JP2017096381A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device capable of properly lubricating a bearing or a multiple disc clutch arranged coaxially with the bearing.SOLUTION: A power transmission device includes a ring gear 20, a drive pinion gear 10, a rear taper roller bearing 40, a front taper roller bearing 30, a differential case 310, a right taper roller bearing 340, a sleeve 50, and a case 100. In the power transmission device, an external fitting part 52 externally fits and holds the right taper roller bearing 340, a held part 53 is fixed to the case 100, a bearing holding part 52b is formed in a trunk part 51, an oil storage chamber 54 configured to store oil is formed at the upper part of the trunk part 51, in the sleeve 50 formed is a first oil passage 55 configured to guide oil in the oil storage chamber 54 to the rear taper roller bearing 40, and in the drive pinion gear 10 formed is a second oil passage 14 opened at a rear side shaft part 12 and a front side shaft part 13 and configured to guide oil from the first oil passage 55 to a back face side of the pinion gear 11.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a power transmission device.

  The final reduction device of the automobile is arranged at the rear of the vehicle, the power generated by the prime mover is decelerated by the transmission, the power transmitted via the propulsion shaft is reduced again, and the left and right wheels are It is intended to provide smooth running by adjusting the number of revolutions.

  The final reduction gear device includes a final reduction gear mechanism, a differential device, and a case (carrier, housing) for housing them. The final reduction gear mechanism includes a pair of bevel gears including a drive pinion gear that is a bevel gear that rotates integrally with a propeller shaft and a ring gear that is a bevel gear meshing at right angles with the drive pinion gear. The differential device includes a differential case that rotates integrally with the ring gear, a side gear that is disposed inside the differential case and rotates integrally with the drive shaft, a pinion gear that meshes with the side gear and that is disposed within the differential case, and is inserted through a hole in the pinion gear. The pinion shaft fits into the differential case.

  Here, since the drive pinion gear and the ring gear mesh at a right angle, the meshing reaction force acts in the axial direction (rotational axis direction) of each gear. For this reason, a taper roller bearing is generally employed as a bearing for supporting the drive pinion gear and the ring gear, and receives an axial reaction force (thrust load). For example, a drive pinion gear is provided with tapered roller bearings on the back surface of a bevel gear formed at the rear end portion and the approximate center of a shaft portion extending forward from the bevel gear, respectively, and receives axial thrust loads in the front and rear directions. Yes.

  In addition, the final reduction gear generally uses a ring gear to scoop up oil stored at the bottom of the case, and supply the splashed oil to a portion that requires lubrication. However, since the tapered roller bearing that supports the drive pinion gear is separated from the ring gear, it is difficult to sufficiently supply oil. Therefore, Patent Document 1 discloses a technique in which an oil path is formed above a tapered roller bearing, and oil that has been scraped up by the ring gear is efficiently supplied to the tapered roller bearing.

JP 2010-261540 A

  By the way, when the multi-plate clutch is arranged on the axis of the drive pinion gear, it is necessary to lubricate the clutch, but the clutch is arranged further away from the taper roller bearing. It becomes difficult to supply.

  Accordingly, an object of the present invention is to provide a power transmission device that suitably lubricates a bearing that supports a drive pinion gear or the like, a multi-plate clutch that is coaxial with the bearing, and the like.

