JP2010203588A - Lubricating structure for planetary gear mechanism - Google Patents

Abstract

Provided is a planetary gear mechanism lubrication structure capable of suppressing insufficient lubrication of a pinion gear even when the rotation speed of a carrier is low.
A planetary gear mechanism lubrication structure 1-1, in which a planetary gear mechanism 30 includes a ring gear 31 that rotates in conjunction with a drive shaft, a sun gear 34, a pinion gear 32 that engages with the ring gear and the sun gear, And a carrier 33 that rotatably supports the pinion gear, projects radially inward from the inner peripheral surface 31a of the ring gear, and corresponds to the pair of wall portions 7 and 50 facing each other in the axial direction and the radial pinion gear. A pinion side through hole 52 that penetrates the wall portion 50 in the axial direction at a position and opens into the space portion 51 formed by the pair of wall portions and the inner peripheral surface, and the space portion from the inside in the radial direction than the pinion gear And a supply passage 5a for supplying lubricating oil to the inner surface and a closing member connected to the inner peripheral surface and the pair of wall portions in the space portion to close the space portion and rotate integrally with the ring gear.
[Selection] Figure 1

Description

  The present invention relates to a lubrication structure for a planetary gear mechanism, and more particularly to a lubrication structure for a planetary gear mechanism that supplies lubricating oil to a pinion gear of the planetary gear mechanism.

  Conventionally, a lubricating structure for supplying lubricating oil to a lubricated portion of a planetary gear mechanism has been proposed. For example, Patent Document 1 discloses a lubricating device for a vehicle hub reducer that supplies lubricating oil to a pinion gear bearing by the centrifugal force of rotation of a planetary carrier.

Japanese Utility Model Publication No. 6-32801

  When lubricating oil is supplied to the pinion gear by rotation of the carrier as in Patent Document 1, when the rotational speed of the carrier is low (including the case where the rotation of the carrier is stopped), the lubricating oil can be appropriately supplied to the pinion gear. Insufficient lubrication may occur.

  An object of the present invention is to provide a lubricating structure of a planetary gear mechanism that can supply lubricating oil to a pinion gear and suppress insufficient lubrication in the pinion gear even when the rotation speed of the carrier is low.

  The lubrication structure of the planetary gear mechanism of the present invention is a lubrication structure of a planetary gear mechanism that transmits power to the drive shaft, and the planetary gear mechanism is an output member of the power, and is interlocked with the drive shaft. A rotating ring gear, a sun gear disposed coaxially with the ring gear radially inward of the ring gear, and disposed between the ring gear and the sun gear in the radial direction, and each of the ring gear and the sun gear The ring gear includes an engaging pinion gear and a carrier that rotatably supports the pinion gear and that is rotatably supported coaxially with the ring gear, and is provided on one side of the pinion gear in the axial direction. A pair of wall portions projecting radially inward from the inner peripheral surface of the inner wall and facing each other in the axial direction, and before facing the pinion gear in the axial direction Pinion-side penetration formed in the wall and penetrating through the wall in the axial direction at a position corresponding to the pinion gear in the radial direction and opening into a space formed by the pair of walls and the inner peripheral surface A hole, a supply passage for supplying lubricating oil to the space from the inside in the radial direction of the pinion gear, and the space connected to the inner peripheral surface and the pair of walls to close the space. And a closing member that rotates integrally with the ring gear.

  In the lubricating structure of the planetary gear mechanism according to the present invention, the opening portion of the pinion side through hole is sandwiched in the circumferential direction by the pair of blocking members in the space portion.

  In the planetary gear mechanism lubrication structure of the present invention, the wall portion is further formed on the wall portion facing the lubrication portion different from the pinion gear in the axial direction, and the wall portion is disposed at a position corresponding to the lubrication portion in the radial direction. A lubricated portion side through hole penetrating in the axial direction, the pinion side through hole and the lubricated portion side through hole are different in radial position, and the space portion is surrounded by a pair of blocking members. A first space part that is sandwiched in a direction and connected to the pinion side through hole and not connected to the lubricated part side through hole, and a pair of the closing members, and is sandwiched in the circumferential direction, and the lubricated part side It has a 2nd space part which is connected with a through-hole and is not connected with the said pinion side through-hole.

  In the lubrication structure of the planetary gear mechanism of the present invention, the space portions are adjacent to each other in the circumferential direction by the plurality of closing members arranged in the circumferential direction, and each of the space portions is formed by a pair of the blocking members. The closing member that is partitioned into a plurality of subspace portions sandwiched in the circumferential direction and partitions the subspace portions adjacent to each other communicates the subspace portion on one side and the subspace portion on the other side in the circumferential direction. And the communicating hole which can distribute | circulate lubricating oil is formed, It is characterized by the above-mentioned.

  In the planetary gear mechanism lubrication structure of the present invention, the planetary gear mechanism includes an internal combustion engine as a drive source and a second drive source different from the internal combustion engine, and stops the internal combustion engine to The hybrid vehicle is mounted on a hybrid vehicle capable of a predetermined travel that travels with the power of the second drive source, and transmits the power of the internal combustion engine to the drive shaft. The carrier is connected to the output shaft of the internal combustion engine. And rotating integrally with the output shaft.

  A planetary gear mechanism lubrication structure according to the present invention includes a pair of wall portions provided on one axial side of the pinion gear, projecting radially inward from the inner peripheral surface of the ring gear, and facing each other in the axial direction. , Formed in a wall portion facing the pinion gear in the axial direction, penetrating the wall portion in the axial direction at a position corresponding to the radial pinion gear, and opened in a space formed by the pair of wall portions and the inner peripheral surface A pinion side through hole and a supply passage for supplying lubricating oil to the space from the inside in the radial direction of the pinion gear. The ring gear rotates in conjunction with the drive shaft. The lubricating oil supplied to the space portion rotates in the same rotational direction as the ring gear, and is ejected from the pinion side through hole toward the pinion gear by obtaining a hydraulic head difference due to centrifugal force.

