JP5369936B2 - Lubrication structure of power transmission device - Google Patents

Description

  The present invention relates to a lubrication structure for a power transmission device, and more particularly to a lubrication structure for a power transmission device that supplies lubricating oil to a planetary gear mechanism.

  2. Description of the Related Art Conventionally, a technique for supplying lubricating oil pumped by a pump to a power transmission device is known. For example, Patent Document 1 discloses a technique for supplying lubricating oil to a power transmission device by a hydraulic pump driven by the driving force of an engine.

JP 2007-177924 A

  However, when a predetermined travel is performed in a vehicle including an internal combustion engine and a predetermined power source that is a power source different from the internal combustion engine and capable of traveling with the power of the predetermined power source by stopping the operation of the internal combustion engine. In the lubricating oil supply method using the power of the internal combustion engine, there is a risk that insufficient lubrication will occur in the power transmission device.

  For example, when the power transmission device includes a planetary gear mechanism having a rotating member that rotates in conjunction with the rotation of the drive wheel, it is desired that the planetary gear mechanism can be supplied with lubricating oil during predetermined traveling. ing.

  SUMMARY OF THE INVENTION An object of the present invention is to provide power for a vehicle that includes an internal combustion engine and a predetermined power source that is a power source different from the internal combustion engine, and that travels by rotating drive wheels with at least one power of the internal combustion engine or the predetermined power source. And a planetary gear mechanism having a rotating member that rotates in conjunction with the rotation of the drive wheel, the power transmission device capable of supplying lubricating oil to the planetary gear mechanism during a predetermined travel. It is to provide a lubrication structure.

  A lubrication structure for a power transmission device according to the present invention includes an internal combustion engine and a predetermined power source that is a power source different from the internal combustion engine, and driving wheels are driven by at least one of the internal combustion engine and the predetermined power source. In a power transmission device provided with a planetary gear mechanism that is provided in the power transmission path of a vehicle that runs while rotating and that rotates in conjunction with rotation of the drive wheel, the planetary gear mechanism is lubricated. A lubricating structure of a power transmission device for supplying oil, which is formed on a lower side in the vertical direction of the gear, and a gear that is opposed to the planetary gear mechanism in the axial direction and rotates in conjunction with rotation of a wheel of the vehicle. , At least when the operation of the internal combustion engine is stopped and traveling with the power of the predetermined power source, the lubricating oil flows in during the predetermined travel, and the storage section that stores the flowing lubricating oil, the storage section, and the planetary gear mechanism And a first bearing that rotatably supports the rotation shaft of the gear, wherein the first bearing is supported by a wall part that forms the storage part, and a radial direction of the outer ring. A plurality of inner rings arranged radially apart from the outer ring and connected to the rotating shaft, and arranged between the raceway surface of the outer ring and the inner ring, and rolling along the raceway surface. And the lubricating oil in the reservoir is introduced into the raceway surface, and the lubricating oil in the raceway surface is sent out in the axial direction toward the planetary gear mechanism by the rolling element that rolls. It is characterized by.

  In the lubricating structure of the power transmission device of the present invention, the planetary gear mechanism has an oil passage that is connected to the lubricated portion of the planetary gear mechanism and has an opening that opens in the axial direction toward the gear. In the radial direction of the planetary gear mechanism, the rolling element is at a position corresponding to the opening.

  In the lubricating structure of the power transmission device according to the present invention, the planetary gear mechanism is connected to a lubricated portion of the planetary gear mechanism and has an oil passage having an opening that opens in an axial direction toward the gear, and the opening. And a catch plate that receives the lubricating oil that flows from the inner side to the outer side in the radial direction of the planetary gear mechanism and guides it to the oil passage. It has a region that does not face the plate in the axial direction.

  In the lubricating structure of the power transmission device of the present invention, the planetary gear mechanism includes a ring gear, a sun gear disposed coaxially with the ring gear inwardly in the radial direction of the ring gear, and the ring gear and the sun gear in the radial direction. A carrier disposed between and having a pinion gear that engages with each of the ring gear and the sun gear, and a shaft portion that rotatably supports the pinion gear, and is rotatably supported coaxially with the ring gear. The lubricated part is a bearing part that supports the pinion gear in the shaft part, and the oil passage is formed in the shaft part.

  In the lubricating structure of the power transmission device of the present invention, the gear is a counter gear that transmits the power between the rotating member and the driving wheel in the power transmission path, and in the radial direction of the counter gear, The tooth surface of the counter gear is inside in the radial direction with respect to the rolling element.

  In the lubricating structure of the power transmission device of the present invention, the gear is a counter gear that transmits the power between the rotating member and the driving wheel in the power transmission path, and a tooth surface of the counter gear includes: It faces the rolling element in the axial direction.

  In the lubricating structure of the power transmission device of the present invention, the gear is a counter gear that transmits the power between the rotating member and the driving wheel in the power transmission path, and in the radial direction of the counter gear, The tooth surface of the counter gear is outside in the radial direction with respect to the rolling element.

  In the lubricating structure for a power transmission device according to the present invention, the counter gear is a helical gear, and when the vehicle moves forward, the tooth surface in the rotational direction of the counter gear is the axial side of the first bearing side. It is characterized by facing.

  In the lubrication structure of the power transmission device of the present invention, the power transmission device further includes a discharge passage for discharging the lubricating oil in the storage portion, and the discharge passage in the radial direction of the outer ring out of the lubricating oil stored in the storage portion. The lubricating oil inside the innermost diameter of the outer ring is discharged.

  In the lubrication structure for a power transmission device according to the present invention, a side of the gear bearing opposite to the first bearing side from the storage portion is rotatably supported by a second bearing, and the second bearing Two outer rings, a second inner ring disposed radially inward of the second outer ring, and a second rolling element disposed between the second outer ring and the second inner ring, the first bearing The inner diameter of the second outer ring is smaller than the inner diameter of the first outer ring which is the outer ring.

  In the lubricating structure of the power transmission device of the present invention, the planetary gear mechanism includes a ring gear, a sun gear disposed coaxially with the ring gear inwardly in the radial direction of the ring gear, and the ring gear and the sun gear in the radial direction. A carrier disposed between and having a pinion gear that engages with each of the ring gear and the sun gear, and a shaft portion that rotatably supports the pinion gear, and is rotatably supported coaxially with the ring gear. The shaft portion is formed with an oil passage that is connected to a bearing portion that supports the pinion gear in the shaft portion and that has an opening portion that opens in the axial direction toward the gear, and the rotating member is The ring gear, and the gear is disposed coaxially with the ring gear, and is located in front of the first bearing on the rotation shaft of the gear. The planetary gear mechanism side is located on the radially inner side of the ring gear, and is connected to the ring gear so as to be integrally rotatable with a disk-like connecting member disposed coaxially with the ring gear. There is a hole through which lubricating oil can flow from the gear side in the axial direction to the opening, and the hole is formed by protruding a part of the connecting member in the axial direction toward the opening. A thrust bearing that supports the connecting member in the axial direction is held by the protruding portion of the connecting member.

  The lubricating structure of the power transmission device according to the present invention is formed on the lower side in the vertical direction of the internal combustion engine, a gear that is opposed to the planetary gear mechanism in the axial direction and that rotates in conjunction with the rotation of the wheels of the vehicle. Lubricating oil flows in during a predetermined run when the operation is stopped and the vehicle is driven by power from a predetermined power source, and is disposed between a storage unit that stores the flowing lubricating oil, and between the storage unit and the planetary gear mechanism, and the rotation of the gear And a first bearing that rotatably supports the shaft. The first bearing includes an outer ring supported by a wall portion that forms a storage portion, an inner ring that is disposed radially inward of the outer ring and spaced radially from the outer ring, is connected to a rotation shaft, and a raceway surface of the outer ring. It has a plurality of rolling elements which are arranged between the inner rings and roll along the raceway surface.

  The lubricating oil stored in the storage portion is introduced into the raceway surface of the outer ring of the first bearing, and the lubricating oil on the raceway surface is sent out in the axial direction toward the planetary gear mechanism by the rolling elements that roll. As described above, according to the lubricating structure of the power transmission device according to the present invention, the lubricating oil is sent in the axial direction toward the planetary gear mechanism by the bearing of the gear that rotates in conjunction with the rotation of the wheel, so that the predetermined traveling Sometimes lubricating oil can be supplied to the planetary gear mechanism.

