JP5018579B2 - 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 suitable for naturally flowing lubricating oil stored in a storage part and supplying the lubricating oil to a power transmission element.

  Conventionally, as a lubricating structure of this type of power transmission device, one that lubricates a planetary gear device as a power transmission element constituting a speed change mechanism of an automobile or the like is known (for example, see Patent Document 1). The lubrication structure of the power transmission device is provided in the casing so as to be positioned above the planetary gear device, and includes a catch tank as a reservoir for temporarily storing the lubricant, and a lubricant oil from the catch tank to the planetary gear device. And a supply path.

  The catch tank collects the lubricating oil that has been scraped up by the final gear of the differential device, and stores the lubricating oil. The lubricating oil supplemented to the catch tank flows down the lubricating oil supply path. And supplied to the constituent members of the planetary gear device so as to prevent seizure and durability of the planetary gear device.

Specifically, as shown in FIG. 7, in the conventional lubricating structure for a power transmission device, the inside of the casing 91 is partitioned by a partition wall 92, and the portion constituting the side wall of the catch tank 93 of the partition wall 92 is in communication. A hole 94 is formed, an oil hole 96 as an opening is formed in the vicinity of the carrier of the planetary gear device 95 of the partition wall 92, and a flow path 97 is formed at a portion connecting the communication hole 94 and the oil hole 96 of the partition wall 92. ing. The oil holes 96 are formed in the direction of the flow line of the lubricating oil flowing down the flow path 97, so that the lubricating oil flowing down the wall surface can easily flow. Then, the lubricating oil stored in the catch tank 93 flows out through the communication hole 94, flows down through the flow path 97 formed in the wall surface of the partition wall 92 as indicated by an arrow F 7, and the planetary gear device through the oil hole 96. 95 is supplied.
JP 2005-273670 A

  However, in such a conventional lubricating structure of a power transmission device, the oil holes 96 are formed in the direction of the flow line of the lubricating oil, and most of the lubricating oil flowing down from the catch tank 93 passes through the oil holes 96 and the planetary gears. Since the oil is supplied to the device 95, the oil amount supplied to the planetary gear device 95 is increased in the normal range where the amount of oil supplemented by the catch tank 93 is large, that is, in the low / medium speed range of the engine. There is a problem that the device 95 is affected by the resistance of the lubricating oil, the stirring loss increases, and the fuel consumption deteriorates.

  In this case, it is conceivable to reduce the amount of oil supplied to the planetary gear unit 95 by reducing the diameter of the oil hole 96, but the lubricating oil becomes highly viscous at a low temperature and the lubricating oil enters the oil hole 96. There is a problem that it is difficult to flow in, and the planetary gear unit 95 cannot be supplied with an oil amount necessary for preventing seizure and maintaining durability.

  The present invention has been made to solve the above-described conventional problems, and provides a lubricating structure of a power transmission device that can supply an appropriate amount of lubricating oil to a power transmission element regardless of traveling conditions. For the purpose.

  In order to achieve the above object, the lubrication structure for a power transmission device according to the present invention includes (1) a power transmission element coupled to a drive source, a casing for housing the power transmission element, and a position above the power transmission element. Power provided with a storage portion that is provided at an upper portion of the casing so as to be temporarily stored and that stores lubricating oil temporarily, and a lubricating oil supply passage that supplies the lubricating oil that naturally flows down from the storage portion to the power transmission element In the lubricating structure of the transmission device, the lubricating oil supply path is formed in an inclined portion that naturally flows down the lubricating oil stored in the storage portion toward a lower portion of the casing, and an intermediate portion of the inclined portion, An opening that opens in a direction intersecting the streamline direction of the lubricating oil flowing down the inclined portion, and an oil passage that guides the lubricating oil introduced through the opening to the power transmission element. The That.