  As means for solving the above-mentioned problems, the present invention provides a first bevel gear, a second bevel gear body meshing with the first bevel gear, and a tooth surface formed on the tooth surface side of the second bevel gear body. A second bevel gear having a side shaft portion and a back side shaft portion formed on the back side of the second bevel gear body, a tooth surface side bearing that rotatably supports the tooth surface side shaft portion, and A back-side bearing that rotatably supports a back-side shaft portion, a cylindrical first rotating member that is coaxially fixed with the first bevel gear and rotates integrally with the first bevel gear, and the first rotating member A first bearing rotatably supporting the cylindrical sleeve, a cylindrical sleeve arranged coaxially with the first bevel gear, the first bevel gear, the second bevel gear, the tooth surface side bearing, the first rotation A member, a first bearing, and a case for housing the sleeve, wherein one end of the sleeve is the first The outer end of the sleeve is fixed to the case, and an outer fitting holding portion is formed on the peripheral wall portion of the sleeve. An oil reservoir for storing oil is formed at an upper portion of the peripheral wall, and a first oil passage for guiding the oil in the oil reservoir to the tooth surface side bearing is formed in the sleeve. In the two bevel gears, there is a second oil passage that opens at the tooth surface side shaft portion and the back surface side shaft portion and guides oil from the first oil passage to the back surface side of the second bevel gear body. The power transmission device is characterized by being formed.

  According to such a configuration, since the oil in the oil reservoir is guided to the tooth surface side bearing through the first oil passage, the tooth surface side bearing can be lubricated. In addition, since oil from the first oil passage is guided to the back side of the second bevel gear body through the second oil passage, devices (bearings, clutches, etc.) arranged on the back side of the second bevel gear body Can be lubricated.

  In the sleeve, a third oil passage for guiding the oil in the oil reservoir to the one end side may be formed.

  According to such a configuration, the oil in the oil reservoir is guided to the one end through the third oil passage, so that the first bearing on the one end and the differential device can be lubricated.

  The first bevel gear may be a ring gear constituting a final reduction gear, and the first rotating member may be a differential case and a differential case to which the ring gear is fixed.

  ADVANTAGE OF THE INVENTION According to this invention, the power transmission device which lubricates suitably the bearing which supports a drive pinion gear etc., the multi-plate clutch on the same axis | shaft, etc. can be provided.

It is a plane sectional view of the final reduction gear device concerning this embodiment. It is a sectional side view (X1-X1 sectional view taken on the line of FIG. 1) of the final reduction gear apparatus which concerns on this embodiment. It is a cross-sectional view (X2-X2 line sectional view of Drawing 1) of the final reduction gear device concerning this embodiment. It is a perspective view of the sleeve which concerns on this embodiment.

  An embodiment of the present invention will be described with reference to FIGS.

≪Configuration of final reduction gear≫
The final reduction gear 1 (power transmission device) according to the present embodiment is mounted on an FF (Front-engine Front-drive) -based four-wheel drive vehicle, and after decelerating the power from a propeller shaft (not shown). A device for transmitting to the left rear wheel and the right rear wheel.

  The final reduction gear 1 includes a drive pinion gear 10 (second bevel gear), a ring gear 20 (first bevel gear), a front taper roller bearing 30 (rear side bearing), and a rear taper roller bearing 40 (tooth surface side bearing). And a sleeve 50 and a case 100. The final reduction gear device 1 includes a clutch 200 and a differential device 300.

<Differential device>
The differential device 300 is a device that differentially rotates the left rear wheel and the right rear wheel. The differential device 300 includes a substantially cylindrical differential case 310 (first rotating member) that rotates about an axis O2, a pinion shaft 321 that is fixed to the differential case 310 and extends in the radial direction, and a pair that rotates about the pinion shaft 321. Pinion gears 322 and 322, and a pair of side gears 323 and 323 that mesh with the pinion gears 322 and 322.

  The differential case 310 includes a spherical shell-shaped differential case body 311, a cylindrical left boss portion 312 formed on the left side of the differential case body 311, a right boss portion 313 formed on the right side of the differential case body 311, and the differential case body 311. And a ring-shaped flange portion 314 extending radially outward from the right end portion on the drive pinion gear 10 side.

  The left boss portion 312 is rotatably supported by the second case 120 and the third case 130 via a left tapered roller bearing 330. A shim 339 for adjusting the meshing backlash between the pinion gear 11 and the ring gear 20 is interposed between the end surface of the left tapered roller bearing 330 and the second case 120 and the third case 130.