FIG. 1 is a sectional view in the axial direction of a first embodiment of a lubricating structure for a power transmission device according to the present invention. FIG. 2 is a diagram showing a schematic configuration of a hybrid vehicle to which the first embodiment of the lubricating structure of the power transmission device according to the present invention is applied. FIG. 3 is a diagram showing a shaft arrangement of the power transmission device according to the first embodiment of the lubricating structure of the power transmission device according to the present invention. FIG. 4 is a diagram showing a state of supply of the lubricating oil when the lubricating oil in the oil reservoir is stirred by the counter drive gear in the first embodiment of the lubricating structure of the power transmission device according to the present invention. FIG. 5 is a diagram showing a second embodiment of the lubricating structure of the power transmission device according to the present invention. FIG. 6 is a sectional view in the axial direction of a third embodiment of the lubricating structure of the power transmission device according to the present invention. FIG. 7 is a sectional view in the axial direction of the fourth embodiment of the lubricating structure of the power transmission device according to the present invention. FIG. 8 is an axial sectional view of a fifth embodiment of the lubricating structure for the power transmission device according to the present invention. FIG. 9 is a diagram showing the rotation directions of the respective gears when the hybrid vehicle is traveling backward in the fifth embodiment of the lubricating structure for the power transmission device according to the present invention. FIG. 10 is an axial sectional view of a sixth embodiment of the lubricating structure for the power transmission device according to the present invention. FIG. 11 is a view showing a ring gear flange according to a sixth embodiment of the lubricating structure of the power transmission device according to the present invention.

  Hereinafter, an embodiment of a lubricating structure of a power transmission device according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or those that are substantially the same.

(First embodiment)
The first embodiment will be described with reference to FIGS. 1 to 4. The present embodiment relates to a lubricating structure of a power transmission device that supplies lubricating oil to a planetary gear mechanism.

  FIG. 1 is an axial sectional view showing a lubricating structure of a power transmission device according to this embodiment, and FIG. 2 is a diagram showing a schematic configuration of a hybrid vehicle to which the lubricating structure of the power transmission device according to this embodiment is applied. FIG. 3 is a diagram showing a shaft arrangement of the power transmission device according to the present embodiment.

  As shown in FIG. 2, the hybrid vehicle 10 is provided with an engine (internal combustion engine) 11 and a second motor generator (predetermined power source) 17b as travel driving sources. The engine 11 is a known internal combustion engine. An intake passage (not shown), a throttle valve for adjusting the flow rate of intake air flowing through the intake passage, a fuel injection device for injecting fuel into the intake passage, and an air-fuel mixture in the cylinder are ignited. An ignition device. The engine 11 burns an air-fuel mixture of air supplied through the intake passage and fuel supplied by the fuel injection device in a cylinder, converts the generated combustion energy into a rotational motion, and outputs it. The hybrid vehicle 10 travels by rotating the drive wheels 13 with the power of at least one of the engine 11 and the second motor generator 17b.

  The hybrid vehicle 10 is equipped with a power transmission device 50. The power transmission device 50 is provided in the power transmission path of the hybrid vehicle 10. The power transmission device 50 includes a power transmission mechanism 12 and a power split mechanism 15.

  The power generated in the engine 11 is divided into two by a power split mechanism (power combining mechanism) 15, one of its output sides is connected to a first motor generator (predetermined power source) 17a, and the other is a second motor generator 17b. And connected to the drive wheel 13. The power of the engine 11 and the power of the second motor generator 17 b are transmitted to the drive wheel 13 via the power transmission mechanism 12 and the drive shaft (drive shaft) 14.

  The first motor generator 17a and the second motor generator 17b have a function (power running function) as an electric motor driven by supply of electric power and a function (regeneration function) as a generator that converts mechanical energy into electric energy. Have both. As the first motor generator 17a and the second motor generator 17b, for example, an AC synchronous motor generator can be used. A battery 20 is mounted on the hybrid vehicle 10 as a power supply device that supplies power to the first motor generator 17a and the second motor generator 17b. The battery 20 is a chargeable / dischargeable secondary battery. The first motor generator 17 a and the second motor generator 17 b are connected to the battery 20 via the inverter 19.

  The hybrid vehicle 10 is provided with an electronic control unit (hereinafter referred to as ECU) 100 as a control means for controlling a vehicle system including the engine 11. The ECU 100 is configured by a well-known microcomputer and performs traveling control of the hybrid vehicle 10. A vehicle speed sensor, an accelerator opening sensor, and the like (not shown) are connected to an input port (not shown) of the ECU 100, and signals indicating detection results of the sensors are input to the ECU 100, respectively. Further, the engine 11, the first motor generator 17a, the second motor generator 17b, and the inverter 19 are connected to an output port (not shown) of the ECU 100, and the engine 11, the first motor generator 17a, and the second motor 19 are connected. Motor generator 17b and inverter 19 are each controlled by ECU 100.

  In the hybrid vehicle 10, the required torque to be transmitted to the drive wheels 13 is calculated based on conditions such as the vehicle speed and the accelerator opening, and the engine 11, the first motor generator 17a, and the first torque are calculated based on the calculation results. The second motor generator 17b is controlled. When transmitting the torque of the engine 11 to the drive wheels 13, the first motor generator 17 a can function as a generator, and the generated power can be charged in the battery 20.

  Further, the second motor generator 17 b can be driven as an electric motor, and the power can be transmitted to the power transmission mechanism 12. The second motor generator 17b can assist when the torque of the engine 11 is insufficient when the hybrid vehicle 10 is accelerated. In this case, the power of the engine 11 and the power of the second motor generator 17 b are combined and input to the power transmission mechanism 12. The combined power is transmitted from the drive shaft 14 to the drive wheels 13 via the power transmission mechanism 12.

  Further, the second motor generator 17b can function alone as a travel drive source of the hybrid vehicle 10. That is, the hybrid vehicle 10 is configured to be capable of EV traveling (predetermined traveling) that travels with the power of the second motor generator 17b while the engine 11 is stopped. The ECU 100 determines whether or not to perform EV traveling based on the charged state or traveling state of the battery 20, and when determining that the EV traveling is to be performed (EV traveling is possible), stops the operation of the engine 11 and performs the second operation. The hybrid vehicle 10 is driven by the power of the motor generator 17b.

  Next, with reference to FIG. 1, the detail of the lubrication structure 1-1 of the principal part of the power transmission device 50 and the power transmission device of this embodiment is demonstrated.

  In FIG. 1, the code | symbol 5 shows the input shaft into which the motive power from the engine 11 is input. The input shaft 5 is disposed coaxially with an output shaft (not shown) of the engine 11 and is connected to the output shaft, and rotates integrally with the output shaft. During operation of the engine 11, the power of the engine 11 is transmitted from the output shaft of the engine 11 to the power split mechanism 15 described later via the input shaft 5.

  The power split mechanism 15 has a so-called single pinion type planetary gear mechanism 30. The planetary gear mechanism 30 is disposed between a ring gear (rotating member) 31, a sun gear 34 disposed coaxially with the ring gear 31 radially inward of the ring gear 31, and the ring gear 31 and sun gear 34 in the radial direction, A pinion gear 32 that engages with each of the ring gear 31 and the sun gear 34 and a carrier 33 that rotatably supports the pinion gear 32 are provided.

  The ring gear 31 has a cylindrical shape with the center axis X of the input shaft 5 as the center line, and is supported rotatably about the center axis X of the input shaft 5 as the center of rotation. A hollow shaft 6 is arranged coaxially with the input shaft 5 on the radially outer side of the input shaft 5. The shaft 6 is supported by the housing 18 of the power transmission device 50 via a planetary side bearing (first bearing) 41 and an engine side bearing (second bearing) 42. A counter drive gear (gear, counter gear) 37 is formed on the shaft 6. The counter drive gear 37 is formed at the central portion of the shaft 6 in the axial direction, and protrudes outward from the shaft 6 in the radial direction. The counter drive gear 37 is opposed to the planetary gear mechanism 30 in the axial direction. The planetary side bearing 41 supports the planetary gear mechanism 30 side from the counter drive gear 37 in the shaft 6, and the engine side bearing 42 supports the engine 11 side from the counter drive gear 37 in the shaft 6.