  The space portion is provided with a closing member that is connected to the inner peripheral surface and the pair of wall portions, closes the space portion, and rotates integrally with the ring gear. Since the movement of the lubricating oil in the circumferential direction is promoted by the closing member, a large centrifugal force acts on the lubricating oil. Therefore, the lubricating oil in the space can reach the upper part in the vertical direction, and the lubricating oil ejected from the pinion side through hole can be supplied to the pinion gear in the upper part in the vertical direction. Thereby, even if the rotation speed of the carrier is low, insufficient pinion gear lubrication is suppressed. For example, when the carrier is stopped, the lubricating oil can be supplied to the pinion gear rotating at the upper position in the vertical direction through the pinion side through hole.

FIG. 1 is an axial sectional view showing a power split mechanism to which a first embodiment of a lubricating structure for a planetary gear mechanism of the present invention is applied. FIG. 2 is a view showing a schematic configuration of a hybrid vehicle equipped with a power split mechanism to which the first embodiment of the planetary gear mechanism lubrication structure of the present invention is applied. FIG. 3 is a radial sectional view showing the first embodiment of the lubricating structure of the planetary gear mechanism of the present invention. FIG. 4 is a radial cross-sectional view showing a modification of the first embodiment of the lubricating structure of the planetary gear mechanism of the present invention. FIG. 5 is a radial cross-sectional view showing a second embodiment of the lubricating structure of the planetary gear mechanism of the present invention. FIG. 6 is a radial cross-sectional view showing a third embodiment of the lubricating structure of the planetary gear mechanism of the present invention. FIG. 7 is a radial cross-sectional view showing an example of a lubrication structure in which the radial positions of the pinion side through hole and the bearing side through hole are different in the lubrication structure of the planetary gear mechanism of the present invention. . FIG. 8 is an axial sectional view showing a fourth embodiment of the lubricating structure of the planetary gear mechanism of the present invention. FIG. 9 is a radial sectional view showing a fourth embodiment of the lubricating structure of the planetary gear mechanism of the present invention.

  Hereinafter, one embodiment of a lubricating structure for a planetary gear mechanism 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 3. The present embodiment relates to a lubrication structure of a planetary gear mechanism that supplies lubricating oil to a pinion gear of the planetary gear mechanism. FIG. 1 is an axial sectional view showing a power split mechanism to which a first embodiment of a planetary gear mechanism lubrication structure according to the present invention is applied, and FIG. 2 is an application of the planetary gear mechanism lubrication structure of the present embodiment. FIG. 3 is a schematic cross-sectional view showing a lubricating structure of the planetary gear mechanism of the present embodiment.

  In the planetary gear mechanism lubrication structure (see reference numeral 1-1 in FIG. 1) of the present embodiment, an oil plate (see FIG. 1) is provided on the inner peripheral surface (see reference numeral 31a in FIG. 1) of the ring gear (see reference numeral 31 in FIG. 1). 50), and a space (see reference numeral 51 in FIG. 1) as an oil reservoir is provided. A pinion side through-hole (see reference numeral 52 in FIG. 1) is formed as an oil ejection hole on the inner diameter side of the pinion gear (see reference numeral 32 in FIG. 1) slightly in the oil plate 50. When the ring gear 31 rotates, lubricating oil accumulated by centrifugal force is ejected from the pinion side through hole 52 by obtaining a water head difference in the space 51 (see arrow Y1 in FIG. 1), and the pinion gear 32 is lubricated. . Thereby, even when the rotational speed of the carrier (see reference numeral 33 in FIG. 1) is low during EV traveling, insufficient lubrication in the pinion gear 32 can be suppressed.

  As shown in FIG. 2, the hybrid vehicle 10 is provided with an engine (internal combustion engine) 11 and a second motor generator (second drive source) 17b as travel driving sources.

  The driving force generated in the engine 11 is divided into two by a power split mechanism (power combining mechanism) 15, one of the output sides thereof is connected to a first motor generator (rotary electric machine) 17a, and the other is a second motor generator 17b. And connected to the drive wheel 13. The driving force of the engine 11 and the driving force 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.

  Next, the details of the lubricating structure 1-1 of the planetary gear mechanism of the present embodiment will be described with reference to FIG.

  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 rotates the ring gear 31, a sun gear 34 disposed coaxially with the ring gear 31 radially inward of the ring gear 31, a pinion gear 32 engaged with each of the ring gear 31 and the sun gear 34, and the pinion gear 32. And a supportable carrier 33.

  The ring gear 31 has a cylindrical shape and is supported so as to be rotatable about the central axis X of the input shaft 5 as a rotation center. A hollow shaft 6 is disposed outside the input shaft 5 in the radial direction. The shaft 6 is supported by a case 18 that accommodates the transaxle of the hybrid vehicle 10 including the planetary gear mechanism 30 via the ball bearing 16. The ball bearing 16 supports the shaft 6 so as to be rotatable from the outside in the radial direction, and faces the ring gear flange 7 described later in the axial direction. The shaft 6 is arranged coaxially with the input shaft 5 and is configured to be rotatable relative to the input shaft 5.

  A ring gear flange 7 formed in an annular shape is connected to the outer side in the radial direction of the shaft 6. The ring gear flange 7 is spline-fitted with the shaft 6 at the radially inner end, and rotates integrally with the shaft 6. The ring gear 31 is connected to the radially outer end of the ring gear flange 7. Specifically, the radially outer end (outer peripheral portion) of the ring gear flange 7 is spline fitted to the inner peripheral surface 31 a of the ring gear 31, and the ring gear 31 rotates integrally with the ring gear flange 7. That is, the shaft 6, the ring gear flange 7, and the ring gear 31 rotate integrally. 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 b is formed on the inner peripheral surface 31 a 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 the sun gear 34 is spline-fitted to an end of the MG shaft 9 on the engine side. That is, the sun gear 34 is connected to the MG shaft 9 and rotates integrally with 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 31b 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 36 via a pinion needle bearing 35. Further, the pinion shaft 36 is rotatably supported by the carrier 33. The carrier 33 is connected to the input shaft 5 and rotates integrally with the input shaft 5 about the center axis X. 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.