  The right boss portion 313 is rotatably supported by the sleeve 50 via a right tapered roller bearing 340. A shim 349 for adjusting the meshing backlash between the pinion gear 11 and the ring gear 20 is interposed between the end face of the right taper roller bearing 340 and the sleeve 50.

  A right end of a left rear drive shaft (not shown) extending from the left rear wheel is splined to the left side gear 323. The left end of a right rear drive shaft (not shown) extending from the right rear wheel is splined to the right side gear 323. For example, when the vehicle travels on a curve, the left and right side gears 323 and 323 rotate differentially, and the pinion gears 322 and 322 rotate.

<Drive pinion gear>
The drive pinion gear 10 is a rod-like member that rotates about an axis O1 extending in the front-rear direction. The drive pinion gear 10 includes a truncated cone-shaped pinion gear 11 (second bevel gear body) whose rear side has a small diameter, and a rear shaft portion 12 (tooth surface side shaft portion) formed on the rear side that is the tooth surface side of the pinion gear 11. ) And a front shaft portion 13 (back surface shaft portion) formed on the front side which is the back surface side of the pinion gear 11.

  The pinion gear 11 meshes with the ring gear 20, and the ring gear 20 constitutes a final reduction gear mechanism. The pinion gear 11 and the ring gear 20 are constituted by hypoid gears, for example.

  The rear shaft portion 12 is rotatably supported by the sleeve 50 via a rear taper roller bearing 40.

The front shaft portion 13 includes a proximal end portion 13a, an intermediate portion 13b, and a distal end portion 13c from the proximal end side (rear side) that is the pinion gear 11 side toward the distal end side (front side).
The base end portion 13 a is rotatably supported by the second case 120 via the front tapered roller bearing 30.

  A shaft spline 13d is formed on the outer peripheral surface of the intermediate portion 13b. The shaft spline 13d is spline-coupled with the hole spline 221 of the inner hub 220.

  The tip portion 13c supports the pump body 242 rotatably via a needle roller bearing 246 (radial bearing). The pump body 242 is supported by the clutch case 210 so as not to be relatively rotatable. For this reason, the front-end | tip part 13c and the clutch case 210 are relatively rotatable.

<Second oil passage>
A second oil passage 14 is formed in the drive pinion gear 10 to guide oil from a pipe 55b (first oil passage 55) described later to the back side of the pinion gear 11 (second bevel gear body). The second oil passage 14 includes a large diameter hole 14a extending on the axis O1 in the rear shaft portion 12, and a small diameter hole 14b extending on the axis O1 in the pinion gear 11 and the front shaft portion 13 from the front end of the large diameter hole 14a. And a radial hole 14c extending radially outward from the front end of the small diameter hole 14b (see FIG. 2).

  The rear end of the large-diameter hole 14a opens at the rear end surface of the rear shaft portion 12. The radially outer end of the radial hole 14 c is opened between the front tapered roller bearing 30 and the inner hub 220 of the clutch 200. In addition, you may form a spiral groove in the internal peripheral surface of the large diameter hole 14a and the small diameter hole 14b. The spiral direction of the spiral groove is the direction in which the oil moves forward when the drive pinion gear 10 rotates in a rotational direction corresponding to the forward direction of the vehicle. The small diameter hole 14b may have a configuration in which the diameter is increased toward the front side.

<Front taper roller bearing>
The front taper roller bearing 30 is a bearing that rotatably supports the base end portion 13 a with respect to the second case 120.

  A shim 39 for adjusting the meshing between the pinion gear 11 and the ring gear 20 is provided between the front taper roller bearing 30 and the pinion gear 11.

<Rear taper roller bearing>
The rear taper roller bearing 40 is a bearing that rotatably supports the rear shaft portion 12 with respect to the sleeve 50.