  Each of the planetary side bearing 41 and the engine side bearing 42 is a ball bearing. The planetary bearing 41 has an outer ring (first outer ring) 41a, an inner ring 41b, and balls 41c as rolling elements. The inner ring 41b is disposed radially inward of the outer ring 41a and radially spaced from the outer ring 41a, and a plurality of balls 41c are disposed between the raceway surface 41d of the outer ring 41a and the raceway surface 41e of the inner ring 41b. Yes. The raceway surface 41d formed on the inner peripheral surface of the outer ring 41a is a groove portion having a circular arc shape that is recessed outward in the radial direction. The raceway surface 41e formed on the outer peripheral surface of the inner ring 41b is a groove having an arcuate cross section that is recessed inward in the radial direction. A plurality of balls 41c are arranged in the circumferential direction between the raceway surface 41d of the outer ring 41a and the raceway surface 41e of the inner ring 41b, and are held by the raceway surfaces 41d and 41e. When the ball 41c rotates (rolls) while moving in the circumferential direction along the raceway surfaces 41d and 41e, the inner ring 41b can rotate relative to the outer ring 41a.

  The outer ring 41 a of the planetary bearing 41 is supported by the housing 18 via the bearing support 21. The bearing support 21 has an annular shape, and the outer peripheral surface of the outer ring 41a is fitted to the inner peripheral surface of the bearing support 21 so as not to be relatively rotatable. The bearing support 21 is fixed to the housing 18 with bolts. That is, the outer ring 41a is supported by the housing 18 so as not to rotate. On the other hand, the inner ring 41 b of the planetary side bearing 41 is fitted to the outer peripheral surface of the shaft 6 so as not to be relatively rotatable. As a result, the shaft 6 is rotatably supported by the housing 18 via the planetary bearing 41.

  The configuration of the engine side bearing 42 is the same as that of the planetary side bearing 41, and includes an outer ring (second outer ring) 42a, an inner ring (second inner ring) 42b, and a ball (second rolling element) 42c. The outer ring 42 a is fitted to the housing 18 and supported so as not to rotate, and the inner ring 42 b is fitted to the shaft 6 so as not to rotate. As a result, the shaft 6 is rotatably supported by the housing 18 via the engine-side bearing 42. The input shaft 5 is supported by the shaft 6 so as to be rotatable relative to the shaft 6.

  The end of the shaft 6 on the planetary gear mechanism 30 side is located on the radially inner side of the ring gear 31 and is connected to the ring gear 31 via a ring gear flange (connecting member) 7. The ring gear flange 7 is formed in a disk shape with the central axis X of the input shaft 5 as the central axis, and the inner peripheral surface is spline-fitted to the shaft 6 and the outer peripheral surface is spline-fitted to the ring gear 31. That is, the ring gear 31 and the shaft 6 are connected via the ring gear flange 7 so as to be integrally rotatable. The ring gear flange 7 is disposed between the planetary side bearing 41 and the planetary gear mechanism 30 and faces the planetary side bearing 41 and the planetary gear mechanism 30 in the axial direction. The relative movement in the axial direction between the ring gear 31 and the ring gear flange 7 is restricted by the snap ring 8. A gear portion 31 a is formed on the inner peripheral surface of the ring gear 31. A parking gear 31 b is formed on the outer peripheral surface of the ring gear 31.

  A sun gear 34 is disposed inside the ring gear 31 in the radial direction. The sun gear 34 is arranged coaxially with the ring gear 31. The sun gear 34 is connected to the MG shaft 9 that is the rotation shaft of the first motor generator 17a. The MG shaft 9 is supported so as to be rotatable about the center axis X, and a sun gear 34 is spline-fitted to an end of the MG shaft 9 on the engine 11 side. That is, the sun gear 34 is connected to the MG shaft 9 and rotates integrally with a rotor (not shown) of the MG shaft 9, and transmits power to the first motor generator 17 a via the MG shaft 9. A gear portion 34 a is formed on the outer peripheral surface of the sun gear 34.

  The pinion gear 32 is disposed between the ring gear 31 and the sun gear 34 in the radial direction, and is engaged with the gear portion 31a of the ring gear 31 and the gear portion 34a of the sun gear 34, respectively. The pinion gear 32 is rotatably supported by a pinion shaft (shaft portion) 36 via a pinion needle bearing (bearing portion) 35. The pinion needle bearing 35 and the pinion shaft 36 form a part of the carrier 33. The carrier 33 is coupled to the input shaft 5 so as not to be relatively rotatable, and is supported so as to be rotatable integrally with the input shaft 5 with the center axis X as a rotation center. That is, the pinion gear 32 can rotate (spin) while being supported by the pinion shaft 36, and can rotate (revolve) around the central axis X.

  Here, the shaft arrangement of the power transmission device 50 will be described with reference to FIG. In FIG. 3, reference numeral 43 is a counter driven gear, 44 is a final drive pinion gear, 45 is an MG2 reduction gear, and 46 is a diff ring gear. Counter driven gear 43 meshes with counter drive gear 37 and MG2 reduction gear 45, respectively. The MG2 reduction gear 45 is connected to the rotor (not shown) of the second motor generator 17 b and transmits the power of the second motor generator 17 b to the counter driven gear 43. The power of the engine 11 and the power of the second motor generator 17 b are combined by the counter driven gear 43. The final drive pinion gear 44 is arranged coaxially with the counter driven gear 43 and rotates integrally with the counter driven gear 43. That is, the power of the engine 11 and the power of the second motor generator 17 b combined in the counter driven gear 43 are transmitted to the diff ring gear 46 through the final drive pinion gear 44.

  The diff ring gear 46 is arranged coaxially with the drive shaft 14, and the power transmitted to the diff ring gear 46 is transmitted to the drive shaft 14 via a differential mechanism (not shown). In the power transmission device 50 configured as described above, when the drive wheel 13 rotates and the drive shaft 14 rotates, the counter drive gear 37 rotates in conjunction with the rotation. That is, the counter drive gear 37 rotates in conjunction with the rotation of the drive wheel 13. Further, the ring gear 31 that rotates integrally with the counter drive gear 37 also rotates in conjunction with the rotation of the drive wheel 13. In the present embodiment, the power transmission mechanism 12 includes a counter drive gear 37, a counter driven gear 43, a final drive pinion gear 44, an MG2 reduction gear 45, and a diff ring gear 46.

  Returning to FIG. 1, when the engine 11 is operated as a power source of the hybrid vehicle 10, the power of the engine 11 is transmitted to the pinion gear 32 via the input shaft 5, the carrier 33, and the pinion shaft 36. The power transmitted to the pinion gear 32 is transmitted to the ring gear 31 and the sun gear 34. The power transmitted to the ring gear 31 is transmitted from the ring gear flange 7 and the counter drive gear 37 to the drive wheel 13 via the power transmission mechanism 12. On the other hand, the power transmitted from the pinion gear 32 to the sun gear 34 is transmitted to the first motor generator 17a via the MG shaft 9, and power is generated by the first motor generator 17a.

  When the second motor generator 17b is supplied with electric power and is driven as a drive source of the hybrid vehicle 10, the power of the second motor generator 17b is transmitted from the MG2 reduction gear 45 (see FIG. 3) to a power transmission mechanism. 12 is transmitted to the drive wheel 13 via 12.

  Next, a method for supplying lubricating oil to the planetary gear mechanism 30 will be described with reference to FIG. A shaft center oil passage (supply passage) 5 a is formed at the shaft center of the input shaft 5. Lubricating oil is supplied to the shaft center oil passage 5a from a lubricating oil storage tank and an oil pump (not shown). The storage tank is supplied with, for example, the lubricating oil that has been lifted up by the diff ring gear 46 (see FIG. 3) of the power transmission mechanism 12, and the shaft is centered from the storage tank while the engine 11 is stopped during EV traveling or the like. Lubricating oil is sent to the oil passage 5a. The oil pump is driven by the power of the engine 11 to pump the lubricating oil. The oil pump is disposed at the end of a pump drive shaft 22 that is fitted to the input shaft 5 so as to be integrally rotatable. When the engine 11 is operated and the input shaft 5 and the pump drive shaft 22 rotate, the oil pump is driven by the rotation of the pump drive shaft 22 and discharges lubricating oil toward the axial center oil passage 5a.