  A counter drive gear 37 is formed on the outer peripheral surface of the ring gear 31. The counter drive gear 37 is engaged with the power transmission mechanism 12 and transmits power to and from the power transmission mechanism 12. That is, the ring gear 31 functions as a power output member in the planetary gear mechanism 30. Further, the counter drive gear 37 is configured to rotate in conjunction with the drive shaft 14, and always rotates when the hybrid vehicle 10 travels. The counter drive gear 37 is also engaged with a rotation shaft (not shown) of the second motor generator 17b separately from the power transmission mechanism 12, and between the rotation shaft of the second motor generator 17b. Transmit power.

  When the engine 11 is operated as a drive 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 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 17 b is supplied with electric power and is driven as a drive source of the hybrid vehicle 10, the power of the second motor generator 17 b is transmitted to the power transmission mechanism 12 via the counter drive gear 37. Is done. That is, the power of the engine 11 and the power of the second motor generator 17 b are combined by the counter drive gear 37 and transmitted to the power transmission mechanism 12.

  Next, the lubricating structure 1-1 of the planetary gear mechanism will be described. 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 oil passage 5a from a lubricating oil storage tank (not shown). The storage tank is supplied with, for example, lubricating oil that has been lifted up by a final ring gear (not shown) of the power transmission mechanism 12, and shaft oil from the storage tank while the engine 11 is stopped during EV traveling or the like. Lubricating oil is sent to the path 5a. The input shaft 5 is formed with a radial oil passage (supply port) 5b that communicates the axial center oil passage 5a and the radially outer side of the input shaft 5 in the radial direction, and lubricates the inside of the shaft center oil passage 5a. The oil flows out of the axial oil passage 5a through the radial oil passage 5b. The radial oil passage 5 b is formed on the same side in the axial direction as the ring gear flange 7 with respect to the pinion gear 32. Further, since the input shaft 5 is located radially inward of the pinion gear 32, the radial oil passage 5 b supplies lubricating oil from the radially inner side of the pinion gear 32.

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

  The pinion shaft 36 is formed with a pinion lubricating oil passage 38 that guides the lubricating oil to the lubricated portion of the pinion gear 32. The pinion lubricating oil passage 38 includes an axial oil passage 39 formed in the axial direction on the axis of the pinion shaft 36, and a radial oil passage 40 that communicates the axial oil passage 39 and the pinion gear 32 in the radial direction. . The axial center oil passage 39 is formed in the axial direction in a range from the end portion on the ring gear flange 7 side of the pinion shaft 36 to the central portion in the axial direction. The shaft center oil passage 39 opens toward the ring gear flange 7, and lubricating oil can flow into the shaft center oil passage 39 from the opening 39 a. 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 makes it relatively easy to supply the lubricating oil to the lubricated portion including the bearing portion (pinion needle bearing 35) of the pinion gear 32.

  For example, when the input shaft 5 is rotating, lubricating oil that scatters outward in the radial direction from the radial oil passage 5b flows into the axial oil passage 39, so that the portion to be lubricated of the pinion gear 32 is lubricated. Is supplied with lubricating oil. 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 axial center oil passage 39, or the pinion gear 32 is immersed in the lubricating oil, so that the pinion gear 32 is lubricated. Lubricating oil is supplied to the part.

  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 portion of the pinion gear 32 is 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 lubricating oil does not scatter from the radial oil passage 5b, and the pinion gear 32 does not revolve. For this reason, in the method of supplying the lubricating oil to the shaft center oil passage 39 by the scattering of the lubricating oil and supplying the lubricating oil by immersing the pinion gear 32 or the pinion shaft 36 in the lubricating oil, in the lubricated portion of the pinion gear 32 It becomes easy to run out of lubricating oil. In particular, in the pinion gear 32 that rotates at the top in the vertical direction, the supply amount of the lubricating oil tends to be insufficient.

  On the other hand, as a method of solving the lack of lubrication of the pinion gear 32, an oil pump that starts the engine 11 when the vehicle has traveled a certain distance after starting EV traveling or supplies lubricating oil to the lubricated portion of the pinion gear 32 Measures such as adding can be considered. However, with the progress of technology such as plug-in hybrids, the distance that can continue EV travel tends to increase in the hybrid vehicle 10, and therefore the lubrication oil is applied to the lubricated portion of the pinion gear 32 without being limited by the EV travel distance. It is desirable to be able to supply In addition, the addition of an oil pump leads to an increase in cost, an increase in weight, and the like.

  In the lubrication structure of the planetary gear mechanism of the present embodiment, as will be described below, the lubricating oil is supplied to the lubricated portion of the pinion gear 32 with a simple configuration regardless of the EV travel distance, and lubrication in the pinion gear 32 is performed. The shortage can be suppressed.

  As shown in FIG. 1, an oil plate 50 is provided on the inner peripheral surface 31 a of the ring gear 31. The oil plate 50 is a plate-like member and is disposed between the ring gear flange 7 and the pinion shaft 36 in the axial direction. The outer peripheral portion of the oil plate 50 is fixed to the inner peripheral surface 31 a of the ring gear 31. The oil plate 50 constitutes a wall portion that protrudes radially inward from the inner peripheral surface 31 a of the ring gear 31. That is, the ring gear flange 7 and the oil plate 50 form a pair of wall portions that protrude radially inward from the inner peripheral surface 31a of the ring gear 31 on one side in the axial direction of the pinion gear 32 and that face each other in the axial direction. ing. Further, the radially inner end (inner peripheral surface) of the oil plate 50 is located radially inward of the axial oil passage 39 of the pinion shaft 36. In other words, the oil plate 50 faces the opening 39 a of the axial oil passage 39 in the axial direction, and separates the opening 39 a and the ring gear flange 7.