A shim 49 is disposed between the rear taper roller bearing 40 and the sleeve 50 to generate a preload on the front taper roller bearing 30 and the rear taper roller bearing 40.
With such a configuration, the shim 49 can be easily replaced by removing the sleeve 50 after removing the third case 130 even if an operation for adjusting the preload occurs. And it becomes possible to generate a preload without arrange | positioning the member which has length like a collapsible spacer.

  As described above, the drive pinion gear 10 is rotatably supported by the front taper roller bearing 30 on the front side of the pinion gear 11 and the rear taper roller bearing 40 on the rear side without using a collapsible spacer. Is shorter than the front side, the base end portion 13a is shortened.

<Ring gear>
The ring gear 20 is a ring-shaped member that rotates about an axis O2 extending in the left-right direction. The ring gear 20 is fastened to the flange portion 314 of the differential case 310 with bolts 21. Further, the lower part of the ring gear 20 is immersed in the oil reservoir 150. When the ring gear 20 rotates, the oil in the oil reservoir 150 is scraped up.

<Sleeve>
The sleeve 50 is a cylindrical member disposed coaxially with the ring gear 20 behind the drive pinion gear 10 and is a member that holds the rear taper roller bearing 40 and the right taper roller bearing 340.

  The sleeve 50 extends in the left-right direction with the axis O2 as a center, and includes a body portion 51 (peripheral wall portion), an outer fitting portion 52 (one end portion) formed on the left side (one end side) of the body portion 51, and a body portion. 51, and a sandwiched portion 53 (the other end portion) formed on the right side (the other end side) of 51. The body portion 51 is formed to be thicker than the outer fitting portion 52 and the sandwiched portion 53. Also in the trunk | drum 51, since the insertion hole 51a mentioned later is formed in the front side, it is thicker than a rear side.

<Sleeve-trunk>
An insertion hole 51 a into which the outer ring of the rear taper roller bearing 40 is inserted is formed on the front side of the body portion 51. That is, a bearing holding portion 51 b (outer fitting holding portion) including an insertion hole 51 a that fits into the rear taper roller bearing 40 is formed in a portion of the body portion 51 that is surrounded by the insertion hole 51 a. The bottom wall portion on the rear side of the bearing holding portion 51b is in contact with the rear taper roller bearing 40 and is regulated in the axial direction (front-rear direction). The center axis of the bearing holding portion 51b is coaxial with the axis O1, and is orthogonal to the axis O2 passing through the center of the body portion 51 in plan view.

<Sleeve-external fitting>
The outer fitting portion 52 is a portion that is fitted and held on the right tapered roller bearing 340.

<Sleeve-sandwiched part>
The sandwiched portion 53 is a portion that is sandwiched between the right semi-cylindrical portion 123 of the second case 120 and the right semi-cylindrical portion 131 of the third case 130 in the front-rear direction. In this way, the sleeve 50 is fixed to the case 100 by the sandwiched portion 53 being sandwiched.

  The right rear drive shaft passes through the hollow portion of the sleeve 50. That is, the space 140 between the second case 120 and the third case 130 on the outer side in the radial direction of the sleeve 50 is shielded from the rotating right rear drive shaft, so that the oil reservoir formed at the bottom of the case 100 is protected. It becomes difficult to reach the splash of oil that is being scraped. Therefore, the breather circuit may be formed by communicating the space 140 with the outside.

<Sleeve-Oil reservoir>
An oil storage chamber 54 (oil storage portion) is formed in the upper portion of the body portion 51. The oil storage chamber 54 is open at the top and is recessed on the axis O2 side (inside in the radial direction). The oil storage chamber 54 is a space for temporarily storing the oil scooped up by the ring gear 20. The oil storage chamber 54 has a rectangular shape in plan view, and is disposed approximately in the middle of the body portion 51 in the direction of the axis O2 (left-right direction).

