JP2018189193A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a power transmission device that can appropriately supply oil to an oil passage inside a pinion shaft while restraining the whole device from being upsized in an axial direction.SOLUTION: A planetary gear mechanism 3 comprises a carrier C3 for rotatably supporting a pinion gear P3 via a pinion shaft 32. A differential gear mechanism 5 comprises a differential case D5 provided integrally with the carrier C3. A shaft inside oil passage 30 comprising an opening part 31 on a second side L2 is formed inside the pinion shaft 32. A communication passage 57 for causing an inside space 50 of the differential case D5 and the opening part 31 of the shaft inside oil passage 30 to communicate with each other is formed in the differential case D5.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a power transmission device including a planetary gear mechanism and a bevel gear-type differential gear mechanism arranged coaxially with the planetary gear mechanism.

  An example of the power transmission device as described above is disclosed in Japanese Unexamined Patent Application Publication No. 2007-120519 (Patent Document 1). As shown in FIGS. 2 and 5 of Patent Document 1, the power transmission device of Patent Document 1 includes a planetary gear type reduction mechanism (24), which is a planetary gear mechanism, and a planetary gear type reduction mechanism (24). And a differential device (26) which is a bevel gear type differential gear mechanism arranged coaxially. This power transmission device is configured such that the differential (26) distributes and outputs the rotation of the electric motor (14) decelerated by the planetary gear speed reduction mechanism (24) to the pair of axles (20A, 20B). Has been. In the description of the background art, the reference numerals shown in parentheses are those of Patent Document 1.

  In the power transmission device of Patent Document 1, the planetary carrier (44) of the planetary gear type reduction mechanism (24) is formed integrally with the differential case (58) of the differential device (26). In order to supply a sufficient amount of lubricating oil to the planetary pinion portion of the planetary gear type speed reduction mechanism (24), the planetary carrier (44) is provided at the end opposite to the differential device (26) in the axial direction. An annular oil catch plate (150) is attached. Specifically, as described in paragraphs 0068-0079 of Patent Document 1, the pinion shaft (43) that rotatably supports the pinion gear (42) has an axial hole (45), and the shaft Lubricating oil supplied to the core hole (45) is supplied to the surface of the pinion shaft (43), the needle bearing (47), and the thrust washers (172, 174) to lubricate them. The oil catch plate (150) is configured to receive the lubricating oil supplied from the radially inner side and guide it to the axial hole (45) of the pinion shaft (43). As a result, a sufficient amount of lubricating oil can be supplied to the pinion shaft (43), and the durability of the pinion shaft (43), the needle bearing (47), and the thrust washers (172, 174) is improved. ing.

JP 2007-120519 A

  However, in the power transmission device of Patent Document 1, since the annular oil catch plate is attached so as to protrude in the axial direction from the axial end surface of the carrier, the power transmission device is more powerful than the case where such an oil catch plate is not attached. The transmission device tends to increase in size in the axial direction.

  Therefore, it is desired to realize a power transmission device that can appropriately supply oil to the oil passage inside the pinion shaft while suppressing an increase in the axial size of the entire device.

  A characteristic configuration of a power transmission device including a planetary gear mechanism and a bevel gear type differential gear mechanism arranged coaxially with the planetary gear mechanism in order from the first side that is one side in the axial direction in view of the above. The planetary gear mechanism includes a carrier that rotatably supports a pinion gear via a pinion shaft, and the differential gear mechanism includes a differential case provided integrally with the carrier, and the differential gear mechanism. A shaft member held in the differential case in a direction along a radial direction with reference to the first direction, a first bevel gear rotatably supported around an axis of the shaft member inside the differential case, A pair of second bevel gears which are arranged separately on both sides in the axial direction with respect to the shaft member inside the differential case and mesh with the first bevel gears, respectively, inside the pinion shaft, Said first in the axial direction A shaft-side oil passage having an opening on the second side opposite to the inner side, and communicating the internal space of the differential case and the opening of the shaft-side oil passage with the differential case The oil path is formed.

According to the above characteristic configuration, the oil supplied to the internal space of the differential case for lubrication of the first bevel gear and the second bevel gear is formed inside the pinion shaft via the communication oil passage. Can be supplied to the oil passage in the shaft. The communication oil passage that enables the oil supply to the in-shaft oil passage is formed in a differential case provided integrally with the carrier that supports the pinion shaft. That is, in the configuration in which the differential case is provided integrally with the carrier, the whole structure in which the differential case is integrated includes a connection portion that connects the portion that supports the pinion shaft and the portion that defines the internal space of the differential case. It is. According to said characteristic structure, a communicating oil path can be formed using such a connection part effectively. Therefore, compared with the case where a dedicated member for supplying oil to the in-shaft oil passage is attached to the axial end surface of the carrier, it is possible to suppress an increase in the size of the entire apparatus in the axial direction.
As described above, according to the above-described characteristic configuration, the power transmission device capable of appropriately supplying oil to the oil passage inside the pinion shaft while suppressing an increase in the axial size of the entire device. Can be realized.

  Further features and advantages of the power transmission device will become clear from the following description of embodiments described with reference to the drawings.

Axial sectional view of a power transmission device according to an embodiment Skeleton diagram of power transmission device according to embodiment The perspective view of the connection member which concerns on embodiment Partial enlarged view of FIG.

  Hereinafter, an embodiment of a power transmission device will be described based on the drawings. FIG. 1 is an axial sectional view of the power transmission device 100, and FIG. 2 is a skeleton diagram of the power transmission device 100. In the present embodiment, the power transmission device 100 is a vehicle drive device that is mounted on a vehicle and drives the wheels 300, and transmits power between the driving force source of the wheels 300 and the wheels 300. That is, the power transmission device 100 is a drive device mounted on, for example, a hybrid vehicle using an internal combustion engine and a rotating electric machine as a driving force source for the wheel 300, or an electric vehicle using a rotating electric machine as a driving force source for the wheel 300. As shown in FIGS. 1 and 2, the power transmission device 100 includes only the rotating electrical machine 2 as a driving force source for the two wheels 300 (the first wheel 301 and the second wheel 302). In the case of a two-wheel drive four-wheel vehicle, an electric vehicle can be realized. In addition, in the case of a four-wheel vehicle driven by four wheels, a hybrid vehicle can be realized by driving the other two wheels with the driving force of the internal combustion engine. Of course, in the case of a four-wheel drive four-wheeled vehicle, the four-wheel drive electric vehicle can also be realized by applying the power transmission device 100 of the present embodiment to the other two wheels.