  By providing the oil plate 50, the inner peripheral surface 31 a of the ring gear 31, the oil plate 50, and the ring gear flange 7 constitute a space portion 51 that functions as a storage portion that stores lubricating oil. As will be described below, the space 51 is connected to through holes 52 and 53 for ejecting lubricating oil.

  The oil plate 50 is formed with a pinion side through hole 52 that penetrates the oil plate 50 in the axial direction. The pinion side through hole 52 is open to the space 51 and communicates the space 51 side of the oil plate 50 and the pinion gear 32 side. The radial position of the pinion side through hole 52 in the oil plate 50 corresponds to the radial position of the pinion gear 32. More specifically, the radial position of the pinion side through hole 52 is a position corresponding to the axial center oil passage 39. For example, when the axial center oil passage 39 and the circumferential phase coincide with each other, the axial center oil passage It is a position (for example, a position on the same axis) opposite to 39 in the axial direction. That is, the radial position of the pinion side through hole 52 is such that when the lubricating oil stored in the space 51 is ejected through the pinion side through hole 52, the ejected lubricating oil flows into the shaft center oil passage 39. It is set to the position to perform. For example, the pinion side through hole 52 can be arranged such that the central axis of the pinion side through hole 52 is located radially inside the central axis of the axial center oil passage 39.

  The ring gear flange 7 is formed with a bearing-side through hole 53 that penetrates the ring gear flange 7 in the axial direction. The bearing-side through hole 53 supplies lubricating oil to the ball bearing 16 that is a portion to be lubricated different from the pinion gear 32. The radial position of the bearing side through hole 53 in the ring gear flange 7 is a position corresponding to the ball bearing 16, for example, a position facing the ball bearing 16 in the axial direction. In other words, the radial position of the bearing-side through-hole 53 is the position where the lubricating oil stored in the space 51 is ejected through the bearing-side through-hole 53 and the sprayed lubricating oil is applied to the ball bearing 16. Is set to

  Next, a method for supplying lubricating oil by the lubricating structure of the planetary gear mechanism of the present embodiment, particularly when the rotation speed of the input shaft 5 is low (including the case where the rotation of the input shaft 5 is stopped) will be described.

  Lubricating oil that flows out of the input shaft 5 from the axial oil passage 5 a of the input shaft 5 through the radial oil passage 5 b flows into the space 51. The lubricating oil flowing out from the radial oil passage 5b flows downward in the vertical direction by gravity, for example, and flows into the space 51. As shown in FIG. 1, the radial oil passage 5 b overlaps with the ring gear flange 7 in the axial direction. Therefore, when the lubricating oil flows out from the radial oil passage 5 b, the lubricating oil is spaced along the ring gear flange 7. Guided to part 51. Further, when the input shaft 5 is rotating, the lubricating oil scattered from the radial oil passage 5 b toward the radially outer side flows into the space 51.

  As will be described below, the lubricating oil that has flowed into the space 51 rotates around the central axis X by receiving a circumferential force. The ring gear 31 rotates in conjunction with the drive shaft 14, and always rotates during traveling regardless of whether the vehicle is traveling EV. Therefore, the ring gear flange 7 and the oil plate 50 connected to the inner peripheral portion 31a of the ring gear 31 are always rotated integrally with the ring gear 31 during traveling. For this reason, the circumferential direction (rotation direction) force (shearing force) acts on the lubricating oil in the space 51 from the inner peripheral surface 31 a of the ring gear 31, the ring gear flange 7, or the oil plate 50. The lubricating oil in the space 51 that receives the circumferential force rotates in the same rotational direction as the ring gear 31. Since centrifugal force acts on the rotating lubricating oil, as shown in FIG. 1, the lubricating oil stays in the space 51 without dropping even in the vertical direction above the central axis X, and rotates together with the ring gear 31.

  When the amount of lubricating oil in the space 51 is increased and the oil level is increased, and the position of the oil surface B is radially inward from the pinion side through hole 52 and the bearing side through hole 53, the oil surface B and the through hole 52 are provided. , 53, a head difference due to centrifugal force occurs.

  Lubricating oil in the space 51 is ejected in the axial direction from the pinion side through hole 52 and the bearing side through hole 53 due to a water head difference. Even if the pinion side through hole 52 and the bearing side through hole 53 are vertically above the center axis X by obtaining the water head difference due to centrifugal force, the lubricating oil in the space 51 passes through the pinion side. It can be ejected from the hole 52 and the bearing side through hole 53. As indicated by the arrow Y 1, the lubricating oil ejected from the space 51 through the pinion side through hole 52 flows into the axial oil passage 39 of the pinion shaft 36. The lubricating oil that has flowed into the shaft center oil passage 39 is supplied to the pinion gear 32 and the pinion needle bearing 35 via the radial oil passage 40. Thereby, when the rotational speed of the input shaft 5 is low, for example, even when the rotation of the input shaft 5 is stopped during EV traveling and the pinion gear 32 is not revolving, the pinion gear rotating at the top in the vertical direction. Lubricating oil can be supplied to the 32 parts to be lubricated to suppress insufficient lubrication. Since the lubricating oil supply method uses the rotation of the ring gear 31 that is always rotating in conjunction with the drive shaft 14 during traveling, the lubricating oil can be supplied to the pinion gear 32 regardless of the EV traveling distance. .

  Further, the lubricating oil (see arrow Y <b> 2) ejected from the space portion 51 through the bearing side through hole 53 is supplied to the ball bearing 16. Thereby, when the rotational speed of the input shaft 5 is low, for example, the rotation of the input shaft 5 is stopped during EV travel, and even if the pinion gear 32 is not revolving, insufficient lubrication in the ball bearing 16 is suppressed. It becomes possible.