<Sleeve-1st oil passage>
A first oil passage 55 that guides the oil in the oil storage chamber 54 to the rear taper roller bearing 40, the front taper roller bearing 30, and the clutch 200 is formed in the body portion 51 (see FIG. 2). The first oil passage 55 extends vertically downward from the front side of the bottom surface of the oil reservoir chamber 54 to the height position of the axis O1, and is inserted into the body portion 51 and extends in the front-rear direction to the lower end of the vertical hole 55a. And a pipe 55b communicating with each other.

  The front half of the pipe 55b is loosely inserted into the large-diameter hole 14a, and a cylindrical gap is formed between the pipe 55b and the large-diameter hole 14a.

<Sleeve-3rd oil passage>
A third oil passage 56 for guiding the oil in the oil storage chamber 54 to the outer fitting portion 52 side (one end portion side) is formed in the body portion 51 (see FIG. 3). The third oil passage 56 includes a through hole that extends obliquely downward to the left from the left side of the bottom surface of the oil storage chamber 54 and opens in the vicinity of the right tapered roller bearing 340.

<Case>
The case 100 is a shell-like container, and in the front-rear direction, a first case 110 disposed on the front side, a second case 120 disposed on the middle, a third case 130 disposed on the rear side, And these are fastened together by bolts or the like. An oil sump 150 (see FIG. 2) for lubricating the meshing portions of the pinion gear 11 and the ring gear 20 is formed at the bottom of the case 100.

  The first case 110 is a cylindrical member and generally accommodates the front half of the clutch 200.

  The second case 120 is a substantially cylindrical member, and has a hemispherical front case portion 121 that is open on the front side, and a rear case portion 122 that is continuous with the rear side of the front case portion 121 and is open on the rear side. And. The front case part 121 generally accommodates the rear half of the clutch 200. The rear case portion 122 generally accommodates the drive pinion gear 10, the sleeve 50, and the front half of the differential device 300.

  The third case 130 is a hemispherical shell-shaped member having an opening on the front side, and generally accommodates the sleeve 50 and the rear half of the differential device 300.

<Clutch>
The clutch 200 is a connecting / disconnecting device for connecting / disconnecting power between a propeller shaft (not shown) and the drive pinion gear 10. In this embodiment, the clutch 200 is constituted by a hydraulic wet multi-plate clutch. The clutch 200 corresponds to a clutch case 210 that rotates integrally with the propeller shaft, an inner hub 220 that rotates integrally with the drive pinion gear 10, a plurality of outer clutch plates 231, a plurality of inner clutch plates 232, and hydraulic pressure. And a hydraulic device 240 that varies the frictional force between the outer clutch plate 231 and the inner clutch plate 232.

<Clutch-Clutch case>
The clutch case 210 includes a bottomed cylindrical clutch case main body 211 whose front side is closed, and a shaft portion 212 extending forward from the front bottom portion of the clutch case main body 211. The clutch case 210 is rotatably supported by the first case 110 via a radial bearing 251.

  A shaft spline 213 is formed substantially in the middle of the shaft portion 212. A hole spline 261 of a companion flange 260 is splined to the shaft spline 213 so that the shaft portion 212 and the companion flange 260 rotate together. The companion flange 260 is a short cylindrical body extending in the direction of the axis O1, and the rear end of the propeller shaft is bolted to the front end portion thereof.

  A male screw 214 is formed at the front end portion of the shaft portion 212. A nut 262 is screwed onto the male screw 214, and a companion flange 260 is fastened to the shaft portion 212.

<Clutch-inner hub>
The inner hub 220 is a cylindrical member, and a hole spline 221 is formed on the inner peripheral surface thereof. The hole spline 221 is splined to the shaft spline 13 d of the drive pinion gear 10.

<Clutch-outer clutch plate, inner clutch plate>
The outer clutch plate 231 is a ring plate-like member, and the outer peripheral edge portion thereof is spline-coupled with the inner peripheral surface of the clutch case main body 211. Therefore, the outer clutch plate 231 and the clutch case main body 211 rotate integrally.