  In the following description, “driving connection” refers to a state where two rotating elements are connected so as to be able to transmit driving force, and the two rotating elements are connected so as to rotate integrally, or It includes a state in which the two rotating elements are connected so as to be able to transmit the driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, such as a shaft, a gear mechanism, a belt, and a chain. The transmission member may include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device or a meshing engagement device. However, in the planetary gear mechanism and the differential gear mechanism (the primary reduction gear device 3, the differential gear device 5, the first output reduction device 71, and the second output reduction device 72) that will be described below, for each rotating element, “drive connection” "Refers to a state in which three or more rotating elements included in the device are connected to each other without intervening other rotating elements.

  The power transmission device 100 includes a rotating electrical machine 2, output members 9 (first output member 91 and second output member 92) that are drivingly connected to the respective wheels 300, and a primary reduction device 3 that decelerates the rotation of the rotating electrical machine 2. And a differential gear device 5 that distributes the output rotation of the primary reduction gear 3 to the two output members 9. In the present embodiment, the power transmission device 100 is different from the first output reduction device 71 that decelerates the rotation distributed to the first output member 91 side by the differential gear device 5 and transmits the rotation to the first output member 91. And a second output speed reduction device 72 that decelerates the rotation distributed to the second output member 92 side by the moving gear device 5 and transmits it to the second output member 92. In this way, by reducing the rotational speed on the output member 9 side relative to the differential gear device 5 and increasing the torque, the connecting shaft 6 described later (particularly, the first connecting shaft 61 penetrating the rotor 21 of the rotating electrical machine 2). ) Can be prevented from increasing, and the diameter of the rotating electrical machine 2 can be prevented from increasing. In the present embodiment, the primary reduction gear device corresponds to a “planetary gear mechanism”, and the differential gear device 5 corresponds to a “bevel gear type differential gear mechanism”.

  By the way, in general, the rotating electrical machine 2 is smaller in the high rotational speed / low torque type than in the low rotational speed / high torque type. Therefore, the power transmission device 100 includes the first output speed reduction device 71 and the second output speed reduction device 72 in addition to the primary speed reduction device 3 as a speed reduction mechanism that reduces the rotation transmitted from the rotating electrical machine 2 side. By realizing a higher gear ratio, the rotating electrical machine 2 can be reduced in size.

  The rotating electrical machine 2, the primary reduction gear device 3, the differential gear device 5, the first output reduction device 71, the second output reduction device 72, and the output member 9 are accommodated in the case 1. The case 1 includes a bottomed cylindrical case body 13, a body cover 14 that closes an opening opposite to the bottom 16 of the case body 13, a bottom cover 15 that covers the bottom 16 outside the bottom 16, and a case body And an internal partition wall 17 (inner wall) provided to close the opening in the vicinity of the 13 openings. As shown in FIG. 1, the rotating electrical machine 2 and the primary reduction gear 3 are arranged in the internal space of the cylindrical case body 13, and the differential gear device 5, the second output reduction gear 72, and the second output member 92 are The first output speed reduction device 71 and the first output member 91 are disposed in an internal space formed by the bottom cover 15 and the bottom portion 16, and are disposed in an internal space formed by the main body cover 14 and the internal partition wall 17. Yes.

  As described above, the rotating electrical machine 2 is a driving force source for the wheels 300. The rotating electrical machine 2 is a permanent magnet type rotating electrical machine including a rotor 21 having a permanent magnet 23 inside a rotor core 22 and a stator 24 having a stator coil 26 wound around a stator core 25. The rotary shaft 27 is fixed to the rotor core 22 inside the rotor core 22 in the radial direction, and the rotor 21 and the rotary shaft 27 rotate integrally. The rotating shaft 27 is rotatable through bearings (a first rotor bearing 83 and a second rotor bearing 84), respectively, at two different locations along the rotating shaft 27 of the rotating electrical machine 2 (an axial direction L described later). It is supported by the case 1. Here, although the permanent magnet type rotary electric machine is illustrated as the rotary electric machine 2, the rotary electric machine 2 may be another type of rotary electric machine such as an induction type rotary electric machine.

  The power transmission device 100 includes a primary reduction gear 3 and a differential gear device 5 arranged coaxially with the primary reduction gear 3 in order from the first side L1 which is one side in the axial direction L. The axial direction L is an axial direction based on the primary reduction gear 3 and also an axial direction based on the differential gear device 5. Hereinafter, the side opposite to the first side L1 in the axial direction L is referred to as a second side L2. In the present embodiment, the rotating electrical machine 2, the first output speed reduction device 71, the second output speed reduction device 72, and the two output members 9 are also arranged coaxially with the primary speed reduction device 3. The rotating electrical machine 2 is disposed on the first side L1 relative to the primary reduction gear 3, and the first output speed reducing device 71 and the first output member 91 are disposed on the first side L1 relative to the rotating electrical machine 2. In addition, the second output speed reduction device 72 and the second output member 92 are disposed on the second side L <b> 2 with respect to the differential gear device 5. The rotating shaft 27 of the rotating electrical machine 2 described above is supported on the bottom 16 of the case 1 via the first rotor bearing 83 on the first side L1 from the rotor core 22, and the second rotor bearing on the second side L2 from the rotor core 22. It is supported by the internal partition wall 17 of the case 1 via 84.

  The primary reduction gear 3 is a planetary gear type gear mechanism. The primary reduction gear 3 is disposed between the rotating electrical machine 2 and the differential gear device 5 in the power transmission path. In the present embodiment, the primary reduction gear 3 decelerates the rotation of the rotating electrical machine 2 (amplifies the torque of the rotating electrical machine 2) and transmits it to the differential gear device 5. The primary reduction gear 3 is a single pinion type planetary gear mechanism including a sun gear S3, a carrier C3, and a ring gear R3. The sun gear S3 is an input element of the primary reduction gear 3 and is drivingly connected to the rotating electrical machine 2. Specifically, the sun gear S3 is coupled to rotate integrally with the rotating shaft 27 of the rotating electrical machine 2. The ring gear R3 is fixed to the case 1 (here, the internal partition wall 17) which is a non-rotating member. The carrier C3 is an output element of the primary reduction gear 3, and is rotatably supported by the case 1 (here, the internal partition wall 17) via a bearing (first input bearing 88).

