuously to the side wall surface and into which the one bearing is fitted,
4. The power transmission device lubrication according to claim 1, wherein the reverse lubricating oil passage is formed across the side wall surface and the bearing fitting hole surface. 5. Construction.   The lubricating structure for a power transmission device according to any one of claims 1 to 4, wherein the rotating body is a differential case, and the carrier is a carrier of a final reduction gear.   The rotating body is a ring gear shaft coupled to a transaxle, and the carrier is a carrier of an auxiliary transmission device that houses the ring gear shaft. The lubrication structure of the power transmission device described in 1.

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