  The inner clutch plate 232 is a ring plate-like member, and the inner peripheral edge thereof is spline-coupled to the outer peripheral surface of the inner hub 220. Therefore, the inner clutch plate 232 and the inner hub 220 rotate integrally.

  The outer clutch plates 231 and the inner clutch plates 232 are alternately stacked in the axial direction (front-rear direction). A ring-shaped pressing plate 233 that is movable in the axial direction is arranged on the front side of the alternately laminated body.

<Clutch-hydraulic device>
The hydraulic device 240 includes a ring-shaped piston 241 and a ring-shaped pump body 242 that slidably accommodates the piston 241 in the axial direction (front-rear direction), and a ring shape between the piston 241 and the pump body 242. The oil chamber 243 is formed. The oil chamber 243 is supplied with oil from the pump 270 and pressure-adjusted by a pressure adjustment valve (not shown) in accordance with a command from an ECU (Electronic Control Unit).

  The piston 241 abuts against the pressing plate 233 via the thrust bearing 244 and is biased to return to the initial position by a disc spring 245 that functions as a return spring (return spring). When the oil pressure in the oil chamber 243 increases, the piston 241 moves backward against the spring force of the disc spring 245, and the frictional force between the outer clutch plate 231 and the inner clutch plate 232 increases, and the propeller shaft Power is transmitted to the drive pinion gear 10.

  A pump 270 is disposed between the pump body 242 and the clutch case 210. The pump 270 is formed of, for example, a Trochoid (registered trademark) pump, and includes an outer rotor 271 that rotates integrally with the clutch case 210 and an inner rotor 272 that rotates integrally with the drive pinion gear 10.

  Since the clutch case 210 rotates integrally with the propeller shaft, the clutch case 210 rotates integrally with the front wheel. Further, the drive pinion gear 10 rotates integrally with the rear wheel. Therefore, since the rotational speeds of the front wheels and the rear wheels are equal in a normal traveling state, the outer rotor 271 and the inner rotor 272 rotate integrally, and the pump 270 does not generate hydraulic pressure. However, for example, when the front wheel idles, a difference in rotational speed occurs between the outer rotor 271 and the inner rotor 272, the pump 270 generates hydraulic pressure, and the hydraulic pressure is supplied to the oil chamber 243.

≪Operation and effect of final reduction gear≫
According to the final reduction gear 1, the following effects are obtained.
The drive pinion gear 10 is configured to be rotatably supported by a rear taper roller bearing 40 on the rear side and a front taper roller bearing 30 on the front side, so that the front shaft portion 13 (back side shaft portion) is It becomes shorter than the prior art of the cantilever structure. Therefore, the drive pinion gear 10 and the case 100 can be reduced in size and weight.

  The oil scooped up from the ring gear 20 is temporarily stored in the oil storage chamber 54. The oil in the oil storage chamber 54 passes through the first oil passage 55 (vertical hole 55a, pipe 55b) and the second oil passage 14 (large diameter hole 14a, small diameter hole 14b, radial direction hole 14c), and is a front taper roller bearing. 30 and the clutch 200, which can be well lubricated.

  Further, a part of the oil from the pipe 55b passes through the gap between the pipe 55b and the large diameter hole 14a and is guided to the rear taper roller bearing 40, which can be lubricated well.

  Furthermore, the oil in the oil storage chamber 54 passes through the third oil passage 56 and is guided to the right taper roller bearing 340 so that the right taper roller bearing 340 can be well lubricated. Further, the oil from the third oil passage 56 is also supplied into the differential case 310, and the pinion gear 322, the side gear 323, and the like can be well lubricated.

≪Modification≫
As mentioned above, although one Embodiment of this invention was described, this invention is not limited to this, For example, you may change as follows.