  Moreover, the lubrication structure 1-1 of the planetary gear mechanism of the present embodiment includes a partition plate that partitions the space 51 in the circumferential direction, as will be described below with reference to FIG. Thereby, the centrifugal force transmission efficiency to lubricating oil improves.

  In FIG. 3, the code | symbol 41 shows a partition plate (blocking member). The partition plate 41 is provided in the space 51, is connected to the inner peripheral surface 31 a of the ring gear 31, the oil plate 50, and the ring gear flange 7, closes the space 51, and rotates integrally with the ring gear 31. In the present embodiment, the partition plate 41 is a plate-like member and is provided at both ends in the circumferential direction of the space 51. The partition plate 41 projects radially inward from the inner peripheral surface 31a of the ring gear 31 and connects the ring gear flange 7 and the oil plate 50 in the axial direction. That is, the partition plate 41 closes the space 51 between the ring gear flange 7 and the oil plate 50, and one side in the circumferential direction of the partition plate 41 is the space 51 and the other side is the outside of the space 51. Yes. In other words, the space 51 is formed by the inner peripheral surface 31 a of the ring gear 31, the ring gear flange 7, the oil plate 50, and the pair of partition plates 41.

  When the lubricating oil supplied from the shaft center flows into the space 51 as shown by the arrow Y3, the force from the partition plate 41 acts on the lubricating oil in the space 51 as shown by the arrow Y4. A circumferential (rotational direction) force acts on the lubricating oil from the wall surface 41a in the rotational direction of the partition plate 41, and the circumferential movement of the lubricating oil around the central axis X is promoted. Therefore, the lubricating oil in the space 51 can be rotated at substantially the same speed as the ring gear 31. That is, since the wall is formed in the rotation direction, the transmission efficiency of the centrifugal force to the lubricating oil is improved. By increasing the centrifugal force acting on the lubricating oil, the lubricating oil in the space 51 can reach the upper part in the vertical direction even at a low vehicle speed. In other words, in the upper part in the vertical direction, it is possible to accumulate lubricating oil in the centrifugal direction in the space 51 from a low vehicle speed (increase the oil level in the radial direction). Further, since the centrifugal force increases, a hydraulic head difference is generated in the lubricating oil even at a low vehicle speed, and the lubricating oil can be ejected from the pinion side through hole 52 and the bearing side through hole 53. The partition plate 41 serves as a guide for lubricating oil to the pinion side through hole 52 or the bearing side through hole 53 and has a function of improving the supply efficiency of the lubricating oil.

  The rotation of the lubricating oil is promoted by the partition plate 41, and the speed difference between the lubricating oil and the wall surface of the space 51 (the inner peripheral surface 31a, the ring gear flange 7 and the oil plate 50) is reduced. The loss caused by is reduced.

  In the planetary gear mechanism lubrication structure of the present embodiment, the greater the ring gear 31 rotates, the greater the centrifugal force acts on the lubricating oil in the space 51. Therefore, when the ring gear 31 rotates at a high speed, the flow rate of the lubricating oil ejected from the pinion side through hole 52 and the bearing side through hole 53 can be increased compared to when the ring gear 31 rotates at a low speed. In other words, the supply amount of the lubricating oil can be increased or decreased according to the rotation speed of the pinion gear 32 or the ball bearing 16.

  In the present embodiment, the oil plate 50 is provided in a part of the circumferential direction so that the space 51 is formed only in the vicinity of the through holes 52 and 53. Thereby, as will be described below, an increase in inertia weight due to the lubricating oil is suppressed. Referring to FIG. 3, a pair of partition plates 41 is installed with the pinion side through hole 52 sandwiched in the circumferential direction, and an oil plate 50 is provided in a region A <b> 1 between the pair of partition plates 41. Similarly, a pair of partition plates 41 is installed with the bearing-side through hole 53 sandwiched in the circumferential direction, and an oil plate 50 is provided in a region A2 between the pair of partition plates 41. Further, the oil plate 50 is not provided in any region other than the regions A1 and A2 in the circumferential direction, and the space 51 is not formed. By providing the oil plate 50 in this way, the space 51 is formed only in the vicinity of the through holes 52 and 53 in the circumferential direction.

  Thereby, the increase in the inertia weight of the ring gear 31 can be suppressed while the lubricating oil supplied to the pinion gear 32 and the ball bearing 16 is accumulated in the space 51. Since both end portions in the circumferential direction of the space 51 are closed by the partition plate 41, the lubricating oil can be reliably accumulated in the vicinity of the through holes 52 and 53, and the lubricating oil can be supplied to the pinion gear 32 and the ball bearing 16. it can. Further, in a region where the space 51 is not formed (the oil plate 50 is not provided) in the circumferential direction, the lubricating oil that has reached the inner peripheral surface 31 a of the ring gear 31 from the axial center flows out of the ring gear 31. For example, as indicated by an arrow Y <b> 5 in FIG. 1, it passes through the meshing portion between the gear portion 31 b of the ring gear 31 and the pinion gear 32 in the axial direction and flows out of the ring gear 31. As a result, the lubricating oil is accumulated only in a necessary portion of the inner peripheral surface 31a of the ring gear 31, and an increase in inertia weight is suppressed.

(Modification of the first embodiment)
A modification of the first embodiment will be described.

  FIG. 4 is a radial cross-sectional view showing the lubricating structure 1-1a of the planetary gear mechanism according to this modification. In the present modification, the partition plate 41 of the first embodiment is not provided. Even with such a configuration, centrifugal force can be applied to the lubricating oil in the space 51, and the lubricating oil can be ejected from the pinion side through hole 52 and the bearing side through hole 53.