With this configuration, since the opening is opened in the middle of the inclined portion in a direction intersecting the streamline direction of the lubricating oil flowing down the inclined portion, the lubricating oil flowing down the inclined portion is branched by the opening. Only a part of the lubricating oil is supplied to the power transmission element through the opening. For this reason, the lubricating oil is not supplied more than necessary to the power transmission element even in the normal range, preventing the power transmission element from being affected by the resistance of the lubricating oil and increasing the agitation loss, thereby deteriorating the fuel consumption. Can be prevented.
Therefore, without reducing the diameter of the opening, it is possible to prevent supply of excessive lubricating oil to the power transmission element, and to prevent seizure of the power transmission element even at low temperatures when the lubricating oil has a high viscosity. Lubricating oil of the amount necessary for maintaining durability can be supplied.
Therefore, an appropriate amount of lubricating oil can be supplied to the power transmission element regardless of the traveling conditions.

  In the lubricating structure of the power transmission device according to (1) above, (2) the opening is opened in a direction substantially orthogonal to a streamline direction of the lubricating oil flowing down the inclined portion, and the oil passage Is configured such that at least a portion communicating with the opening extends in the same direction as the opening.

  With this configuration, the opening portion of the oil passage and at least the portion communicating with the opening portion are formed in a direction substantially perpendicular to the flow direction of the lubricating oil flowing down the inclined portion. Lubricating oil is prevented from being supplied more than necessary, and at low temperatures when the lubricating oil has a high viscosity, the flow speed of the lubricating oil flowing down the inclined portion decreases, flows into the opening, and is supplied to the power transmission element. The amount of lubricating oil can be increased.

  In the lubricating structure for a power transmission device according to the above (1) or (2), (3) the power transmission element is a planetary gear device.

  With this configuration, it is possible to supply the amount of oil necessary for preventing seizure and maintaining durability to the planetary gear device having a large number of rotations.

  ADVANTAGE OF THE INVENTION According to this invention, the lubrication structure of the power transmission device which can supply a suitable quantity of lubricating oil to a power transmission element irrespective of driving conditions can be provided.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 to FIG. 6 are diagrams showing an embodiment of a lubricating structure for a power transmission device according to the present invention, and show an example applied to a power transmission device for a four-wheel drive front drive. The present invention can also be applied to gears, timing belts, and timing chains as power transmission elements constituting the power transmission device, but here, for convenience of explanation, the pinion gear bearing that supports the pinion gear shaft of the planetary gear device is lubricated. The case where oil as oil is supplied will be described.

  FIG. 1 is a cross-sectional view of a power transmission device according to an embodiment of the present invention. 2 is a partially enlarged view of a cross-sectional view of the power transmission device of FIG.

First, the configuration will be described.
As shown in FIG. 1, the power transmission device 1 has a transmission case 2 as a casing, and in the transmission case 2, a compound planetary gear device 3 constituting a speed change mechanism, and front drive shafts 44, 45. The differential device 4 capable of differential output to the motor, the drive motor 5 that drives the vehicle with the stored electric power, the motor generator 6 that can generate electric power by power from an engine (not shown), and the power transmission device 1 An oil pump 7 for supplying oil is accommodated.

  The compound planetary gear unit 3 includes a first planetary gear unit 11 that transmits power output from the drive motor 5 and a second planetary gear unit 12 that transmits power output from the engine. The power output from the drive motor 5 and the engine can be selectively transmitted to the differential device 4.

The transmission case 2 includes a housing 21 that is fastened and supported on the engine side, and a case 22 that is fixed to an opening end of the housing 21 opposite to the engine side.
A case cover 23 is attached to the opening end of the case 22 opposite to the housing 21 side, and an oil pump cover 24 is attached to the opposite side of the case cover 23 to the case 22 side.

A housing cover 25 is attached to the housing 21, and the inside of the housing 21 is defined as a storage portion of the motor generator 6 and a storage portion of a damper element 14 that is a driving force transmission mechanism from the engine.
The housing 21, the case 22, the case cover 23, and the housing cover 25 constitute the transmission case 2, and each storage portion that stores the compound planetary gear device 3, the differential device 4, the drive motor 5, and the motor generator 6. Is formed.

The case 22 is formed with a bottomed annular partitioning portion 22a so as to surround the outer periphery of the compound planetary gear device 3. The annular partitioning portion 22a is a bearing that rotatably supports one end of the compound planetary gear device 3. 27 is attached.
The housing 21 is formed with an annular thick portion 21a that abuts the annular partition portion 22a and forms the housing portion of the composite planetary gear device 3 together with the annular partition portion 22a. The annular thick portion 21a includes a composite planetary planet 21a. A bearing 28 that rotatably supports the other end of the gear device 3 is mounted.