  As shown in FIG. 4, the carrier C <b> 3 supports the pinion gear P <b> 3 via the pinion shaft 32 so as to be freely rotatable. The pinion shaft 32 is supported from both sides in the axial direction L by the carrier C3 in a state where both end portions in the axial direction L are inserted into holes formed in the carrier C3. The pinion shaft 32 is secured to the pinion 33 in a state where the rotation with respect to the hole (rotation around the axis of the pinion shaft 32) is restricted by the pin 33. The pinion shaft 32 rotatably supports the pinion gear P3 while being disposed so as to penetrate the pinion gear P3 in the axial direction L. Although illustration is omitted, a plurality of (for example, three or four) pinion shafts 32 are arranged at equal intervals along a circumferential direction (a circumferential direction with reference to the primary reduction gear 3), and each of the pinion shafts 32 is One pinion gear P3 is rotatably supported.

  The differential gear device 5 is a bevel gear type differential gear mechanism. The differential gear device 5 is disposed between the primary reduction device 3 and the first output reduction device 71 and the second output reduction device 72 in the power transmission path, and is transmitted from the rotating electrical machine 2 via the primary reduction device 3. The driving force is distributed to the first output reduction device 71 and the second output reduction device 72 (distributed to the first output member 91 and the second output member 92) and output. The differential gear device 5 is rotatably supported around the axis A of the shaft member F5 inside the differential case D5, the shaft member F5 held by the differential case D5, and the differential case D5. And a pair of second bevel gears B5 as distribution output elements. The shaft member F5 is oriented along the radial direction (hereinafter referred to as “radial direction R”) with respect to the differential gear device 5, that is, the direction along the axis A of the shaft member F5 is the radial direction R. They are arranged in parallel orientation. The shaft member F5 supports the first bevel gear P5 rotatably with respect to the shaft member F5 in a state where the shaft member F5 is disposed so as to penetrate the first bevel gear P5 in the radial direction R. The pair of second bevel gears B5 are arranged separately on both sides in the axial direction L with respect to the shaft member F5 inside the differential case D5, and mesh with the first bevel gears P5, respectively.

  The pair of second bevel gears B <b> 5 are rotating elements after distribution in the differential gear device 5. When the torque of the rotating electrical machine 2 is input to the differential case D5 via the primary reduction gear 3, the first bevel gear P5 revolves with the rotation of the differential case D5, so that the pair of second bevel gears B5 Driven by rotation. At this time, if a difference in rotational resistance occurs between the first wheel 301 and the second wheel 302 due to the vehicle traveling on a curved road or the like, the first bevel gear P5 rotates to rotate, and the pair of second bevels. The gear B5 rotates at different speeds. Hereinafter, the second bevel gear B5 disposed on the first side L1 with respect to the shaft member F5 of the pair of second bevel gears B5 is referred to as a first side gear B51 (first distribution output element), and the pair of second bevel gears. The second bevel gear B5 disposed on the second side L2 with respect to the shaft member F5 of the gear B5 is defined as a second side gear B52 (second distribution output element). As will be described later, the first side gear B51 is drivingly connected to a first sun gear S71 that is an input element of the first output reduction device 71, and the second side gear B52 is a second element that is an input element of the second output reduction device 72. Drive coupled to the sun gear S72.

  As shown in FIG. 4, the differential gear device 5 includes a flat plate-shaped first washer 85 disposed between the differential case D5 and the second bevel gear B5 in the axial direction L, and a differential in the radial direction R. A curved plate-like second washer 86 disposed between the case D5 and the first bevel gear P5. The first washer 85 receives a thrust load in the axial direction L, and the second washer 86 receives a load in a direction (radial direction R) along the axis A of the shaft member F5.

  In the present embodiment, the differential gear device 5 includes two first bevel gears P5. When two first bevel gears P5 are provided in this way, the two first bevel gears P5 can be rotatably supported by one common shaft member F5. Then, two shaft members F5 are provided corresponding to the two first bevel gears P5, and each of the two shaft members F5 rotatably supports one first bevel gear P5. Specifically, each of the shaft members F5 has a cylindrical shape with one end in the direction along the axis A (the outer end in the radial direction R) inserted into a hole formed in the differential case D5. The fixing member 56 (pin) is fixed to prevent the rotation around the axis A while being restricted. In addition, each of the shaft members F5 is inserted into an insertion hole 41 whose other end in the direction along the axis A (the inner end portion in the radial direction R) is open to the outside in the radial direction R formed in the connecting member 4. Thus, the two shaft members F5 are connected by the connecting member 4. In this example, as shown in the perspective view of FIG. 3, the connecting member 4 is a columnar member, and the respective shaft members F5 are fitted at two positions on the peripheral wall 43 symmetric with respect to the center. An insertion hole 41 is formed. The connecting member 4 is formed with a through hole 45 that penetrates the center of the bottom surface in the axial direction L. Specifically, the connecting member 4 includes a pair of fitting recesses 42 into which opposite ends of a pair of connecting shafts 6 (a first connecting shaft 61 and a second connecting shaft 62) to be described later are fitted, respectively. The through hole 45 is formed so that the bottom surfaces of the pair of fitting recesses 42 communicate with each other. The through hole 45 communicates with a supply oil passage 60 (described later) formed at the center of the connecting shaft 6.

  As shown in FIG. 4, the differential case D <b> 5 is provided integrally with a carrier C <b> 3 that is an output element of the primary reduction gear 3. That is, the differential case D5 is formed integrally with the carrier C3 or connected so as to rotate integrally with the carrier C3. In the present embodiment, the differential case D5 is formed integrally with the carrier C3. The differential case D5 and the carrier C3 are integrally formed using, for example, an integral molding technique by casting (or cutting a cast product), or integrally formed by using an integral molding technique by forging. The The differential case D5 is rotatably supported by supported portions (a first supported portion 58 and a second supported portion 59) provided at two different locations in the axial direction L. The second supported portion 59 is provided on the second side L2 (the second output reduction device 72 side in the axial direction L) from the first supported portion 58. The differential case D5 formed integrally with the carrier C3 of the primary reduction gear 3 extends further to the first side L1 (the side of the rotating electrical machine 2 in the axial direction L) than the primary reduction gear 3, and the first The supported portion 58 is provided on the first side L1 with respect to the primary reduction gear 3. As described above, the carrier C3 of the primary reduction gear 3 is rotatably supported by the internal partition wall 17 via the first input bearing 88. Accordingly, the first supported portion 58 is freely rotatable via the first input bearing 88 by the internal partition wall 17 (inner wall) of the case 1 disposed between the rotating electrical machine 2 and the differential gear device 5 in the axial direction L. It is supported by.