  The input shaft 5 is formed with a planetary-side radial oil passage 5b and an engine-side radial oil passage 5c that communicate the axial center oil passage 5a with the radially outer side of the input shaft 5 in the radial direction. The lubricating oil in the shaft center oil passage 5a flows out of the shaft center oil passage 5a through the planetary side oil passage 5b or the engine side oil passage 5c. The planetary radial oil passage 5b is formed at a position corresponding to the ring gear flange 7 in the axial direction. In other words, the planetary side radial oil passage 5 b opens in the radial direction toward the inner peripheral surface of the ring gear flange 7.

  The lubricating oil that has flowed out of the axial center oil passage 5a through the planetary radial oil passage 5b flows toward the outside in the radial direction through the gap between the input shaft 5 and the ring gear flange 7, as indicated by an arrow Y1. Here, a thrust bearing 23 that supports the ring gear flange 7 in the axial direction is provided between the input shaft 5 and the ring gear flange 7. Therefore, the thrust bearing 23 is lubricated and cooled by the lubricating oil flowing between the input shaft 5 and the ring gear flange 7. The input shaft 5 and the housing 18 are sealed by an oil seal at a position closer to the engine than the shaft 6 in the input shaft 5.

  When the input shaft 5 is rotating, such as when the engine 11 is operating, the lubricating oil is scattered from the planetary radial oil passage 5b toward the outside in the radial direction by the centrifugal force of the rotation. The parts of the planetary gear mechanism 30 and the bearings that support the input shaft 5 and the shaft 6 are lubricated and cooled by the scattered lubricating oil.

  The pinion shaft 36 is formed with a pinion lubricating oil path (oil path) 38 that guides lubricating oil to a pinion needle bearing 35 as a lubricated part. The pinion lubricating oil passage 38 includes an axial oil passage 39 formed in the axial direction on the axial center of the pinion shaft 36, and a radial oil passage 40 that communicates the axial oil passage 39 and the pinion needle bearing 35 in the radial direction. Have The shaft center oil passage 39 is formed in the axial direction in a range from the end portion on the counter drive gear 37 side of the pinion shaft 36 to the central portion in the axial direction. The shaft center oil passage 39 opens toward the counter drive gear 37, and the lubricating oil can flow into the shaft center oil passage 39 from the opening 39a. The radial oil passage 40 opens toward the inner peripheral surfaces of the pinion needle bearing 35 and the pinion gear 32. Lubricating oil that has flowed from the opening 39 a of the shaft center oil passage 39 is supplied to the pinion needle bearing 35 and the pinion gear 32 via the shaft center oil passage 39 and the radial oil passage 40. As described above, the provision of the pinion lubricating oil passage 38 facilitates the supply of the lubricating oil to the lubricated portion including the bearing portion of the pinion gear 32 (pinion needle bearing 35).

  The carrier 33 is provided with an oil catch plate 24 that receives the lubricating oil and guides it to the shaft center oil passage 39. The oil catch plate 24 is fixed to an end surface of the carrier 33 on the counter drive gear 37 side in the axial direction. The oil catch plate 24 is axially opposed to the radially outer region of the planetary gear mechanism 30 at the opening 39a of the axial oil passage 39 (the end of the axial oil passage 39 on the counter drive gear 37 side). . The outer edge portion of the oil catch plate 24 is fixed to the periphery of the opening 39 a in the carrier 33, and the portion of the oil catch plate 24 that faces the opening 39 a in the axial direction is directed toward the counter drive gear 37 in the axial direction. It protrudes. That is, the carrier 33 and the oil catch plate 24 form an oil receiving portion that opens radially inward. Lubricating oil that flows from the inner side to the outer side in the radial direction of the planetary gear mechanism 30 is received by the oil catch plate 24 and guided to the shaft center oil passage 39. Thereby, the lubricating oil that has flowed out from the axial oil passage 5a of the input shaft 5 through the planetary radial oil passage 5b can be efficiently supplied to the pinion lubricating oil passage 38.

  For example, when the input shaft 5 is rotating, lubricating oil that scatters outward in the radial direction from the planetary radial oil passage 5 b is captured by the oil catch plate 24 and flows into the shaft oil passage 39. As a result, the lubricating oil is supplied to the lubricated portions of the pinion shaft 36 and the pinion gear 32. Further, when the input shaft 5 rotates, the pinion gear 32 revolves around the center axis X as the center of rotation. Along with this, the pinion shaft 36 is immersed in the lubricating oil accumulated in the ring gear 31 and the lubricating oil flows into the shaft center oil passage 39, or the pinion gear 32 is immersed in the lubricating oil, thereby lubricating the lubricated portion. Oil is supplied.

  Here, when the rotational speed of the input shaft 5 is low, there is a possibility that the supply of lubricating oil to the lubricated parts of the pinion shaft 36 and the pinion gear 32 may be insufficient. In particular, when the engine 11 is stopped and the rotation of the input shaft 5 is stopped, such as during EV traveling, the centrifugal force does not act, so the lubricating oil flowing out from the planetary side radial oil passage 5b is laterally or vertically. It will not scatter upward in the direction. In addition, the flow rate of the lubricating oil flowing out through the planetary radial oil passage 5b is reduced, and the flow velocity is reduced. For this reason, in the supply of the lubricating oil to the pinion lubricating oil passage 38 by the lubricating oil flowing out from the planetary radial oil passage 5b, the lubricating oil tends to be insufficient in the portions to be lubricated of the pinion shaft 36 and the pinion gear 32.

  On the other hand, as a method of solving the lack of lubrication of the pinion gear 32, it is conceivable to start the engine 11 every time it travels for a certain distance or for a certain time after the start of EV travel, and perform forced lubrication by an oil pump. However, new problems such as deterioration in fuel consumption caused by starting the engine 11 only for the lubrication of the planetary gear mechanism 30 and reduction in drivability due to a start shock of the engine 11 will occur. Further, with the progress of technology such as plug-in hybrid, there is a tendency that the distance in which the EV travel can be continued in the hybrid vehicle 10, so that the coverage of the pinion shaft 36 and the pinion gear 32 is not limited by the limitation of the EV travel continuing distance. It is desired that lubricating oil can be supplied to the lubricating part.

  In the lubricating structure 1-1 of the power transmission device according to the present embodiment, the lubricating oil is discharged in the axial direction toward the pinion gear 32 by the balls 41c of the planetary bearing 41 that is rotating even during EV traveling. As a result, even during EV travel in which the rotation of the input shaft 5 is stopped, the lubricating oil is allowed to flow into the pinion lubricating oil passage 38 and sent to the lubricated portions of the pinion shaft 36 and the pinion gear 32. it can.

  The lubricating structure 1-1 of the power transmission device according to the present embodiment includes an oil reservoir 25, a planetary bearing 41, and a conduction hole 7a formed in the ring gear flange 7.

  The oil reservoir (reservoir) 25 functions as a reservoir for storing lubricating oil, and is formed by the housing 18 and the bearing support 21. The housing 18 and the bearing support 21 are opposed to each other in the axial direction with the counter drive gear 37 interposed therebetween, and are in contact with each other on the radially outer side of the counter drive gear 37. Thus, an oil reservoir 25 capable of storing lubricating oil is formed below the shaft 6 in which the counter drive gear 37 is formed in the vertical direction. The oil reservoir 25 is formed so that lubricating oil supplied to each part of the power transmission device 50 and flowing downward in the vertical direction can flow in. Further, the lubricating oil that flows out from the axial center oil passage 5 a of the input shaft 5 through the engine-side radial oil passage 5 c and lubricates the engine-side bearing 42 flows into the oil reservoir 25. As a result, the lubricating oil continuously flows into the oil reservoir 25 even during EV travel when the engine 11 is stopped.

  Since the oil reservoir 25 is formed on the engine side of the bearing support 21 that supports the planetary bearing 41, the planetary bearing 41 is located between the oil reservoir 25 and the planetary gear mechanism 30. . The engine-side bearing 42 is opposed to the planetary-side bearing 41 in the axial direction with the oil reservoir 25 interposed therebetween. That is, the engine-side bearing 42 supports the shaft 6 on the opposite side of the oil reservoir 25 from the planetary-side bearing 41 side.