  An input shaft 15 extending so as to penetrate the motor generator 6 and the second planetary gear device 12 is disposed at the rotation center portion of the motor generator 6 and the second planetary gear device 12, and a driving motor is provided. An oil pump drive shaft 16 that extends through the drive motor 5 and the first planetary gear unit 11 is disposed at the rotation center portion of the fifth planetary gear unit 11 and the first planetary gear unit 11.

One end of the input shaft 15 is integrally engaged with the crankshaft 17 in the rotational direction, and the other end is connected to the second planetary gear unit 12, and power from the engine is supplied to the compound planetary gear unit 3. To communicate.
One end of the oil pump drive shaft 16 is integrally engaged with the input shaft 15 in the rotational direction, and the other end is connected to the oil pump 7, and transmits power from the input shaft 15 to the oil pump 7. It is like that.

  Further, a plurality of oil passages are formed in the oil pump drive shaft 16 and the input shaft 15, and the oil pumped up by the oil pump 7 through the oil passages is sent to each part of the power transmission device 1. ing.

Further, in the transmission case 2, a counter driven gear 41 and a final drive gear 42 that transmit power output from the compound planetary gear device 3 to the differential device 4 are provided.
The counter driven gear 41 is meshed with a counter drive gear 13 of the composite planetary gear device 3 to be described later. The counter driven gear 41 is spline-coupled to a counter shaft 43 integrally formed with a final drive gear 42.

The differential device 4 includes a hollow differential case 51, and the differential case 51 is rotatably supported by the case 22 and the housing 21 via bearings 58 and 59.
A final gear 52 that meshes with the final drive gear 42 is fastened to the outer periphery of the differential case 51 so that the power output from the compound planetary gear unit 3 is transmitted to the differential case 51 via the final gear 52. It has become.

A pinion gear shaft 53 is rotatably supported inside the differential case 51, and a pair of differential pinion gears 54 and 55 are fixed to the pinion gear shaft 53.
Each differential pinion gear 54, 55 is engaged with two side gears 56, 57, and front drive shafts 44, 45 are connected to the side gears 56, 57, respectively. The front wheels (not shown) are respectively fixed. It should be noted that such deceleration by the plurality of gears 54, 55, 56, 57, the function of the differential device 4 and the like are well known and will not be described in detail here.

  As shown in FIG. 2, the compound planetary gear unit 3 distributes the power from the engine side to the first planetary gear unit 11 for output reduction of the drive motor 5, and to the motor generator 6 and the counter drive gear 13. The second planetary gear device 12 having a power distribution function is constituted by the first planetary gear device 11 and the second planetary gear device 12 in which the ring gear R1 and the ring gear R2 on the outer peripheral side are arranged in the rotation axis direction. The counter drive gear 13 is connected.

  Specifically, the first planetary gear device 11 is provided at equal intervals in the circumferential direction around the sun gear S1, the inner ring gear R1 surrounding the sun gear S1, and the sun gear S1, and meshes with the sun gear S1 and the ring gear R1. It has a plurality of pinion gears P1 and a carrier Cr1 that supports the plurality of pinion gears P1 so as to be able to rotate and is fixed to the case 22.

  The carrier Cr1 is disposed between the pair of annular plate portions 31a and 31b located on both ends of the plurality of pinion gears P1 and the plurality of pinion gears P1 at equal intervals in the circumferential direction, and couples the pair of annular plate portions 31a and 31b. It is comprised from the some support | pillar part 32. FIG.

The pinion gear P1 is rotatably held on a pinion gear shaft 34 supported at both ends by a pair of annular plate portions 31a and 31b via a pinion gear bearing 33 as a power transmission element.
In the pinion gear shaft 34, there are formed a pinion gear shaft oil passage 34a extending in the rotation axis direction, and a branch passage communicating the pinion gear shaft oil passage 34a and the outside of the outer peripheral surface of the pinion gear shaft 34. The oil is supplied to the pinion gear bearing 33 through the pinion gear shaft internal oil passage 34a and the branch passage.