  As shown in FIG. 1, the second supported portion 59 is a second input bearing by a second carrier C72 that is an output element of the second output reduction device 72 (a rotating element that is drivingly connected to the second output member 92). It is rotatably supported via 89. As will be described later, the second carrier C72 and the second output member 92 are coupled so as to rotate integrally, and the second output member 92 is rotatable to the case 1 via the second output bearing 82. It is supported. Therefore, the differential case D5 is rotatably supported by the case 1 via the second input bearing 89, the second carrier C72, and the second output member 92 in the second supported portion 59. As described above, the differential case D5 is rotatably supported with respect to the case 1 at two different positions in the axial direction L.

  The differential gear device 5 distributes the driving force from the rotating electrical machine 2 to the two output members 9 of the first output member 91 and the second output member 92, but the first side gear B 51 and the first output member 91 A first output reduction device 71, which is a planetary gear type differential gear mechanism, is provided in the power transmission path between them, and the planetary gear is provided in the power transmission path between the second side gear B52 and the second output member 92. A second output reduction device 72, which is a differential gear mechanism of the type, is provided. In the present embodiment, the first output reduction device 71 decelerates the rotation of the first side gear B51 and transmits it to the first output member 91, and the second output reduction device 72 decelerates the rotation of the second side gear B52. This is transmitted to the second output member 92. The first output reduction device 71 and the second output reduction device 72 are configured to have the same reduction ratio. The differential gear device 5, the first output reduction device 71 and the second output reduction device 72 are drivingly connected via a pair of connection shafts 6. The connecting shaft 6 is disposed along the axial direction L, and a supply oil passage 60 is formed at the center thereof.

  The differential gear device 5 and the first output reduction device 71 are drivingly connected via a first connection shaft 61, and the differential gear device 5 and the second output reduction device 72 are connected via a second connection shaft 62. Drive coupled. The first output reduction device 71 and the second output reduction device 72 are separately arranged on both sides in the axial direction L with the rotating electrical machine 2, the primary reduction device 3, and the differential gear device 5 interposed therebetween. Specifically, the first output speed reduction device 71, the rotating electrical machine 2, the primary speed reduction device 3, the differential gear device 5, and the second output speed reduction from the first side L1 to the second side L2 along the axial direction L. The devices 72 are arranged in this order. Since the differential gear device 5 and the second output reduction device 72 are adjacent to each other in the axial direction L, the differential gear device 5 can be easily driven and connected via the second connecting shaft 62. The rotary electric machine 2 and the primary reduction gear 3 exist between the first output reduction gear 71 and the first output reduction gear 71. For this reason, the first connecting shaft 61 that drives and connects the differential gear device 5 and the first output reduction gear 71 penetrates the radially inner side of the rotor 21 of the rotating electrical machine 2 in the axial direction L. That is, in the present embodiment, the first connecting shaft 61 corresponds to a “connecting shaft” connected to the bevel gear (first side gear B51) disposed on the first side L1 of the pair of second bevel gears B5. The first connecting shaft 61 is disposed so as to penetrate the rotating electrical machine 2 in the axial direction L and extend to the first side L1 from the rotating electrical machine 2.

  The first connecting shaft 61 is disposed along the axial direction L between the first output reduction device 71 and the differential gear device 5 in the axial direction L, and the second connecting shaft 62 is a differential gear in the axial direction L. It is disposed along the axial direction L between the device 5 and the second output reduction device 72. In addition, with the connecting member 4 of the differential gear device 5 interposed therebetween, the end portion on the second side L2 of the first connecting shaft 61 and the end portion on the first side L1 of the second connecting shaft 62 are in the axial direction L. Opposite. Specifically, the end of the second side L2 of the first connecting shaft 61 is fitted into the fitting recess 42 that opens on the first side L1 formed in the connecting member 4, and is formed in the connecting member 4. The end portion of the first side L1 of the second connecting shaft 62 is fitted into the fitting recess 42 that opens to the second side L2. Accordingly, the first connecting shaft 61, the connecting member 4, and the second connecting shaft 62 are changed from the first output reduction device 71 arranged on the first side L1 to the second output reduction device 72 arranged on the second side L2. Until, it is arranged side by side along the axial direction L. As described above, the supply oil passage 60 is formed at the center of the pair of connection shafts 6 (the first connection shaft 61 and the second connection shaft 62), and the connection member 4 communicates with the supply oil passage 60. A through hole 45 is formed. Accordingly, the supply oil passage 60 communicates along the axial direction L from the first output speed reduction device 71 disposed on the first side L1 to the second output speed reduction device 72 disposed on the second side L2. .

  The first output reduction gear 71 is constituted by a single pinion type planetary gear mechanism including a first sun gear S71, a first carrier C71, and a first ring gear R71. In the first output reduction device 71 provided in the power transmission path between the first side gear B51 and the first output member 91, the first sun gear S71 as an input element is connected to rotate integrally with the first side gear B51. The first ring gear R71 is fixed to the case 1 which is a non-rotating member, and the first carrier C71 as an output element is connected to rotate integrally with the first output member 91. More specifically, the first side gear B51 is connected to rotate integrally with the first connecting shaft 61, and the first connecting shaft 61 and first sun gear S71 are connected to rotate integrally. In the present embodiment, the first connecting shaft 61 and the first sun gear S71 are integrally formed. The first output speed reduction device 71 disposed on the first side L1 is accommodated in a space formed by the bottom 16 and the bottom cover 15 of the case body 13. That is, the first output reduction device 71 is disposed at a position overlapping the bottom cover 15 in the radial direction, and the first ring gear R71 is fixed to the bottom cover 15. In addition, the radial direction here is a radial direction on the basis of the 1st output reduction device 71, and corresponds with the radial direction R in this embodiment.