  The conduction hole 7a penetrates the ring gear flange 7 in the axial direction. The conduction hole 7a is circular in cross section and has a diameter that allows the lubricating oil to flow in the axial direction. The cross-sectional shape of the conduction hole 7a is not limited to a circle, and may be an ellipse or a rectangle. The conduction hole 7a may be formed in a slit shape in the circumferential direction. The conduction hole 7 a is formed at a position corresponding to the ball 41 c of the planetary side bearing 41 in the radial direction of the planetary gear mechanism 30. In other words, the conduction hole 7a is formed at a position facing the ball 41c in the ring gear flange 7 in the axial direction. The ball 41c corresponds to the axial center oil passage 39 of the pinion shaft 36 in the radial position. That is, the shaft center oil passage 39 of the pinion shaft 36, the conduction hole 7a, and the ball 41c of the planetary bearing 41 have substantially the same diameter from the central axis X. For example, in the radial direction orthogonal to the center axis X of the input shaft 5, the center axis of the axial oil passage 39, the center axis of the conduction hole 7a, and the center of the ball 41c may be at the same position. By forming the conduction hole 7a, the ring gear flange 7 is reduced in weight.

  When the oil level of the oil reservoir 25 rises and reaches the lower end 41f in the vertical direction at the innermost diameter of the outer ring 41a of the planetary bearing 41, the lubricating oil flows between the outer ring 41a and the inner ring 41b. Thereby, the lubricating oil in the oil reservoir 25 is introduced into the raceway surface 41d of the outer ring 41a. Some of the lubricating oil that has flowed over the raceway surface 41d (groove) of the outer ring 41a flows toward the pinion shaft 36 as it is, and some lubricant oil accumulates in the groove of the raceway surface 41d. Lubricating oil collected in the grooves of the raceway surface 41d is discharged in the axial direction by centrifugal force generated by the rotation of the balls 41c moving along the raceway surface 41d. In other words, the lubricating oil accumulated in the groove of the raceway surface 41d is pressed outward in the radial direction by the centrifugal force of the ball 41c, and is sent out (discharged) in the axial direction by the pressure by the centrifugal force. That is, the lubricating oil on the raceway surface 41d is discharged in the axial direction by the pumping action of the planetary bearing 41.

  In this embodiment, the rolling element of the planetary bearing is the ball 41c, and the lubricating oil on the raceway surface 41d can be efficiently discharged in the axial direction. When the ball 41c enters the lubricating oil accumulated in the groove of the raceway surface 41d, the ball 41c rolls along the raceway surface 41d while scraping the lubricating oil in an axial direction that is a direction orthogonal to the traveling direction (circumferential direction). To go. That is, the lubricating oil collected in the groove of the raceway surface 41d is pressed between the ball 41c and the raceway surface 41d and overflows from the groove. At this time, the lubricating oil follows the raceway surface 41d having a circular arc shape in cross section. Out on both sides in the axial direction. With the momentum of this outflow, the lubricating oil scatters from the groove of the raceway surface 41d toward both sides in the axial direction. A part of the lubricating oil to be discharged advances in the axial direction toward the pinion shaft 36 as indicated by an arrow Y2. The lubricating oil traveling from the raceway surface 41 d toward the pinion shaft 36 passes through the conduction hole 7 a of the ring gear flange 7 and reaches the opening 39 a of the axial center oil passage 39 of the pinion shaft 36.

  Here, the oil catch plate 24 is formed so as not to obstruct the flow of the lubricating oil from the conduction hole 7a toward the opening 39a. That is, the oil catch plate 24 is formed so that there is a region that does not face the oil catch plate 24 in the axial direction in the opening 39a. Specifically, in the radial direction orthogonal to the central axis X of the input shaft 5, the inner diameter of the oil catch plate 24 is set in the vicinity of the central axis of the axial oil passage 39 of the pinion shaft 36. Therefore, in the radial direction orthogonal to the central axis X, the oil catch plate 24 is not opposed to the oil catch plate 24 in the radial direction inside the opening 39a, and the lubricating oil is axially blocked without being blocked by the oil catch plate 24. There is an area that can flow into.

  Since the oil catch plate 24 is configured in this way, when the engine 11 is operated, the lubricating oil flowing out from the shaft center oil passage 5a through the planetary side radial oil passage 5b is more effective by the oil catch plate 24. To the axial oil passage 39. On the other hand, during EV travel in which the operation of the engine 11 is stopped, the lubricating oil sent in the axial direction toward the pinion shaft 36 by the pumping action of the planetary bearing 41 is not obstructed by the oil catch plate 24, and the shaft center oil It can flow into the channel 39.

  Thus, the lubricating oil discharged by the pumping action of the planetary side bearing 41 is supplied to the shaft center oil passage 39 provided as a supply passage that can efficiently supply the lubricating oil to the lubricated portion during the operation of the engine 11. Since the position of the ball 41c is set so as to flow in, lubricating oil can be supplied to the lubricated portions of the pinion shaft 36 and the pinion gear 32 even during EV traveling without providing a new oil passage. By using the pinion lubricating oil path 38 as an oil path during EV traveling, it becomes possible to supply lubricating oil during EV traveling without special processing of the planetary gear mechanism 30, thereby reducing costs. Become.

  In the present embodiment, as will be described below with reference to FIG. 4, the lubricating oil in the oil reservoir 25 is agitated by the counter drive gear 37, so that the lubricating oil is efficiently directed toward the pinion shaft 36. Can send.

  FIG. 4 is a diagram illustrating a state of supply of the lubricating oil when the lubricating oil in the oil reservoir 25 is agitated by the counter drive gear 37. As shown in FIG. 4, the gear portion 37 a of the counter drive gear 37 has a larger diameter than the innermost diameter of the outer ring 41 a of the planetary bearing 41. As a result, when the lubricating oil is stored in the oil reservoir 25, the lower portion of the counter drive gear 37 in the vertical direction is immersed in the lubricating oil, and the lubricating oil is stirred. The dynamic oil level L2 of the lubricating oil agitated by the counter drive gear 37 is higher than the static oil level L1 in the vertical direction, and the lubricating oil flows between the outer ring 41a and the inner ring 41b of the planetary bearing 41. Outflow is promoted.

  The counter drive gear 37 is a helical gear, and has a twist angle in a direction in which the lubricant can be sent toward the ball 41c of the planetary bearing 41. Specifically, when the hybrid vehicle 10 moves forward, the tooth surface on the front side in the rotational direction of the gear portion 37a of the counter drive gear 37 faces the planetary bearing 41 in the axial direction. In other words, when the hybrid vehicle 10 moves forward, the tooth surface on the front side in the rotational direction of the counter drive gear 37 faces the planetary side bearing 41 in the axial direction. Thus, when the hybrid vehicle 10 moves forward, the gear portion 37 a of the counter drive gear 37 applies a thrust force toward the planetary bearing 41 in the axial direction against the lubricating oil in the oil reservoir 25. Therefore, a flow toward the planetary bearing 41 occurs in the lubricating oil in the oil reservoir 25 in the axial direction. In other words, the counter drive gear 37 can splash the lubricant on the planetary side bearing 41.

  Furthermore, as indicated by an arrow Y3, the lubricating oil that has flowed out of the axial oil passage 5a of the input shaft 5 through the engine-side radial oil passage 5c lubricates the engine-side bearing 42 and is directed to the planetary-side bearing 41. It flows into the oil reservoir 25 as a flow in the direction. Thereby, in the oil reservoir 25, the axial flow toward the planetary bearing 41 is further promoted. That is, the torsion angle of the counter drive gear 37 and the inflow path of the lubricating oil to the oil reservoir 25 function as means for promoting the flow of the lubricating oil in the axial direction toward the ball 41c of the planetary bearing 41, respectively. .

  As described above, the axial flow from the engine 11 side toward the ball 41c of the planetary bearing 41 is generated, so that the lubricating oil accumulated in the groove of the raceway surface 41d of the outer ring 41a is caused by the ball 41c to the engine 11 side (see FIG. 4), the lubricant is pushed back into the flow toward the ball 41c. Further, the lubricating oil that flows over the raceway surface 41 d and flows toward the pinion shaft 36 is pushed by the lubricating oil that is discharged in the axial direction toward the pinion shaft 36 by the pumping action of the planetary side bearing 41 toward the pinion shaft 36. It is discharged in the axial direction. As the balls 41c roll, the lubricating oil on the raceway surface 41d is sent out in the axial direction one after another, so that a continuous lubricating oil flow in the axial direction toward the pinion shaft 36 is created.