  The second planetary gear device 12 includes a sun gear S2, an inner ring gear R2 surrounding the sun gear S2, a plurality of pinion gears P2 provided at equal circumferential intervals around the sun gear S2 and meshed with the sun gear S2 and the ring gear R2. And a plurality of pinion gears P2 that are rotatably supported and have a carrier Cr2 coupled to the input shaft 15.

  The carrier Cr2 is disposed between the pair of annular plate portions 35a and 35b located on both ends of the plurality of pinion gears P2 and the plurality of pinion gears P2 at equal intervals in the circumferential direction, and couples the pair of annular plate portions 35a and 35b. It comprises a plurality of support columns 36.

The pinion gear P2 is rotatably held on a pinion gear shaft 39 supported at both ends by a pair of annular plate portions 35a and 35b via a pinion gear bearing 38 as a power transmission element.
In the pinion gear shaft 39, an oil passage 39a in the pinion gear shaft that extends in the rotation axis direction, and a branch passage that connects the oil passage 39a in the pinion gear shaft and the outside of the outer peripheral surface of the pinion gear shaft 39 are formed. Oil is supplied to the pinion gear bearing 38 through the inner oil passage 39a and the branch passage.

Returning to FIG. 1, the drive motor 5 includes a rotor 62 on which a permanent magnet 61 is mounted and a stator 64 around which a three-phase coil 63 is wound, and is configured as a permanent magnet synchronous motor.
The rotor 62 has a through hole formed in the direction of the rotation axis, and is rotatably supported by the case 22 and the case cover 23 via bearings 66 and 67 with the oil pump drive shaft 16 inserted through the through hole. Has been. The rotor 62 is spline-coupled to the sun gear S1 of the first planetary gear unit 11 at the end of the engine side so as to rotate integrally with the sun gear S1.

The motor generator 6 includes a rotor 72 on which a permanent magnet 71 is mounted and a stator 74 around which a three-phase coil 73 is wound. The motor generator 6 is configured as a permanent magnet synchronous generator motor like the drive motor 5. Yes.
The rotor 72 has a through hole formed in the direction of the rotation axis. The rotor 72 is rotatably supported by the housing 21 and the housing cover 25 via bearings 76 and 77 with the input shaft 15 inserted through the through hole. Yes. The rotor 72 is spline-coupled to the sun gear S2 of the second planetary gear unit 12 at the end of the engine side, and rotates integrally with the sun gear S2.

  The rotors 62 and 72 of the drive motor 5 and the motor generator 6 are arranged with a slight gap between the rotors 62 and 72 and the inner circumferences of the stators 64 and 74, respectively, so that a magnetic field is generated by the rotation of the rotors 62 and 72. It has become.

  The stators 64 and 74 of the drive motor 5 and the motor generator 6 are not shown in detail, but for example, annular yokes 65 and 75 in which magnetic materials are laminated have a plurality of stator teeth separating the winding grooves. The three-phase coils 63 and 73 are wound around the winding grooves of the yokes 65 and 75.

The oil pump 7 includes a drive rotor 47 mounted on the oil pump drive shaft 16 and a driven rotor (not shown), and is rotatably supported by the case cover 23.
In addition, a relief valve 48 is accommodated in the oil pump cover 24, and oil pressure control is performed.

  The oil pumped up by the oil pump 7 is limited to a predetermined set pressure by the relief valve 48, and the power transmission device 1 passes through a plurality of oil passages formed in the oil pump drive shaft 16 and the input shaft 15. It is supplied to each part constituting.

  A catch tank 79 as a storage portion is formed above the storage portion of the compound planetary gear device 3 by the case 22 and the housing 21, and a partition portion 22 b that partitions the storage portion of the drive motor 5 and the catch tank 79. A communication hole 81 is formed as an outlet of the catch tank 79.

Incidentally, the oil supplied from the oil pump 7 to the differential device 4 is accumulated in the housing portion of the differential device 4 of the case 22 so that the lower portion of the final gear 52 is immersed.
The oil accumulated in the storage section of the differential device 4 is swung up by the final gear 52 and scattered in the storage section when the final gear 52 rotates as the vehicle travels.