  The second output reduction device 72 is constituted by a single pinion type planetary gear mechanism including a second sun gear S72, a second carrier C72, and a second ring gear R72. In the second output reduction device 72 provided in the power transmission path between the second side gear B52 and the second output member 92, the second sun gear S72 as an input element is connected to rotate integrally with the second side gear B52. The second ring gear R72 is fixed to the case 1 which is a non-rotating member, and the second carrier C72 as an output element is connected to rotate integrally with the second output member 92. More specifically, the second side gear B52 is connected to rotate integrally with the second connecting shaft 62, and the second connecting shaft 62 and second sun gear S72 are connected to rotate integrally. In the present embodiment, the second connecting shaft 62 and the second sun gear S72 are integrally formed. The second output speed reduction device 72 disposed on the second side L2 is accommodated in a space surrounded by the main body cover 14 and the internal partition wall 17 of the case main body 13. That is, the second output speed reduction device 72 is disposed at a position overlapping the main body cover 14 in the radial direction, and the second ring gear R72 is fixed to the main body cover 14. In addition, the radial direction here is a radial direction on the basis of the 2nd output reduction device 72, and corresponds with the radial direction R in this embodiment.

  The first output member 91 is connected to the first carrier C71 of the first output speed reduction device 71 so as to rotate integrally, and the second output member 92 is rotated to be integrated with the second carrier C72 of the second output speed reduction device 72. It is connected to. In the present embodiment, the first carrier C71 and the first output member 91 are integrally formed, and the second carrier C72 and the second output member 92 are integrally formed. The output member 9 is a cylindrical member that is drivingly connected to a drive shaft 200 that is connected so as to rotate integrally with the wheel 300. The first output member 91 is connected to rotate integrally with the first wheel 301 via the first drive shaft 201, and the second output member 92 rotates integrally with the second wheel 302 via the second drive shaft 202. To be connected.

  In the case 1, along the axial direction L from the first side L1 to the second side L2, the first output member 91, the first output speed reduction device 71, the rotating electrical machine 2, the primary speed reduction device 3, and the differential gear. The device 5, the second output reduction device 72, and the second output member 92 are arranged in the order described. A pair of bearing support portions 10 that support the output bearing 8 are provided at both ends in the axial direction L of the case 1. The first output member 91 and the second output member 92 are rotatably supported by the pair of bearing support portions 10 via the output bearing 8. Specifically, the first bearing support portion 11 that supports the first output bearing 81 is formed on the bottom cover 15 at the end portion of the first side L1 of the case 1. Further, a second bearing support portion 12 that supports the second output bearing 82 is formed in the main body cover 14 at the end portion on the second side L2 side of the case 1. The first output member 91 is rotatably supported by the first bearing support portion 11 via the first output bearing 81, and the second output member 92 is supported by the second bearing support portion 12 via the second output bearing 82. And is supported rotatably.

  Since the output member 9 is supported by the case 1 at both ends in the axial direction L, the coaxially arranged devices can be accommodated and supported in the case 1 with high accuracy and stability. The first output bearing 81 and the second output bearing 82 are angular bearings (Angular Bearing / Angular Contact Ball Bearing), in particular, a combination angular bearing (Matched Mounting Angular Contact) in which a plurality of single row angular bearings are combined. Ball bearings) and double-row angular contact ball bearings having double-row inner and outer rings are preferred. The angular bearing can appropriately support the supported member with respect to both the radial direction R and the axial direction L of the supported member (here, the output member 9). As shown in FIG. 1, the output member 9 is a cylindrical member, and is connected to rotate integrally with the output member 9 in a form in which the drive shaft 200 abuts on the inner surface of the cylindrical portion. That is, the output member 9 and the drive shaft 200 are coupled so as to rotate integrally with a relatively long contact surface in the axial direction L. If the output bearing 8 is, for example, a double-row angular bearing, a long guide can be secured in the axial direction L to support the output member 9, and the load transmitted from the wheel 300 and the drive shaft 200 can be appropriately supported. be able to. Note that the angular bearing is an example, and instead of this, for example, a roller bearing (Roller Bearing) or the like may be preferably used.

  The power transmission device 100 includes a mechanical oil pump 400 that supplies lubricating oil to the rotating electrical machine 2, the primary speed reduction device 3, the differential gear device 5, the first output speed reduction device 71, and the second output speed reduction device 72. I have. The oil pump 400 is disposed at a position where the oil pump 400 and the differential gear device 5 overlap at least partially when viewed in the radial direction R. In the present embodiment, the oil pump 400 is driven by the rotation of the differential case D5 provided integrally with the carrier C3. Specifically, in this embodiment, a drive gear for driving the oil pump 400 is formed on the outer peripheral portion of the differential case D5.

  Generally, the rotational speed of the rotating electrical machine 2 that is a driving force source for the wheels 300 is often higher than the rotational speed of the internal combustion engine when the internal combustion engine is used as a driving force source. The rotational speed (the rotational speed of the carrier C3) after being decelerated by the primary speed reducer 3 approaches the rotational speed of the internal combustion engine. Therefore, when the oil pump 400 is driven by the rotation of the differential case D5 provided integrally with the carrier C3, the oil pump 400 is driven by using the output of the internal combustion engine generally used in automobiles and the like. It can be used appropriately without changing the specifications of the pump.

  The oil discharged from the oil pump 400 passes through an oil passage (not shown) and is supplied to the introduction oil passage 19 of the power transmission device 100. The introduction oil passage 19 is formed in the bottom portion 16 of the case 1 so as to extend along the radial direction R between the rotating electrical machine 2 and the first output reduction gear 71 in the axial direction L. A supplied portion 69 to which lubricating oil is supplied from the introduction oil passage 19 is formed in a portion of the first connecting shaft 61 that is disposed on the first side L1 from the rotating electrical machine 2. Specifically, the first connecting shaft 61 is formed in a cylindrical shape extending in the axial direction L, and a supply oil passage 60 extending in the axial direction L is formed inside the first connecting shaft 61. And the to-be-supplied part 69 is formed by the hole which penetrates the cylindrical part of the 1st connection shaft 61 to radial direction R, and connects the supply oil path 60 and the outer peripheral surface of the 1st connection shaft 61, The oil supplied from the oil pump 400 to the introduction oil passage 19 is supplied from the supplied portion 69 to the supply oil passage 60. As described above, the supply oil passage 60 communicates along the axial direction L from the first output speed reduction device 71 disposed on the first side L1 to the second output speed reduction device 72 disposed on the second side L2. doing. In the connecting shaft 6, holes that penetrate the cylindrical portion of the connecting shaft 6 in the radial direction R and connect the supply oil path 60 and the outer peripheral surface of the connecting shaft 6 are formed at a plurality of positions in the axial direction L. The plurality of holes, the opening of the supply oil passage 60 at the end of the first connection shaft 61 on the first side L1, and the supply oil passage at the end of the second connection shaft 62 on the second side L2. Oil is supplied to the mechanisms arranged in the axial direction L through the 60 openings.