  In the present embodiment, the innermost diameter of the outer ring 42 a of the engine-side bearing 42 is smaller than the innermost diameter of the outer ring 41 a of the planetary-side bearing 41. Thereby, it is suppressed that rotating parts, such as the ball | bowl 42c of the engine side bearing 42, and the inner ring | wheel 42b, contact the lubricating oil of the oil reservoir part 25. FIG. As a result, the stirring resistance in the engine side bearing 42 can be reduced. Since the planetary bearing 41 is larger than the engine bearing 42, the parking gear 31b can be disposed on the outer periphery of the ring gear 31 of the planetary gear mechanism 30. Further, the planetary side bearing 41 is enlarged as compared with the engine side bearing 42, so that the counter drive gear 37 is twisted so that the thrust force of the counter drive gear 37 is input to the planetary side bearing 41 during forward running. It is preferable to set. In this twist direction, the splashing direction of the lubricating oil by the counter drive gear 37 is the same as the twist direction in which the planetary side bearing 41 is formed.

  As described above, according to the lubricating structure 1-1 of the power transmission device of the present embodiment, the lubricating oil in the oil reservoir 25 is supplied to the planetary-side bearing even during EV traveling when the operation of the engine 11 is stopped. 41 is discharged toward the pinion shaft 36 by the pump action, and can be supplied to the lubricated portion of the pinion shaft 36 or the pinion gear 32. Thereby, the occurrence of insufficient lubrication in the planetary gear mechanism 30 can be suppressed. Lubricating oil can be efficiently used by further using the lubricating oil that has lubricated each part of the engine side bearing 42, the planetary side bearing 41, the counter drive gear 37, and the like for the lubrication of the planetary gear mechanism 30. Loss associated with the circulation of can be reduced. Lubricating oil can be supplied to the planetary gear mechanism 30 during EV traveling without starting the engine 11. For this reason, it is possible to avoid problems such as a decrease in fuel consumption caused by operating the engine 11 to perform forced lubrication by the oil pump, a start-up shock of the engine 11, and the like.

  Further, in the lubricating structure 1-1 of the power transmission device of the present embodiment, the supply amount of the lubricating oil changes according to the rotation state of the planetary gear mechanism 30. For example, when the vehicle is traveling at a high vehicle speed, that is, when the drive wheel 13 is rotating at a high speed, the counter drive gear 37 and the pinion gear 32 are rotated at a high speed according to the rotation. On the other hand, when the vehicle is traveling at a low vehicle speed, that is, when the drive wheel 13 is rotating at a low speed, the counter drive gear 37 and the pinion gear 32 are rotated at a low speed according to the rotation. That is, the rotation speed of the pinion gear 32 and the rotation speed of the counter drive gear 37 correspond to each other. When the pinion gear 32 rotates at a high speed, the counter drive gear 37 also rotates at a high speed. When the counter drive gear 37 rotates at a high speed, the planetary bearing 41 also rotates at a high speed, and the flow rate of the lubricating oil discharged toward the pinion shaft 36 by the pump action increases as compared with the case where the counter drive gear 37 rotates at a low speed. . Thus, when the pinion gear 32 rotates at a high speed, a large amount of lubricating oil can be supplied to the pinion needle bearing 35, and the planetary gear mechanism 30 can be appropriately lubricated.

  In the present embodiment, the oil reservoir 25 is formed by the housing 18 and the bearing support 21 fixed to the housing 18. By adopting a configuration in which the bearing support 21 that supports the planetary bearing 41 is fixed to the housing 18 in the axial direction, one-way assembly of the transaxle with the housing 18 down is possible.

  In this embodiment, the rolling element of the planetary bearing 41 is the ball 41c, but the shape of the rolling element is not limited to this. The rolling element may be a tapered roller or a cylindrical roller. In other words, any shape can be used as long as it is a rolling element that can push the lubricating oil accumulated on the raceway surface in the axial direction by centrifugal force.

  In the present embodiment, the case where the predetermined power source is the motor generator has been described. However, the predetermined power source is not limited to the motor generator, and the hybrid vehicle 10 can be driven with the power of the predetermined power source by stopping the engine 11. Anything is possible. The gear that faces the planetary gear mechanism 30 in the axial direction and rotates in conjunction with the rotation of the wheel is not limited to the counter drive gear 37, and may be another gear. Furthermore, this gear does not need to rotate in conjunction with the rotation of the drive wheel 13 but may rotate in conjunction with the rotation of a wheel other than the drive wheel 13. In other words, the gear that rotates in conjunction with the rotation of the wheel may not be provided on the power transmission path.

(Modification of the first embodiment)
A modification of the first embodiment will be described. In the ring gear flange 7 of the first embodiment, the ring gear flange 7 may be formed so that more lubricating oil can be supplied to the pinion lubricating oil passage 38 through the conduction hole 7a.

  For example, a groove portion that guides the lubricating oil to the conduction hole 7 a can be formed on the surface of the ring gear flange 7 that faces the planetary bearing 41. Lubricating oil discharged toward the pinion shaft 36 by the pumping action of the planetary side bearing 41 not only flows directly into the conduction hole 7 a but also adheres to the wall surface of the ring gear flange 7. Thus, the efficiency of supplying the lubricating oil to the pinion lubricating oil passage 38 can be increased by guiding the lubricating oil adhering to the wall surface to the conduction hole 7a through the groove portion or the like. For example, a groove portion connected to the conduction hole 7 a can be formed in the circumferential direction on the engine-side wall surface of the ring gear flange 7. In this way, the lubricating oil flowing toward the outside in the radial direction along the wall surface by the centrifugal force can be captured in the groove portion and guided to the conduction hole 7a. The means for guiding the lubricating oil to the conduction hole 7a is not limited to the groove. For example, in addition to or instead of the groove portion, the ring gear flange 7 may be tapered to guide the lubricating oil to the conduction hole 7a using centrifugal force or the like.

(Second Embodiment)
A second embodiment will be described with reference to FIG. In the second embodiment, only differences from the first embodiment will be described.

  The lubrication structure 1-2 of the power transmission device according to the present embodiment is different from the lubrication structure 1-1 of the power transmission device according to the first embodiment in that a discharge path for discharging the lubricating oil is provided in the oil reservoir 25. It is a point. FIG. 5 is a diagram illustrating a lubricating structure 1-2 of the power transmission device according to the present embodiment.

  As shown in FIG. 5, the oil reservoir 25 is connected to a discharge path (discharge path) 26 that discharges the lubricating oil in the oil reservoir 25 to the outside of the oil reservoir 25. The discharge path 26 is a path that is different from the lubricating oil path formed between the outer ring 41a and the inner ring 41b of the planetary bearing 41 (a path that is discharged by the pump action). The discharge path 26 can be formed in the bearing support 21, for example.

  The discharge path 26 is formed in the horizontal direction at substantially the same position as the lower end 41f of the innermost diameter of the outer ring 41a of the planetary bearing 41 in the vertical direction. That is, the discharge path 26 discharges the lubricating oil stored in the oil reservoir 25 above the lower end in the vertical direction at the shoulder that forms the innermost diameter of the outer ring 41a of the planetary bearing 41. Can do. In other words, the discharge path 26 can discharge the lubricating oil stored in the oil reservoir 25 and radially inward from the innermost diameter of the outer ring 41 a of the planetary bearing 41. Thereby, the oil level of the oil reservoir 25 is positively controlled. An excessive increase in the oil level of the oil reservoir 25 is suppressed, and useless agitation of the lubricating oil (increase in agitation resistance) by the counter drive gear 37 can be reduced.

  The discharge path 26 guides the lubricating oil discharged from the oil reservoir 25 to the parking component. As shown in FIG. 5, each component constituting the parking brake 60 is disposed in the vicinity of the bearing support 21. The parking brake 60 includes a parking lock pole 61, a parking sleeve 62, and a parking gear 31b (see FIG. 4). When a shift lever (not shown) is moved to the parking position, the parking lock pole 61 is driven, the engaging portion 61a of the parking lock pole 61 is engaged with the parking gear 31b, and the rotation of the ring gear 31 is restricted. Lubricating oil discharged through the discharge path 26 is supplied to each operating portion and sliding portion such as the parking lock pole 61 and the parking sleeve 62. Thereby, the durability of each part of the parking brake 60 can be improved by using the lubricating oil surplus in the oil reservoir 25.