The scooped-up oil lubricates the counter drive gear 13, the counter driven gear 41, the final drive gear 42, and their bearings, and a part of the oil is captured by the catch tank 79 and temporarily stored. It has become.
Then, the oil stored in the catch tank 79 flows out from the communication hole 81, and an inclined channel 82 as an inclined part, an oil hole 83 as an opening, a folded part 84 as an oil path, and an annular channel 85 described later. The pinion gear bearing 33 is lubricated through the pinion gear shaft internal oil passage 34a of the pinion gear shaft 34.

Here, with reference to FIG. 3 to FIG. 6, the flow path from the catch tank until the oil is supplied to the pinion gear bearing of the pinion gear constituting the compound planetary gear device will be described.
FIG. 3 is a front view of the compound planetary gear device in which the sun gear of the first planetary gear device, the sun gear of the second planetary gear device, the pinion gear, and the carrier are omitted. FIG. 4 is a cross-sectional schematic view of the AA cross section in which a part of the case surrounding the compound planetary gear device is added to the compound planetary gear device of FIG. 3. FIG. 5 is a schematic cross-sectional view taken along the line B-B in which a part of the case surrounding the compound planetary gear device is added to the compound planetary gear device of FIG. 3. FIG. 6 is a schematic diagram of an annular flow path formed in the case.

  As shown in FIGS. 3 and 5, the annular partitioning portion 22a of the case 22 has an inclined surface that is inclined from the vicinity of the communication hole 81 toward the lower portion of the case 22, and the inclined surface has a concave cross section. An inclined channel 82 is formed. The oil stored in the catch tank 79 flows along the inclined channel 82 toward the inner peripheral bottom surface of the lower part of the case 22.

  An oil hole 83 communicating with the housing portion of the compound planetary gear device 3 is formed in the middle of the inclined channel 82, and the oil hole 83 opens in a direction perpendicular to the inclination direction of the inclined channel 82. ing. That is, the oil hole 83 is opened in a direction orthogonal to the flow direction of the oil flowing down the inclined channel 82, and only a part of the oil flowing down the inclined channel 82 is the oil hole 83. It has come to flow into.

Also, the wall surface of the annular partition 22a on the side of the compound planetary gear unit 3 is bent in a direction perpendicular to the inclination direction of the inclined flow path 82 at the upstream edge of the opening edge of the oil hole 83 in the streamline direction. The folding | returning part 84 to be provided is provided, This folding | returning part 84 is extended to the compound planetary gear apparatus 3 side.
Further, the folded portion 84 is provided on the extension of the oil hole 83, and guides the oil flowing into the oil hole 83 and feeds it into the annular flow path 85.

  As shown in FIGS. 3 and 6, the pinion gears P <b> 1 are arranged at equal intervals in the circumferential direction, and the pinion gear shaft 34 of each pinion gear P <b> 1 is placed on the wall surface of the annular partition 22 a of the case 22 on the compound planetary gear device 3 side. An annular flow path 85 having a concave cross section communicating with the inner pinion gear shaft internal oil path 34a is formed. In FIG. 6, the position of the oil passage 34a in the pinion gear shaft in the pinion gear shaft 34 is a portion indicated by a circle drawn by a two-dot chain line.

  The annular flow path 85 has an annular shape centering on the rotation center portion of the compound planetary gear device 3, and the width of the flow path is narrowed from upstream to downstream. In the annular flow path 85, oil reservoirs 85a, 85b, 85c, 85d, and 85e are formed corresponding to the positions of the oil passages 34a in the pinion gear shaft in each pinion gear shaft 34.

Subsequently, the flow of oil from the catch tank to the pinion gear bearing of the pinion gear shaft constituting the compound planetary gear device will be described with reference to FIGS.
As shown in FIG. 5, when the oil stored in the catch tank 79 flows out from the communication hole 81, the oil flows down the inclined channel 82 and is branched by the oil hole 83 in the direction indicated by the arrow F <b> 1 and the direction indicated by the arrow F <b> 2. The The oil that has flowed down in the streamline direction along the inclined channel 82 that is the direction indicated by the arrow F <b> 1 falls naturally and is stored on the inner peripheral bottom surface of the case 22.