  As described above, the supply oil passage 60 is extended to the second side L <b> 2 from the differential gear device 5 by the through hole 45 provided in the connecting member 4. Accordingly, the oil is appropriately supplied also to the second output speed reduction device 72 disposed on the second side L2 with respect to the differential gear device 5. In order to supply oil to the second output reduction gear 72, it is not necessary to provide a separate oil passage between the differential gear device 5 and the second output reduction gear 72 in the axial direction L. An increase in the size of the transmission device 100 is suppressed.

  Further, as described below, the oil supplied to the supplied portion 69 is supplied to the internal space 50 of the differential case D5, and the oil supplied to the internal space 50 of the differential case D5 is a pinion shaft. The oil is supplied to an in-shaft oil passage 30 formed inside 32. Specifically, as shown in FIG. 4, at the position in the axial direction L corresponding to the differential gear device 5, the cylindrical portion of the first connecting shaft 61 penetrates in the radial direction R and the supply oil passage 60 A hole that communicates with the outer peripheral surface of the first connecting shaft 61 is formed. By this hole, the supply oil passage 60 formed inside the first connecting shaft 61 is passed into the inner space 50 of the differential case D5. An oil passage 64 for supplying oil is formed. That is, the supply oil passage 60 formed inside the first connecting shaft 61 is formed so as to communicate the supplied portion 69 and the internal space 50 of the differential case D5. The oil passage 64 is formed to open to the internal space 50 in a gap formed between the first side gear B51 and the connecting member 4 in the axial direction L. Then, the oil supplied to the internal space 50 of the differential case D5 lubricates the first bevel gear P5, the second bevel gear B5, the first washer 85, the second washer 86, and the like.

  As shown in FIG. 4, the in-shaft oil passage 30 formed inside the pinion shaft 32 has an opening 31 on the second side L2. In the differential case D5, a communication oil passage 57 that connects the internal space 50 and the opening 31 of the in-shaft oil passage 30 is formed. Specifically, the end of the second side L2 of the pinion shaft 32 is fitted into a hole 51 that opens in the first side L1 formed in the differential case D5. The communication oil passage 57 is formed so as to open on the inner surface of the hole 51. The number of holes 51 is the same as the number of pinion shafts 32, and the communication oil passages 57 correspond to the plurality of holes 51 at a plurality of positions in the circumferential direction (circumferential direction based on the primary reduction gear 3). Is formed. By forming the communication oil passage 57 in the differential case D5 in this way, the oil supplied to the internal space 50 of the differential case D5 for lubrication of the first bevel gear P5, the second bevel gear B5, etc. The oil can be supplied to the in-shaft oil passage 30 formed inside the pinion shaft 32 via the communication oil passage 57. In addition, in this way, by supplying the oil to the in-shaft oil passage 30 from the opening 31 facing the outside in the axial direction L in the in-shaft oil passage 30, the oil is supplied to the in-shaft oil passage 30 in the shaft The configuration of the in-shaft oil passage 30 can be simplified as compared with the case where the inner oil passage 30 is opened from an opening facing the outside in the radial direction (the radial direction with respect to the pinion shaft 32). .

  The pinion shaft 32 has a gap between the end surface of the second side L2 of the pinion shaft 32 and the bottom surface of the hole 51 (the surface facing the first side L1 that defines the second side L2 of the hole 51). The communication oil passage 57 opens at a portion where the gap is formed on the inner surface of the hole 51. In the example shown in FIG. 4, the bottom surface of the hole 51 is formed by a conical inner surface that is reduced in diameter toward the second side L2. That is, the inner surface of the hole 51 includes a cylindrical surface to which the end of the second side L2 of the pinion shaft 32 is fitted, and a conical surface formed continuously to the second side L2 with respect to the cylindrical surface. And have. And the end surface of the second side L2 of the pinion shaft 32 is disposed on the first side L1 with respect to the connecting portion between the cylindrical surface and the conical surface (the end portion on the second side L2 of the cylindrical surface). ing. By arranging the pinion shaft 32 in this way, it is possible to smoothly introduce the oil supplied from the communication oil passage 57 into the hole 51 into the in-shaft oil passage 30. In the example shown in FIG. 4, the communication oil passage 57 is formed so as to open to a portion including the connecting portion between the cylindrical surface and the conical surface on the inner surface of the hole 51.

  The in-shaft oil passage 30 is formed in a radial direction (referenced to the pinion shaft 32) from a connecting portion between the axial oil passage 30a extending along the axial direction L from the opening 31 toward the first side L1 and the axial oil passage 30a. And a radial oil passage 30b that opens along the outer peripheral surface of the pinion shaft 32. Therefore, the oil supplied to the opening 31 via the communication oil passage 57 is discharged to the outer peripheral surface of the pinion shaft 32 through the axial oil passage 30a and the radial oil passage 30b in this order. Then, by the oil discharged to the outer peripheral surface of the pinion shaft 32, a pinion gear P3, a pinion bearing 90 disposed between the pinion gear P3 and the pinion shaft 32, and a third washer disposed between the pinion gear P3 and the carrier C3. 87 (thrust washer) or the like is lubricated.

[Other Embodiments]
Next, other embodiments of the power transmission device will be described.

(1) In the above embodiment, a configuration in which the supplied portion 69 to which lubricating oil is supplied is formed in a portion of the first connecting shaft 61 that is disposed on the first side L1 from the rotating electrical machine 2 is an example. As explained. However, the present invention is not limited to such a configuration, and a configuration may be adopted in which the supplied portion 69 is formed in a portion of the first connecting shaft 61 that is disposed on the second side L2 relative to the rotating electrical machine 2.

(2) In the above embodiment, the configuration in which oil is supplied from the oil passage 64 formed in the first connecting shaft 61 to the internal space 50 of the differential case D5 has been described as an example. However, the configuration is not limited to such a configuration, and a configuration in which oil is supplied to the internal space 50 of the differential case D5 from the oil passage formed in the second connecting shaft 62, or the differential case D5 is formed. The oil may be supplied from the oil passage to the internal space 50 of the differential case D5.