(Third embodiment)
A third embodiment will be described with reference to FIG. In the third embodiment, only differences from the above embodiments will be described.

  The lubrication structure 1-3 of the power transmission device according to this embodiment differs from the above embodiments in that the gear portion 37a of the counter drive gear 37 and the ball 41c of the planetary bearing 41 are substantially the same in the radial direction of the input shaft 5. This is the point that is the diameter. As a result, the counter drive gear 37 can smoothly supply the lubricating oil between the outer ring 41 a and the inner ring 41 b of the planetary bearing 41.

  FIG. 6 is a cross-sectional view in the axial direction showing the lubrication structure 1-3 of the power transmission device according to the present embodiment. As shown in FIG. 6, the gear portion 37a of the counter drive gear 37 faces the ball 41c of the planetary bearing 41 in the axial direction. In other words, the gear portion 37 a is formed at a position corresponding to the gap between the outer ring 41 a and the inner ring 41 b of the planetary bearing 41 in the radial direction orthogonal to the central axis X of the input shaft 5. Thereby, lubricating oil can be smoothly supplied between the outer ring | wheel 41a and the inner ring | wheel 41b. The tooth surface of the gear portion 37a directly sends out the lubricating oil toward the gap between the outer ring 41a and the inner ring 41b, so that a stronger axial lubricating oil flow toward the pinion shaft 36 can be generated. Further, the area where the counter drive gear 37 contacts the lubricant in the oil reservoir 25 can be made as small as possible, and the lubricant can be sent toward the pinion shaft 36 while reducing the stirring resistance of the counter drive gear 37.

(Fourth embodiment)
A fourth embodiment will be described with reference to FIG. In the fourth embodiment, only differences from the above embodiments will be described.

  In the lubricating structure 1-4 of the power transmission device of this embodiment, the difference from the above embodiments is that the diameter of the gear portion 37a of the counter drive gear 37 is compared with the diameter of the track of the ball 41c of the planetary bearing 41. This is a small diameter point. Thereby, the stirring resistance of the counter drive gear 37 can be reduced.

  FIG. 7 is a sectional view in the axial direction showing the lubricating structure 1-4 of the power transmission device according to the present embodiment. As shown in FIG. 7, the gear portion 37 a (tooth surface) of the counter drive gear 37 is located on the radially inner side of the ball 41 c in the radial direction orthogonal to the central axis X of the input shaft 5. Here, being inside in the radial direction from the ball 41c means being at least inside in the radial direction as compared with the center of the ball 41c, for example. In the present embodiment, the gear portion 37 a of the counter drive gear 37 is opposed to the inner ring 41 b of the planetary bearing 41 in the axial direction. In the radial direction orthogonal to the central axis X of the input shaft 5, the outer diameter of the counter drive gear 37 and the outer diameter of the inner ring 41 b of the planetary bearing 41 are substantially the same. Since the outer diameter of the counter drive gear 37 is set in this way, the counter drive gear 37 is prevented from contacting the lubricating oil stored in the oil reservoir 25. As a result, the stirring resistance of the counter drive gear 37 is reduced. Further, the smaller the diameter of the counter drive gear 37, the lower the gear ratio between the counter drive gear 37 and the counter driven gear 43 becomes. As a result, it is possible to ensure appropriate power performance even in the hybrid vehicle 10 having a heavy vehicle weight.

  In the case of the present embodiment, since the counter drive gear 37 does not contact the lubricating oil, the flow of the lubricating oil in the axial direction by the counter drive gear 37 (the flow toward the planetary bearing 41 in the oil reservoir 25) does not occur. However, an axial flow in the oil reservoir 25 is generated by the lubricating oil (arrow Y3) flowing into the oil reservoir 25. Therefore, the lubricating oil can be smoothly supplied to the pinion shaft 36.

(Fifth embodiment)
A fifth embodiment will be described with reference to FIGS. 8 and 9. In the fifth embodiment, only differences from the above embodiments will be described.

  The lubrication structure 1-5 of the power transmission device of this embodiment is different from the above embodiments in that the diameter of the counter drive gear 37 is increased. Thereby, the lubrication state of the tooth surface of the counter drive gear 37 can be kept good.

  FIG. 8 is a cross-sectional view in the axial direction showing the lubricating structure 1-5 of the power transmission device according to the present embodiment. As shown in FIG. 8, the gear portion 37 a (tooth surface) of the counter drive gear 37 is formed radially outside the ball 41 c of the planetary bearing 41 in the radial direction orthogonal to the central axis X of the input shaft 5. ing. Here, being outside in the radial direction with respect to the ball 41c means, for example, being outside in the radial direction at least compared with the center of the ball 41c. In particular, in the present embodiment, the gear portion 37 a is formed on the outer side in the radial direction than the outer ring 41 a of the planetary bearing 41. As described above, the diameter of the counter drive gear 37 is larger than the diameter of the track of the ball 41c, so that the gear portion 37a of the counter drive gear 37 is immersed in the lubricating oil in the oil reservoir 25 and the tooth surface is lubricated. Can be good. Further, the rotation of the counter drive gear 37 can generate an axial flow toward the planetary bearing 41 in the oil reservoir 25 as in the first to third embodiments.

  Further, as will be described with reference to FIG. 9, the counter driven gear 43 can be lubricated by the lubricating oil lifted up by the counter drive gear 37 during reverse travel.

  FIG. 9 is a diagram illustrating the rotation direction of each gear during reverse travel of the hybrid vehicle 10. During reverse travel, the counter drive gear 37 rotates in the direction perpendicular to the central axis X of the input shaft 5 in the direction perpendicular to the counter driven gear 43. Therefore, the lubricating oil in the oil reservoir 25 can be sent upward by the rotation of the counter drive gear 37 and applied to the counter driven gear 43 as shown by the arrow Y5. In particular, when the counter drive gear 37 has a large diameter and the distance from the bottom surface of the oil reservoir 25 is small, a lot of lubrication occurs along the inner wall surface of the oil reservoir 25 by the rotation of the counter drive gear 37. The oil can be sent upward, and the counter driven gear 43 can be efficiently lubricated.

  Further, as the diameter of the counter drive gear 37 is increased, the gear ratio between the counter drive gear 37 and the counter driven gear 43 becomes higher, and fuel consumption can be reduced.

(Sixth embodiment)
A sixth embodiment will be described with reference to FIGS. 10 and 11. In the sixth embodiment, only differences from the above embodiments will be described.

  The lubrication structure 1-6 of the power transmission device of this embodiment is different from the above embodiments in that the ring gear flange has a holding function for holding the thrust bearing 23, and the lubricating oil is supplied from the engine 11 side to the planetary side of the ring gear flange. A holding portion that also serves as a guiding function is formed. The lubricating oil is guided to the shaft center oil passage 39 of the pinion shaft 36 by the holding portion, so that the lubrication efficiency of the pinion gear 32 is increased.

  FIG. 10 is a sectional view in the axial direction showing the lubricating structure 1-6 of the power transmission device according to this embodiment, and FIG. 11 is a view showing the ring gear flange 70 of this embodiment. As shown in FIGS. 10 and 11, the ring gear flange 70 is provided with a holding portion 71. A plurality of holding portions 71 are formed in the circumferential direction at positions near the inner peripheral surface of the ring gear flange 70 in the radial direction perpendicular to the central axis X of the input shaft 5. The holding part 71 has a part of the ring gear flange 70 protruding in the axial direction by press molding or the like. The holding portion 71 is a band-like region having a predetermined length in the circumferential direction in the disk-shaped portion of the ring gear flange 70, and both ends in the circumferential direction of the holding portion 71 are continuous with the adjacent region in the circumferential direction. Both ends in the direction are discontinuous in the radial direction with respect to adjacent regions. The holding portion 71 protrudes in a U shape in the axial direction toward the planetary gear mechanism 30. That is, the holding | maintenance part 71 has comprised the shape which protrudes large in the axial direction toward the planetary gear mechanism 30 compared with the center part of the circumferential direction compared with the both ends of the circumferential direction. Since the holding portion 71 protrudes in the axial direction in this way, the ring gear flange 70 is formed with a hole 72 through which lubricating oil can flow from the axial counter drive gear 37 side to the opening 39a side. .