  On the other hand, the oil that has flowed into the oil hole 83 that is orthogonal to the streamline direction, which is the direction indicated by the arrow F <b> 2, flows into the annular flow path 85 through the folded portion 84. At this time, the amount of oil flowing into the oil hole 83 varies depending on the viscosity of the oil. For example, when the viscosity of the oil is low, such as at normal temperature, the flow rate flowing down the inclined channel 82 increases, the amount of oil jumping over the oil hole 83 increases, and the amount of oil flowing into the oil hole 83 decreases. In addition, when the viscosity of the oil is high, such as at a low temperature, the flow rate flowing down the inclined flow path 82 decreases, the amount of oil jumping over the oil holes 83 decreases, and the amount of oil flowing into the oil holes 83 increases.

  As shown in FIG. 6, the oil that has flowed into the annular flow path 85 first flows down in the direction indicated by the arrow F3, and the oil is stored in the uppermost oil reservoirs 85a and 85b. Next, the oil overflowing the uppermost oil reservoirs 85a and 85b, or the oil not captured by the uppermost oil reservoirs 85a and 85b flows down in the direction indicated by the arrow F4, and the oil flows into the intermediate oil reservoirs 85c and 85d. Is stored. Finally, the oil overflowing the middle oil sump 85c, 85d, or the oil not captured by the uppermost sump 85a, 85b and the middle sump 85c, 85d flows down in the direction indicated by the arrow F5. Oil is stored in the lower oil reservoir 85e.

  As shown in FIG. 4, the oil stored in each oil reservoir 85e is supplied to the pinion gear bearing 33 through the pinion gear shaft internal oil passage 34a formed in the pinion gear shaft 34 as shown by an arrow F6. As a result, the seizure prevention of the pinion gear P1 disposed in a severe environment in terms of load and rotation speed in the power transmission device can be prevented, and durability can be maintained.

  As described above, in the present embodiment, the inclined channel 82 that naturally flows down the oil stored in the catch tank 79 toward the lower portion of the case 22 and the middle portion of the inclined channel 82 are formed. An oil passage 83 that opens in a direction orthogonal to the direction of the streamline of the oil flowing down 82, and an annular passage 85 that guides the oil introduced through the oil hole 83 to the pinion gear bearing 33 and the oil passage 34 a in the pinion gear shaft are provided. It consists of what you have.

Therefore, the oil flowing down the inclined channel 82 is branched by the oil hole 83 and only a part of the oil is formed in the oil hole 83, the turn-back part 84, the annular channel 85 and the pinion gear shaft 34. It is supplied to the pinion gear bearing 33 through 34a. For this reason, the oil is not supplied to the pinion gear bearing 33 more than necessary even in the normal range, and the composite planetary gear device 3 is prevented from increasing the stirring loss due to the influence of the oil resistance, and the fuel consumption is deteriorated. Can be prevented.
Therefore, without reducing the diameter of the oil hole 83, it is possible to prevent excessive supply of oil to the pinion gear bearing 33 and to prevent seizure and durability of the pinion gear bearing 33 even at low temperatures when the oil has a high viscosity. The amount of oil necessary to maintain the performance can be supplied to the pinion gear bearing 33.
In this way, an appropriate amount of oil can be supplied to the pinion gear bearing 33 regardless of running conditions.

  In the present embodiment, since the oil hole 83 and the folded portion 84 are provided in a direction orthogonal to the inclined flow path 82, the oil is supplied to the pinion gear bearing 33 more than necessary in the normal range. At a low temperature when the oil has a high viscosity, the flow rate of the oil flowing down the inclined portion decreases, and the amount of oil that flows into the oil hole 83 and is supplied to the pinion gear bearing 33 can be increased.

Further, in the present embodiment, the inclined channel 82 is formed in the left-right direction of the vehicle, and the amount of oil flowing down the inclined channel 82 increases when the vehicle turns, but the oil hole 83 passes through the inclined channel 82. Since the opening is made in a direction orthogonal to the flow line direction of the oil flowing down, it is possible to prevent the oil from being supplied to the pinion gear bearing 33 more than necessary.
Further, for example, when the inclined flow path 82 is formed in the front-rear direction of the vehicle, the pinion gear bearing is more than necessary even if the amount of oil flowing down the inclined flow path 82 increases due to the inclination of the vehicle when climbing or the like. It is possible to prevent oil from being supplied to 33.