  In the above-described embodiment, the configuration in which the power transmission device is applied to the final reduction gear 1 is illustrated, but other configurations, for example, may be applied to a transfer device (sub-transmission device). The transfer device is a device that is mounted on an FF-based four-wheel drive vehicle, branches power from the engine toward the front drive shaft, which is the drive wheel, and inputs it to the front end of the propeller shaft that extends in the front-rear direction.

  In this case, the driven-side pinion gear fixed to the front end of the propeller shaft constitutes the second bevel gear, the drive-side ring gear that rotates about the axis extending in the vehicle width direction constitutes the first bevel gear, and the ring gear The fixed ring gear shaft constitutes the first rotating member. The driven pinion gear includes a pinion gear (second bevel gear body) that meshes with the ring gear, a front shaft portion formed on the front side (tooth surface side) of the pinion gear, and a rear shaft formed on the rear side (rear side) of the pinion gear. A portion.

  A sleeve is arranged coaxially with the ring gear shaft, one end portion of the sleeve holds the ring gear shaft rotatably via the first bearing, and the other end portion of the sleeve is fixed to the case of the transfer device. Moreover, the external fitting holding | maintenance part formed in the surrounding wall part of a sleeve becomes a structure which hold | maintains a front side axial part rotatably via a tooth surface side bearing.

1 Final reduction gear (power transmission device)
10 Drive pinion gear (second bevel gear)
11 Pinion gear (second bevel gear body)
12 Rear shaft (tooth surface side shaft)
13 Front shaft (back shaft)
14 Second oil passage 14a Large diameter hole 14b Small diameter hole 14c Radial direction hole 20 Ring gear (first bevel gear)
30 Front taper roller bearing (back side bearing)
39 Shim 40 Rear taper roller bearing (tooth side bearing)
50 Sleeve 51 Body (peripheral wall)
51a Insertion hole 51b Bearing holding part (external fitting holding part)
52 Outer fitting (one end)
53 Clamped part (other end part)
54 Oil reservoir (oil reservoir)
55 1st oil path 55a Vertical hole 55b Pipe 56 3rd oil path 100 Case 200 Clutch 300 Differential gear 310 Differential case (1st rotation member)
340 Right taper roller bearing (first bearing)

Claims (3)

A first bevel gear;
A second bevel gear body meshing with the first bevel gear, a tooth surface side shaft portion formed on a tooth surface side of the second bevel gear body, and a back surface formed on a back surface side of the second bevel gear body A second bevel gear having a side shaft portion;
A tooth surface side bearing rotatably supporting the tooth surface side shaft portion;
A back side bearing that rotatably supports the back side shaft portion;
A cylindrical first rotating member, wherein the first bevel gear is fixed coaxially and rotates integrally with the first bevel gear;
A first bearing rotatably supporting the first rotating member;
A cylindrical sleeve arranged coaxially with the first bevel gear;
A case for housing the first bevel gear, the second bevel gear, the tooth surface side bearing, the first rotating member, the first bearing, and the sleeve;
With
One end of the sleeve is externally fitted and held on the first bearing,
The other end of the sleeve is fixed to the case,
On the peripheral wall portion of the sleeve, an external fitting holding portion that externally fits and holds the tooth surface side bearing is formed,
An oil reservoir for storing oil is formed at the top of the peripheral wall,
A first oil passage is formed in the sleeve for guiding the oil in the oil reservoir to the tooth surface side bearing,
In the second bevel gear, a second oil is opened at the tooth surface side shaft portion and the back surface side shaft portion, and guides oil from the first oil passage to the back surface side of the second bevel gear body. A power transmission device characterized in that a path is formed. The power transmission device according to claim 1, wherein a third oil passage is formed in the sleeve for guiding the oil in the oil reservoir to the one end side. The first bevel gear is a ring gear constituting a final reduction gear;
The power transmission device according to claim 1 or 2, wherein the first rotating member is a differential case that constitutes a differential device and to which the ring gear is fixed.

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