  As shown in FIG. 4, a plurality of pinion side through holes 52 and bearing side through holes 53 are formed in the circumferential direction. In this modification, the pinion side through holes 52 and the bearing side through holes 53 are alternately arranged in the circumferential direction.

  Even if the partition plate 41 is not provided, since the circumferential force (rotational direction) acts on the lubricating oil from the inner peripheral surface 31a of the ring gear 31, the ring gear flange 7, or the oil plate 50, the lubricating oil is the center. It rotates about the axis X as the center of rotation. Therefore, the lubricating oil can be ejected from the pinion side through hole 52 and the bearing side through hole 53.

(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 planetary gear mechanism of the present embodiment is different from the lubrication structure 1-1 of the planetary gear mechanism of the first embodiment in that the inflow port on the radially inner side of the space 51 is wide and the lubricating oil It is a point that is easy to flow in.

  FIG. 5 is a radial sectional view showing the lubricating structure 1-2 of the planetary gear mechanism according to the present embodiment. In FIG. 5, reference numeral 51 a indicates the inlet of the space 51. As shown in FIG. 5, the width W in the circumferential direction of the space 51 increases in the radially inner region from the through holes 52 and 53 toward the radially inner side. In other words, the pair of partition plates 42 constituting the space 51 are inclined so that they are farther away from each other in the circumferential direction on the radially inner side than the through holes 52 and 53. Thereby, the lubricating oil supplied from the shaft center can easily flow into the space 51 from the inflow port 51a.

  In addition, a circumferential width W of a portion 51b radially outside the through holes 52 and 53 in the space 51 (hereinafter simply referred to as “radially outer portion”) 51b is narrowed. The circumferential width W of the radially outer portion 51 b is slightly larger than the diameter of the pinion side through hole 52 or the bearing side through hole 53. As described above, the circumferential width W is wider on the inner side in the radial direction than the through holes 52 and 53, and the circumferential width W is narrowed on the radially outer portion 51b. Even if the amount of lubricating oil is small, the lubricating oil can be quickly stored in the space 51 to a level that reaches the through holes 52 and 53. Therefore, the lubricating oil can be supplied to the lubricated portion of the pinion gear 32 and the ball bearing 16 through the through holes 52 and 53 even at a low vehicle speed. For example, the supply of lubricating oil to the lubricated portion of the pinion gear 32 and the ball bearing 16 can be started from the stage of low vehicle speed after the start of traveling.

(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 planetary gear mechanism lubrication structure 1-3 of this embodiment is different from the planetary gear mechanism lubrication structure of each of the above embodiments in that the pinion side through hole 52 and the bearing side through hole 53 are provided in different space portions. It is being done.

  FIG. 6 is a radial sectional view showing the lubricating structure 1-3 of the planetary gear mechanism according to the present embodiment. As shown in FIG. 6, a plurality of pinion side through holes 52 and bearing side through holes 53 are formed in the circumferential direction, and the pinion side through holes 52 and the bearing side through holes 53 are alternately arranged in the circumferential direction. Is arranged. The partition plate 43 partitions the pinion side through hole 52 and the bearing side through hole 53 in the circumferential direction. By the partition plate 43, the space 51 is connected to the first space 51-1 to which the pinion side through hole 52 is connected and the bearing side through hole 53 is not connected, and to the pinion side through hole. The hole 52 is partitioned into a second space portion 51-2 that is not connected. In other words, the space 51 is sandwiched between the pair of partition plates 43 in the circumferential direction, is connected to the pinion side through hole 52 and is not connected to the bearing side through hole 53, and the pair of the space 51. The second space portion 51-2 is sandwiched between the partition plates 43 in the circumferential direction, connected to the bearing side through hole 53, and not connected to the pinion side through hole 52.

  Thereby, the pinion side through-hole 52 and the bearing side through-hole 53 can be arrange | positioned in the optimal position in radial direction. Assuming that the pinion side through hole 52 and the bearing side through hole 53 are connected to a single space 51, the lubricating oil must be provided unless the pinion side through hole 52 and the bearing side through hole 53 are aligned in the radial direction. Will be unbalanced. FIG. 7 is a radial cross-sectional view showing an example of the lubricating structure of the planetary gear mechanism configured such that the pinion side through hole 52 and the bearing side through hole 53 have different radial positions.

  In the lubricating structure shown in FIG. 7, the pinion side through hole 52 is provided on the inner side in the radial direction than the bearing side through hole 53. In this case, the lubricating oil in the space 51 is preferentially discharged through the bearing side through hole 53, and the amount of lubricating oil supplied to the pinion gear 32 becomes insufficient. Therefore, if the lubricating oil is to be ejected from each of the pinion side through hole 52 and the bearing side through hole 53 in a balanced manner, it is necessary to align the radial positions of the pinion side through hole 52 and the bearing side through hole 53. However, when the axial oil passage (see reference numeral 39 in FIG. 1) and the radial position of the ball bearing 16 are different, if the radial positions of the pinion side through hole 52 and the bearing side through hole 53 are aligned, The radial positions of the through holes 52 and 53 will deviate from the optimum positions based on the efficiency of the lubricating oil supply.

  On the other hand, in the lubricating structure 1-3 of the planetary gear mechanism of the present embodiment, the pinion side through hole 52 and the bearing side through hole 53 are connected to different space portions, so that the radial position is separately set. Even if set, the lubricating oil can be ejected from each through hole in a well-balanced manner. Therefore, the through holes 52 and 53 can be provided at positions where the lubrication efficiency is optimal. The radial position of the pinion side through hole 52 is set so that the lubricating efficiency of the pinion gear 32 by the lubricating oil supplied through the axial oil passage 39 of the pinion shaft 36 is optimized, and the ball bearing 16 is lubricated. The radial position of the bearing-side through hole 53 can be set so that the efficiency is optimal.