(3) In the above embodiment, the oil supplied to the supply oil passage 60 inside the first connecting shaft 61 passes through the through hole 45 provided in the connecting member 4 and is supplied inside the second connecting shaft 62. The configuration supplied to the oil passage 60 has been described as an example. However, without being limited to such a configuration, the supply oil passage 60 inside the first connection shaft 61 and the supply oil passage 60 inside the second connection shaft 62 do not communicate with each other via the connection member 4. The oil may be separately supplied to the supply oil passage 60 inside the first connection shaft 61 and the supply oil passage 60 inside the second connection shaft 62.

(4) In the above-described embodiment, two shaft members F5 are provided corresponding to the two first bevel gears P5, and the two shaft members F5 are connected by the connecting member 4 as an example. . However, the present invention is not limited to such a configuration, and the differential gear device 5 does not include the connecting member 4 and the two first bevel gears P5 are rotatably supported by one common shaft member F5. It can also be. In the above-described embodiment, the differential gear device 5 has been described as an example of a configuration including two first bevel gears P5. However, the differential gear device 5 includes three or more first bevel gears P5. You can also In this case, the differential gear device 5 includes the same number of shaft members F5 as the first bevel gear P5, and the same number of insertion holes 41 as the shaft members F5 are formed in the peripheral wall 43 of the connecting member 4.

(5) In the above embodiment, the configuration in which the differential case D5 is formed integrally with the carrier C3 has been described as an example. However, the present invention is not limited to such a configuration, and the differential case D5 may be connected to the carrier C3 so as to rotate integrally with a fastening bolt or the like.

(6) In the above embodiment, the configuration in which the sun gear S3 is drivingly connected to the rotating electrical machine 2 and the ring gear R3 is fixed to the non-rotating member (case 1) has been described as an example. However, the configuration is not limited to such a configuration, and the ring gear R3 may be drivingly connected to the rotating electrical machine 2 and the sun gear S3 may be fixed to the non-rotating member (case 1).

(7) In the above embodiment, the configuration in which the rotating electrical machine 2 is arranged coaxially with the primary reduction gear 3 has been described as an example. However, the configuration is not limited to such a configuration, and the rotary electric machine 2 may be arranged on a different axis from the primary reduction gear 3. In this case, unlike the above-described embodiment, the supplied portion 69 may be formed in a portion where the rotating electrical machine 2 and the arrangement region in the axial direction L overlap in the first connecting shaft 61.

(8) In the above embodiment, the configuration in which the power transmission device 100 includes the rotating electrical machine 2 has been described as an example. However, the configuration is not limited to such a configuration, and the power transmission device 100 may not include the rotating electrical machine 2. For example, when the power transmission device according to the present disclosure is applied to a vehicle drive device that is used in a vehicle that includes only an internal combustion engine as a wheel driving force source, the power transmission device 100 does not include the rotating electrical machine 2.

(9) In the above embodiment, the configuration in which the power transmission device 100 includes the first output reduction device 71 and the second output reduction device 72 has been described as an example. However, the configuration is not limited to such a configuration, and the power transmission device 100 may be configured not to include the first output reduction device 71 and the second output reduction device 72. Specifically, for example, the first side gear B51 is connected to rotate integrally with the first output member 91, and the second side gear B52 is connected to rotate integrally with the second output member 92. it can.

(10) It should be noted that the configurations disclosed in the above-described embodiments may be applied in combination with the configurations disclosed in the other embodiments unless there is a contradiction (between the embodiments described as other embodiments). (Including combinations) is also possible. Regarding other configurations, the embodiments disclosed herein are merely examples in all respects. Accordingly, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

[Overview of the above embodiment]
Hereinafter, an outline of the power transmission device described above will be described.

  In order from the first side (L1) which is one side in the axial direction (L), a planetary gear mechanism (3) and a bevel gear type differential gear mechanism (5) arranged coaxially with the planetary gear mechanism (3). The planetary gear mechanism (3) includes a carrier (C3) that rotatably supports the pinion gear (P3) via the pinion shaft (32), and The differential gear mechanism (5) has a differential case (D5) provided integrally with the carrier (C3) and a direction along a radial direction (R) with respect to the differential gear mechanism (5). A shaft member (F5) held by the differential case (D5) and a first member rotatably supported around the axis (A) of the shaft member (F5) inside the differential case (D5). Bevel gear (P5) and the shaft member (F5) inside the differential case (D5) And a pair of second bevel gears (B5) arranged separately on both sides in the axial direction (L) and meshing with the first bevel gear (P5), respectively, inside the pinion shaft (32) An in-shaft oil passage (30) having an opening (31) is formed on a second side (L2) opposite to the first side (L1) in the axial direction (L), and the differential case In (D5), a communication oil passage (57) is formed which communicates the internal space (50) of the differential case (D5) with the opening (31) of the in-shaft oil passage (30).

According to the above configuration, the oil supplied to the internal space (50) of the differential case (D5) for lubricating the first bevel gear (P5), the second bevel gear (B5), etc. Through (57), the oil can be supplied to the in-shaft oil passage (30) formed inside the pinion shaft (32). The communication oil passage (57) that enables the oil supply to the in-shaft oil passage (30) as described above is provided integrally with the carrier (C3) that supports the pinion shaft (32). (D5). That is, in the configuration in which the differential case (D5) is provided integrally with the carrier (C3), the entire structure in which the differential case (D5) is integrated, the portion that supports the pinion shaft (32) and the internal space of the differential case (D5). The connection part which connects the part which divides (50) is contained. According to said structure, a communicating oil path (57) can be formed using such a connection part effectively. Therefore, compared with the case where a dedicated member for supplying oil to the in-shaft oil passage (30) is attached to the axial end surface of the carrier (C3), the size of the entire apparatus in the axial direction (L) is increased. Can be suppressed.
As mentioned above, according to said structure, oil is appropriately supplied with respect to the oil path (30) inside a pinion shaft (32), suppressing the enlargement of the axial direction (L) of the whole apparatus. It is possible to realize a power transmission device (100) that can be used.

  Here, the rotating electrical machine (2) arranged coaxially with the planetary gear mechanism (3) is further provided, and the planetary gear mechanism (3) includes the carrier (C3), the sun gear (S3), and the ring gear (R3). A single pinion type planetary gear mechanism, wherein one of the sun gear (S3) and the ring gear (R3) is drivingly connected to the rotating electrical machine (2), and the other of the sun gear (S3) and the ring gear (R3) is It is preferable to be fixed to the non-rotating member (1).