  In the present embodiment, the oil hole 83 is formed so as to open in a direction orthogonal to the direction of the oil stream flowing down the inclined channel 82, but the direction of the oil stream flowing down the inclined channel 82 The oil holes 83 may be formed so as to open in any direction as long as they intersect.

Further, in the present embodiment, the oil hole 83 is formed in the middle part of the inclined channel 82 to branch the oil flow, but a bifurcated branch path is formed in the middle part of the inclined channel 82. Alternatively, the oil hole 83 may be formed in the direction of the streamline of the oil flowing down one of the branch paths.
Even with such a configuration, the oil flowing down the inclined channel 82 is diverted by the branch path, and only a part of the oil can be supplied to the compound planetary gear device 3 through the oil hole 83.

  In the present embodiment, the inclined channel 82 and the annular channel 85 are configured by the concave grooves formed on the wall surface of the case 22, but are configured by a pair of parallel guide portions that are formed to protrude from the wall surface of the case 22. Alternatively, it may be configured by a pipe formed in a tubular shape on the wall surface of the case 22.

  The embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

  As described above, the present invention is capable of supplying an appropriate amount of lubricating oil to the power transmission element regardless of running conditions, and in particular, the power transmission element by naturally flowing down the lubricating oil stored in the storage section. It is useful for a lubricating structure of a power transmission device suitable for supplying to a vehicle.

It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is sectional drawing of a power transmission device. It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is the elements on larger scale of FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is the front of the compound planetary gear apparatus which abbreviate | omitted the sun gear of the 1st planetary gear apparatus, the sun gear of the 2nd planetary gear apparatus, the pinion gear, and the carrier. FIG. It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is a cross-sectional schematic diagram of the AA cross section which added a part of case which encloses a compound planetary gear apparatus to the compound planetary gear apparatus of FIG. is there. It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is a cross-sectional schematic diagram of the BB cross section which added a part of case surrounding a compound planetary gear apparatus to the compound planetary gear apparatus of FIG. is there. It is a figure which shows embodiment of the lubrication structure of the power transmission device which concerns on this invention, and is a schematic diagram of the annular flow path formed in the case. It is a figure which shows the prior art of the lubricating structure of the power transmission device which concerns on this invention, and is explanatory drawing of the flow of the oil in the lubricating structure of the conventional power transmission device.

Explanation of symbols

1 Power transmission device 2 Transmission case (casing)
3 Compound planetary gear unit (planetary gear unit)
Reference Signs List 4 differential device 5 drive motor 6 motor generator 7 oil pump 11 first planetary gear device 12 second planetary gear device 13 counter drive gear 15 input shaft 16 oil pump drive shaft 22 case 22a annular partitioning portion 22b partitioning portion 31a, 31b, 35a, 35b Annular plate part 32, 36 Post part 33, 38 Pinion gear bearing (power transmission element)
34, 39 Pinion gear shaft 34a, 39a Oil passage in the pinion gear shaft (oil passage)
79 Catch tank (reservoir)
81 communication hole 82 inclined channel (inclined part)
83 Oil hole (opening, oil passage)
84 Folding part (oil passage)
85 Annular channel (oil channel)

Claims (3)

A power transmission element connected to a drive source, a casing for housing the power transmission element, and a storage part that is provided above the casing so as to be positioned above the power transmission element and temporarily stores lubricating oil And a lubricating structure of a power transmission device comprising a lubricating oil supply path for supplying lubricating oil that naturally flows down from the storage portion to the power transmission element,
The lubricating oil supply path is
An inclined portion for allowing the lubricating oil stored in the storage portion to naturally flow toward a lower portion of the casing;
A bifurcation branching in the middle of the inclined portion and an opening formed in one of the bifurcations and opening in a direction intersecting the streamline direction of the lubricating oil flowing down one of the bifurcations. And an oil passage for guiding the lubricating oil introduced through the opening to the power transmission element. The opening is open in a direction substantially perpendicular to the streamline direction of the lubricating oil flowing down the inclined portion;
2. The lubricating structure for a power transmission device according to claim 1, wherein at least a portion of the oil passage communicating with the opening extends in the same direction as the opening.   The lubricating structure for a power transmission device according to claim 1, wherein the power transmission element is a planetary gear device.

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