  The holding part 71 holds the outer diameter side of the thrust bearing 23 in the radial direction. Of the lubricating oil being stirred in the power transmission device 50, the lubricating oil that has fallen between the counter drive gear 37 and the ring gear flange 70 flows along the ring gear flange 70, as indicated by an arrow Y6 in FIG. Then, it is guided to the axial oil passage 39 of the pinion shaft 36 through the hole 72 by centrifugal force. The lubricating oil that has flowed into the hole 72 from the engine 11 side passes through the hole 72 and is discharged to the planetary side of the ring gear flange 70, and moves between the carrier 33 and the ring gear flange 70 toward the outside in the radial direction. The lubricating oil flows directly into the axial oil passage 39 of the pinion shaft 36 from the opening 39 a or is received by the oil catch plate 24 and guided to the axial oil passage 39. As a result, a lubrication path to the pinion shaft 36 can be secured and insufficient lubrication of the planetary gear mechanism 30 can be suppressed.

  By forming the hole 72 and the holding part 71 at the same time by press molding or the like, the process for forming the ring gear flange 70 is reduced as compared with the case where the hole 72 and the holding part 71 are formed in separate processes. And cost reduction is possible.

  In addition, in FIG. 11, the code | symbol 70a shows the conduction hole similar to the conduction hole 7a of the ring gear flange 7 of said each embodiment. Thus, the conduction hole 70a and the hole 72 may be provided independently, and the hole 72 and the conduction hole 70a may be made common.

1-1, 1-2, 1-3, 1-4, 1-5, 1-6 Lubricating structure of the power transmission device 5 Input shaft 5a Shaft center oil passage 5b Planetary side radial oil passage 5c Engine side radial oil Road 6 Shaft 7, 70 Ring gear flange 7a, 70a Conducting hole 10 Hybrid vehicle 11 Engine 13 Drive wheel 17b Second motor generator 18 Housing 21 Bearing support 23 Thrust bearing 24 Oil catch plate 25 Oil reservoir 26 Discharge path 30 Planetary gear mechanism 31 ring gear 32 pinion gear 35 pinion needle bearing 36 pinion shaft 37 counter drive gear 38 pinion lubricating oil passage 39 shaft center oil passage 39a opening 40 radial oil passage 41 planetary side bearing 41a outer ring 41b inner ring 41c ball 41d , 41e raceway surface 50 power transmission device 71 holding portion 72 hole portion

Claims (11)

Transmission of the power of a vehicle that includes an internal combustion engine and a predetermined power source that is a power source different from the internal combustion engine, and that travels by rotating drive wheels with the power of at least one of the internal combustion engine or the predetermined power source In a power transmission device provided with a planetary gear mechanism provided on a path and having a rotating member that rotates in conjunction with rotation of the drive wheel, the lubricating structure of the power transmission device that supplies lubricating oil to the planetary gear mechanism. There,
A gear that is axially opposed to the planetary gear mechanism and that rotates in conjunction with rotation of a wheel of the vehicle;
A storage portion that is formed on the lower side in the vertical direction of the gear and that stores lubricating oil that flows in and flows in at a predetermined time when at least the operation of the internal combustion engine is stopped and travels with the power of the predetermined power source; ,
A first bearing disposed between the storage unit and the planetary gear mechanism and rotatably supporting a rotation shaft of the gear;
The first bearing includes an outer ring supported by a wall portion that forms the storage portion, an inner ring that is radially spaced from the outer ring and is radially connected to the outer ring, and is connected to the rotating shaft. A plurality of rolling elements that are disposed between the raceway surface of the outer ring and the inner ring and roll along the raceway surface;
Lubricating oil in the reservoir is introduced into the raceway surface, and the lubricating oil on the raceway surface is sent out in the axial direction toward the planetary gear mechanism by the rolling elements that roll. Lubrication structure. In the lubricating structure of the power transmission device according to claim 1,
The planetary gear mechanism has an oil passage that is connected to a lubricated portion of the planetary gear mechanism and has an opening that opens in an axial direction toward the gear.
The lubrication structure for a power transmission device, wherein the rolling element is in a position corresponding to the opening in a radial direction of the planetary gear mechanism. In the lubricating structure of the power transmission device according to claim 1 or 2,
The planetary gear mechanism is provided with an oil passage that is connected to the lubricated portion of the planetary gear mechanism and has an opening that opens in the axial direction toward the gear, and is opposed to the opening in the axial direction. A catch plate that receives the lubricating oil flowing from the radially inner side to the outer side of the planetary gear mechanism and guides it to the oil passage;
The opening has a region that is not opposed to the catch plate in the axial direction. In the lubricating structure of the power transmission device according to claim 2 or 3,
The planetary gear mechanism is arranged between a ring gear, a sun gear coaxially arranged with the ring gear inwardly in the radial direction of the ring gear, and between the ring gear and the sun gear in the radial direction, and the ring gear and the A pinion gear that engages with each of the sun gears, a shaft portion that rotatably supports the pinion gear, and a carrier that is rotatably supported coaxially with the ring gear;
The lubricated part is a bearing part that supports the pinion gear in the shaft part,
The oil passage is formed in the shaft portion. A lubricating structure for a power transmission device, wherein: In the lubricating structure of the power transmission device according to any one of claims 1 to 4,
The gear is a counter gear that transmits the power between the rotating member and the drive wheel in the power transmission path,
A lubricating structure for a power transmission device, wherein a tooth surface of the counter gear is located on an inner side of the rolling element in a radial direction in the radial direction of the counter gear. In the lubricating structure of the power transmission device according to any one of claims 1 to 4,
The gear is a counter gear that transmits the power between the rotating member and the drive wheel in the power transmission path,
A lubricating structure for a power transmission device, wherein a tooth surface of the counter gear faces the rolling element in an axial direction. In the lubricating structure of the power transmission device according to any one of claims 1 to 4,
The gear is a counter gear that transmits the power between the rotating member and the drive wheel in the power transmission path,
A lubricating structure for a power transmission device, wherein a tooth surface of the counter gear is located on an outer side in a radial direction with respect to the rolling element in a radial direction of the counter gear. In the lubricating structure of the power transmission device according to claim 6 or 7,
The counter gear is a helical gear, and when the vehicle moves forward, the tooth surface in the front direction of rotation of the counter gear faces the first bearing side in the axial direction. Lubrication structure of the device. In the lubricating structure of the power transmission device according to any one of claims 5 to 8,
Furthermore, a discharge path for discharging the lubricating oil of the storage unit is provided,
The lubricating structure of the power transmission device according to claim 1, wherein the discharge passage discharges the lubricating oil stored in the storage portion inside the innermost diameter of the outer ring in the radial direction of the outer ring. In the lubricating structure of the power transmission device according to any one of claims 1 to 9,
In the bearing of the gear, the side opposite to the first bearing side than the storage portion is rotatably supported by a second bearing,
The second bearing includes a second outer ring, a second inner ring disposed radially inward of the second outer ring, and a second rolling element disposed between the second outer ring and the second inner ring. Have
The lubrication structure for a power transmission device, wherein an inner diameter of the second outer ring is smaller than an inner diameter of a first outer ring that is the outer ring of the first bearing. In the lubricating structure of the power transmission device according to any one of claims 1 to 10,
The planetary gear mechanism is arranged between a ring gear, a sun gear coaxially arranged with the ring gear inwardly in the radial direction of the ring gear, and between the ring gear and the sun gear in the radial direction, and the ring gear and the A pinion gear that engages with each of the sun gears, a shaft portion that rotatably supports the pinion gear, and a carrier that is rotatably supported coaxially with the ring gear;
The shaft portion is formed with an oil passage that is connected to a bearing portion that supports the pinion gear in the shaft portion and has an opening portion that opens in an axial direction toward the gear,
The rotating member is the ring gear;
The gear is disposed coaxially with the ring gear,
The planetary gear mechanism side of the rotating shaft of the gear is integrated with the ring gear by a disk-shaped connecting member that is positioned radially inward of the ring gear and coaxial with the ring gear. It is connected rotatably
The connecting member has a hole through which lubricating oil can flow from the gear side in the axial direction to the opening side, and the hole protrudes a part of the connecting member in the axial direction to the opening side. And a thrust bearing that supports the connecting member in the axial direction is held by the protruding portion of the connecting member.

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