  According to this configuration, the rotation of the rotating electrical machine (2) can be reduced by the planetary gear mechanism (3) and transmitted to the differential case (D5) of the differential gear mechanism (5). It becomes easy to appropriately secure the magnitude of the torque output from the pair of second bevel gears (B5) in (5). Further, since the rotating electrical machine (2) is coaxially arranged with the planetary gear mechanism (3), the planetary gear mechanism (3), the differential gear mechanism (5), and the rotating electrical machine (2) are all coaxially arranged, It is also possible to reduce the size of the entire apparatus in the radial direction (R).

  The rotating electrical machine (2) is coaxially disposed with the planetary gear mechanism (3), and the rotating electrical machine (2) is disposed closer to the first side (L1) than the planetary gear mechanism (3). The connecting shaft (61) connected to the bevel gear (B51) disposed on the first side (L1) of the pair of second bevel gears (B5) serves as the shaft for the rotating electrical machine (2). It arrange | positions so that it may penetrate to a direction (L) and may extend to the said 1st side (L1) rather than the said rotary electric machine (2), The said 1st side rather than the said rotary electric machine (2) in the said connection shaft (61). L1) is provided with a portion to be supplied (69) to which lubricating oil is supplied, and inside the connecting shaft (61) the difference between the portion to be supplied (69) and the difference It is preferable that a supply oil passage (60) communicating with the internal space (50) of the moving case (D5) is formed. A.

  According to this configuration, the connecting shaft (61) connected to the bevel gear (B51) disposed on the first side (L1) of the pair of second bevel gears (B5) is provided by the rotating electrical machine (2). Is also arranged to extend to the first side (L1), so that the rotating electrical machine (2) is coaxial with the planetary gear mechanism (3) and arranged on the first side (L1). Torque output from the bevel gear (B51) disposed on the first side (L1) can be appropriately transmitted to the member disposed on the first side (L1) rather than the rotating electrical machine (2). . And according to said structure, the to-be-supplied part (69) to which the oil for lubrication is supplied is rotated by forming a supply oil path (60) in the connecting shaft (61) arrange | positioned in this way. It can be provided on the first side (L1) from the electric machine (2). When the rotating electrical machine (2) is disposed coaxially with the planetary gear mechanism (3) and on the first side (L1), the rotating electrical machine (2), the planetary gear mechanism (3), and the differential gear mechanism ( 5) are arranged side by side in the axial direction (L), since a connecting member for connecting the rotating members, a support structure for supporting the rotating members, and the like are arranged in such an axial region. If the supplied part (69) is provided, the entire apparatus may be increased in size in the axial direction (L). On the other hand, according to the above configuration, the supplied portion (69) can be provided on the first side (L1) from the rotating electrical machine (2) while avoiding such an axial region, and thus the apparatus It is possible to provide an oil supply structure to the internal space (50) of the differential case (D5) while suppressing an increase in the size of the entire axial direction (L).

  Further, the pinion shaft (32) is fitted with an end portion on the second side (L2) in a hole portion (51) opened on the first side (L1) formed in the differential case (D5). The communication oil passage (57) is preferably formed so as to open on the inner surface of the hole (51).

  According to this configuration, the oil is supplied from the communication oil passage (57) to the in-shaft oil passage (30) of the pinion shaft (32) in a space at least partially partitioned by the inner surface of the hole (51). Therefore, the oil discharged from the communication oil passage (57) can be efficiently supplied to the in-shaft oil passage (30) with a simple configuration.

  The power transmission device according to the present disclosure only needs to exhibit at least one of the effects described above.

1: Case (non-rotating member)
2: Rotating electrical machine 3: Primary reduction gear (planetary gear mechanism)
5: Differential gear unit (bevel gear type differential gear mechanism)
30: Inner shaft oil passage 31: Opening portion 32: Pinion shaft 50: Inner space 51: Hole 57: Communication oil passage 60: Supply oil passage 61: First connecting shaft (connecting shaft)
69: Supply part 100: Power transmission device A: Shaft center B5: Second bevel gear C3: Carrier D5: Differential case F5: Shaft member L: Axial direction L1: First side L2: Second side P3: Pinion gear P5 : First bevel gear R: radial direction R3: ring gear S3: sun gear

Claims (4)

In order from the first side which is one side in the axial direction, a power transmission device comprising a planetary gear mechanism and a bevel gear type differential gear mechanism arranged coaxially with the planetary gear mechanism,
The planetary gear mechanism includes a carrier that rotatably supports a pinion gear via a pinion shaft,
The differential gear mechanism includes a differential case provided integrally with the carrier, a shaft member held by the differential case in a radial direction with respect to the differential gear mechanism, and the difference A first bevel gear supported rotatably around the axis of the shaft member inside the moving case, and arranged separately on both sides in the axial direction with respect to the shaft member inside the differential case. A pair of second bevel gears respectively meshing with the first bevel gears,
An in-shaft oil passage having an opening on the second side opposite to the first side in the axial direction is formed inside the pinion shaft,
A power transmission device in which a communication oil passage is formed in the differential case to communicate the internal space of the differential case with the opening of the in-shaft oil passage. A rotating electrical machine disposed coaxially with the planetary gear mechanism;
The planetary gear mechanism is a single pinion type planetary gear mechanism including the carrier, a sun gear, and a ring gear;
One of the sun gear and the ring gear is drivingly connected to the rotating electrical machine,
The power transmission device according to claim 1, wherein the other of the sun gear and the ring gear is fixed to a non-rotating member. A rotating electrical machine disposed coaxially with the planetary gear mechanism;
The rotating electrical machine is disposed on the first side with respect to the planetary gear mechanism,
A connecting shaft connected to the bevel gear disposed on the first side of the pair of second bevel gears extends through the rotating electrical machine in the axial direction to the first side than the rotating electrical machine. Arranged as
A supply portion to which lubricating oil is supplied is formed in a portion of the connection shaft that is disposed on the first side of the rotating electrical machine, and the supply portion is provided inside the connection shaft. The power transmission device according to claim 1, wherein a supply oil passage that communicates with the internal space of the differential case is formed. The pinion shaft has an end portion on the second side fitted in a hole portion opened on the first side formed in the differential case,
The power transmission device according to any one of claims 1 to 3, wherein the communication oil passage is formed so as to open to an inner surface of the hole.

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