(Fourth embodiment)
The fourth embodiment will be described with reference to FIGS. 8 and 9. In the fourth embodiment, only differences from the above embodiments will be described. FIG. 8 is an axial sectional view showing the lubrication structure 1-4 of the planetary gear mechanism according to this embodiment, and FIG. 9 is a radial section showing the lubrication structure 1-4 of the planetary gear mechanism according to this embodiment. FIG.

  The planetary gear mechanism lubrication structure 1-4 of the present embodiment is different from the planetary gear mechanism lubrication structure 1-3 of the third embodiment in that the first space portion 51-1 and the second space portion 51-2. A communication hole 54 is provided. The communication hole 54 balances the oil level between the space portions, so that the shaft balance is prevented from being lost.

  As shown in FIG. 9, a plurality of pinion side through holes 52 and bearing side through holes 53 are formed in the circumferential direction, and the pinion side through holes 52 and the bearing side through holes 53 are alternately arranged in the circumferential direction. Is arranged. A plurality of partition plates 44 are arranged in the space 51 in the circumferential direction. Similar to the partition plate 43 of the third embodiment, the partition plate 44 partitions the pinion side through hole 52 and the bearing side through hole 53 in the circumferential direction. As a result, the space 51 is connected to the pinion-side through-hole 52 and is not connected to the bearing-side through-hole 53, the bearing-side through-hole 53 is connected to the pinion-side through-hole 52. Is partitioned off from the second space 51-2 which is not connected. That is, the space portion 51 is adjacent to the circumferential direction by the partition plates 44 arranged in the circumferential direction with the partition plates 44 interposed therebetween, and each of the space portions 51 is sandwiched between the pair of partition plates 44 in the circumferential direction. It is partitioned into a space (first space 51-1, second space 51-2).

  As shown in FIGS. 8 and 9, the partition plate 44 is formed with a communication hole 54 that penetrates the partition plate 44 in the circumferential direction. The communication hole 54 communicates the first space portion 51-1 and the second space portion 51-2 that are adjacent to each other in the circumferential direction with the partition plate 44 interposed therebetween, and the first space portion 51-1 and the second space portion 51-2. Lubricating oil can be circulated in both directions between the space 51-2. In other words, the partition plate 44 that partitions the first space portion 51-1 and the second space portion 51-2, which are adjacent subspace portions, has a first space portion that is a subspace portion on one side in the circumferential direction. A communication hole 54 is formed through which 51-1 communicates with the second space portion 51-2 which is the other sub space portion and through which lubricating oil can flow.

  Since the supply of the lubricating oil from the shaft center is performed in an eventual manner, the flow rate is not constant. For this reason, the amount of the lubricating oil flowing into the space portion varies depending on the space portion, and as a result, the oil level of the space portion may vary. If the variation in the oil level is not eliminated, the shaft 6 supporting the ring gear 31 is shaken due to imbalance.

  In the lubrication structure 1-4 of the planetary gear mechanism of the present embodiment, the first space portion 51-1 and the second space portion 51-2 are communicated with each other through the communication hole 54. For this reason, even if a difference arises between the oil level of the 1st space part 51-1, and the oil level of the adjacent 2nd space part 51-2, the difference of the oil level is reduced. For example, as shown in FIG. 9, the oil level (distance in the radial direction between the inner peripheral surface 31 a of the ring gear 31 and the oil surface C) H <b> 1 of the first space 51-1 When it becomes larger than the level H2, as indicated by an arrow Y6, the lubricating oil in the first space portion 51-1 flows out to the second space portion 51-2 through the communication hole 54. Thereby, the difference of the oil level of the 1st space part 51-1 and the 2nd space part 51-2 is reduced. As a result, the shaft balance of the shaft 6 that supports the ring gear 31 can be made uniform in the circumferential direction. In addition, a balance between the amount of lubricating oil supplied to the pinion gear 32 and the amount of lubricating oil supplied to the ball bearing 16 can be maintained, and insufficient lubrication can be suppressed.

  In the present embodiment, the radial position of the communication hole 54 is set based on the radial positions of the through holes 52 and 53. As described below, the communication hole 54 is, for example, a position that can reduce the difference in oil level between the space portions and can supply lubricating oil to the lubricated portion even at a low vehicle speed. Formed. When the communication hole 54 is provided at a position on the radially outer side of the partition plate 44, the oil level H1, H2 is small between the first space portion 51-1 and the second space portion 51-2 through the communication hole 54. The lubricating oil can be circulated. For this reason, in order to reduce the difference between the oil level H1 of the first space portion 51-1 and the oil level H2 of the second space portion 51-2, the radial position of the communication hole 54 is moved outward in the radial direction. It is advantageous.

  On the other hand, in order to supply the lubricating oil to the lubricated part through the through holes 52 and 53 even at a low vehicle speed, the lubricating oil should be concentrated in any of the space parts 51-1 and 51-2. It is advantageous. Lubricating oil concentrates in the space part (first space part 51-1 and second space part 51-2) where the amount of inflow of lubricating oil is large compared to other space parts, and the oil level in the space part increases. If the lubricating oil is ejected from the through holes 52 and 53, the lubricating oil is supplied to the lubricated portion even at a low vehicle speed. For example, in EV traveling, since the lubricating oil is supplied to the lubricated portion from the low vehicle speed stage after the start of traveling, occurrence of insufficient lubrication is suppressed. In other words, in order to supply the lubricating oil to the lubricated portion even at a low vehicle speed, the communication hole prevents the lubricating oil from flowing through the communication hole 54 until the lubricating oil is ejected from the through holes 52 and 53. It is advantageous to bring 54 radial positions inward in the radial direction.

  As shown in FIG. 9, the radial position of the communication hole 54 of the present embodiment is set to be approximately the same as the radial position of the through holes 52 and 53. As a result, in the first space portion 51-1 or the second space portion 51-2 where the lubricating oil is concentrated, the oil level rapidly increases until the through holes 52 and 53 are reached even at a low vehicle speed. Lubricating oil is supplied to 32 and the ball bearing 16. When the oil level exceeds the level at which the oil level C reaches the communication hole 54, the lubricating oil flows between the first space part 51-1 and the second space part 51-2 through the communication hole 54, The oil level is equalized between the spaces.

  Note that the flow passage cross-sectional area of the communication hole 54 is sufficient to balance the oil level for each space portion and to keep the oil level in the space portion where the lubricating oil is concentrated properly, through the through holes 52 and 53. It is preferable to set so as to be compatible with the supply of the lubricating oil.

  In any of the above embodiments, when the pinion side through hole 52 and the bearing side through hole 53 are connected to the same space, either one of the through holes is made to function as an oil level adjusting hole. It may be.

  For example, the bearing side through hole 53 can be disposed radially inward of the pinion side through hole 52 and the bearing side through hole 53 can have an oil level adjusting function. In this case, for example, the diameter of the pinion side through hole 52 is set to a size that can supply the minimum necessary lubricating oil to the pinion gear 32. On the other hand, the diameter of the bearing-side through hole 53 is large enough to allow the lubricating oil flowing into the space portion to be discharged to the outside of the space portion, in other words, by discharging the lubricating oil from the bearing-side through hole 53, It is set to a size that can suppress further increase in level.

  Since the pinion side through hole 52 is disposed on the outer side in the radial direction than the bearing side through hole 53, the lubricating oil in the space is preferentially supplied to the pinion gear 32. Further, surplus lubricating oil exceeding the amount necessary for lubricating the pinion gear 32 is discharged from the space portion toward the ball bearing 16 through the bearing side through hole 53. As a result, it is possible to suppress an increase in stirring loss in the planetary gear mechanism 30 due to excess lubricant remaining while lubricating the ball bearing 16.

1-1, 1-1a, 1-2, 1-3, 1-4 Lubricating structure of planetary gear mechanism 5a Shaft oil passage 5b Radial oil passage 7 Ring gear flange 10 Hybrid vehicle 11 Engine 12 Power transmission mechanism 14 Drive shaft DESCRIPTION OF SYMBOLS 15 Power split mechanism 16 Ball bearing 17a 1st motor generator 17b 2nd motor generator 30 Planetary gear mechanism 31 Ring gear 32 Pinion gear 33 Carrier 34 Sun gear 35 Pinion needle bearing 37 Counter drive gear 38 Pinion lubricating oil path 39 Shaft center oil path 40 Radial direction oil passage 41, 42, 43, 44 Partition plate 50 Oil plate 51 Space part 51-1 First space part (sub space part)
51-2 Second space (subspace)
52 Pinion side through hole 53 Bearing side through hole 54 Communication hole 100 ECU
B, C Oil level

Claims (5)

A planetary gear mechanism lubrication structure for transmitting power to a drive shaft,
The planetary gear mechanism is a power output member, a ring gear that rotates in conjunction with the drive shaft, a sun gear disposed coaxially with the ring gear radially inward of the ring gear, The pinion gear disposed between the ring gear and the sun gear and engaged with each of the ring gear and the sun gear, the pinion gear is rotatably supported, and is rotatably supported coaxially with the ring gear. And a carrier
A pair of wall portions provided on one side in the axial direction from the pinion gear, projecting radially inward from the inner peripheral surface of the ring gear, and facing each other in the axial direction;
It is formed in the wall portion facing the pinion gear in the axial direction, penetrates the wall portion in the axial direction at a position corresponding to the radial pinion gear, and is formed by the pair of wall portions and the inner peripheral surface. A pinion side through hole that opens into the space part,
A supply passage for supplying lubricating oil to the space from the inside in the radial direction than the pinion gear;
A planetary gear mechanism lubrication structure comprising: a closing member that is connected to the inner peripheral surface and the pair of wall portions in the space portion, closes the space portion, and rotates integrally with the ring gear. . In the lubricating structure of the planetary gear mechanism according to claim 1,
The planetary gear mechanism lubrication structure, wherein an opening of the pinion side through hole is sandwiched in a circumferential direction by the pair of blocking members in the space portion. In the lubricating structure of the planetary gear mechanism according to claim 1 or 2,
Furthermore, the through-hole to be lubricated portion is formed in the wall portion facing the lubricated portion different from the pinion gear in the axial direction and penetrates the wall portion in the axial direction at a position corresponding to the lubricated portion in the radial direction. With
The pinion side through hole and the lubricated part side through hole have different radial positions,
The space portion is sandwiched in the circumferential direction by a pair of blocking members, connected to the pinion side through hole, and not connected to the lubricated portion side through hole, and a pair of the blocking members A planetary gear mechanism lubrication structure comprising: a second space portion that is sandwiched in a circumferential direction by the shaft and connected to the to-be-lubricated portion side through hole and not connected to the pinion side through hole. In the lubricating structure of the planetary gear mechanism according to any one of claims 1 to 3,
The space portions are adjacent to each other in the circumferential direction by the plurality of closing members arranged in the circumferential direction, and each of the sub space portions is sandwiched in the circumferential direction by a pair of the closing members. Divided into
The closing member for partitioning the adjacent sub space portions is formed with a communication hole through which the sub space portion on one side in the circumferential direction and the sub space portion on the other side communicate with each other and through which lubricating oil can flow. Lubricating structure for planetary gear mechanism, characterized by In the lubricating structure of the planetary gear mechanism according to any one of claims 1 to 4,
The planetary gear mechanism has an internal combustion engine as a drive source and a second drive source different from the internal combustion engine, and stops with the internal combustion engine and travels with the power of the second drive source. Mounted in a hybrid vehicle capable of transmitting the power of the internal combustion engine to the drive shaft,
The planetary gear mechanism lubrication structure, wherein the carrier is connected to an output shaft of the internal combustion engine and rotates integrally with the output shaft.

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