WO2023190129A1

WO2023190129A1 - Drive transmission device for vehicle

Info

Publication number: WO2023190129A1
Application number: PCT/JP2023/011764
Authority: WO
Inventors: 三治広明; 五島弘喜; 石川佳樹
Original assignee: 株式会社アイシン
Priority date: 2022-03-30
Filing date: 2023-03-24
Publication date: 2023-10-05

Abstract

A drive transmission device (10) comprises: a speed-reduction planetary gear mechanism (20) for reducing the speed of rotation of an input shaft (15) and transmitting the speed-reduced rotation to an output shaft (16); and a case (50) that stores the planetary gear mechanism (20). A scraping-up part (35) for scraping-up oil in the case (50) is provided to the outer peripheral part of a carrier (30) of the planetary gear mechanism (20). The scraping-up part (35) is disposed on one side in an axial direction (X) with respect to a ring gear (25). The lower end (Tf) of the scraping-up part (35) in a rotation trajectory is disposed on a lower side (Z2) lower than the lower end (Tp) of a pinion (22) in the rotation trajectory. An oil supply path (Rt) through which the oil scraped-up by the scraping-up part (35) flows to a lubrication necessary part (70) is formed in the case (50).

Description

Vehicle drive transmission device

The present invention relates to a vehicle drive transmission device equipped with a planetary gear mechanism.

A vehicle drive transmission device is known that includes a planetary gear mechanism and a scraping part for scraping up oil in a case. Patent Document 1 describes a vehicle drive transmission device including a stirring blade that rotates together with a carrier to scrape up oil in a stirring chamber.

JP2021-095952A

However, the vehicle drive transmission device described in Patent Document 1 has a configuration in which the oil in the stirring chamber is scraped up by the stirring blade, and the lower end of the revolution trajectory of the pinion is arranged below the lower end of the stirring blade. Therefore, there was a problem in that the proportion of the pinion immersed in oil tends to increase, and the amount of oil agitation tends to increase.

Therefore, in a configuration in which oil is scraped up using the rotation of a planetary gear mechanism, it is desired to realize a technology that can suppress the agitation of oil by the pinion.

In view of the above, the characteristic configuration of a vehicle drive transmission device includes an input shaft that is drivingly connected to a drive source, an output shaft that is drivingly connected to a wheel, and a system that decelerates the rotation of the input shaft and transmits it to the output shaft. A vehicle drive transmission device comprising a planetary gear mechanism for deceleration and a case accommodating the planetary gear mechanism, the planetary gear mechanism being connected to the input shaft so as to rotate integrally with the input shaft. a sun gear; a carrier that supports a pinion and is connected to rotate integrally with the output shaft; and a ring gear that is fixed to the case; A scraping part for scraping up is provided, the direction along the rotational axis of the carrier is the axial direction, and the direction along the vertical direction is the vertical direction, and the scraping part is arranged in one direction in the axial direction with respect to the ring gear. The lower end of the rotational trajectory of the scraping part is arranged below the lower end of the revolving trajectory of the pinion, and the oil scraped up by the scraping part is directed to areas requiring lubrication in the case. An oil supply path is formed to allow the oil to flow.

According to this characteristic configuration, even if the oil level is below the lower end of the pinion's orbit, the scraping part can scrape up the oil and supply oil to the parts that require lubrication, so the pinion can It is easy to reduce the oil agitation caused by the pinion by reducing the immersion ratio. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.

Further features and advantages of the technology according to the present disclosure will become clearer from the following description of exemplary and non-limiting embodiments, written with reference to the drawings.

A schematic diagram of a vehicle equipped with a vehicle drive transmission device according to an embodiment of the present invention A cross-sectional view of a vehicle drive transmission device according to a first embodiment Schematic diagram of the side view of the vehicle drive transmission device in Figure 2 An enlarged view of the upper part of the vehicle drive transmission device in FIG. 2 An enlarged view showing the lower part of the vehicle drive transmission device in FIG. 2 A sectional view of a vehicle drive transmission device according to a second embodiment A diagram showing another example of a vehicle equipped with a vehicle drive transmission device according to an embodiment of the present invention.

[First embodiment]
Below, a vehicle drive transmission device (hereinafter referred to as a drive transmission device) 10 according to a first embodiment will be described with reference to FIGS. 1 to 5.

FIG. 1 is a schematic diagram of a vehicle 11 equipped with a drive transmission device 10. FIG. 2 is a sectional view of the drive transmission device 10. FIG. 3 is a schematic side view of the drive transmission device 10 viewed from the first axial side X1. The drive transmission device 10 is mounted on a vehicle 11 that includes a drive source 12 such as a rotating electric machine, a differential gear device 13, and wheels 14, for example. The differential gear device 13 distributes the driving force input from the drive source 12 via the drive transmission device 10 to the pair of wheels 14 . Note that in this application, the term "rotating electric machine" is used as a concept that includes a motor (electric motor), a generator (generator), and, if necessary, a motor/generator that functions as both a motor and a generator.

The drive transmission device 10 includes an input shaft 15 drivingly connected to a drive source 12, an output shaft 16 drivingly connected to the wheels 14, and a deceleration planet that decelerates the rotation of the input shaft 15 and transmits it to the output shaft 16. It includes a gear mechanism 20 and a case 50 that accommodates the planetary gear mechanism 20. In this embodiment, the input shaft 15 and the output shaft 16 are arranged coaxially, and the input shaft 15 and the output shaft 16 are arranged side by side in the axial direction X, which will be described later. Further, in this embodiment, the input shaft 15 is rotatably supported with respect to the case 50 by an input bearing 71. Further, the output shaft 16 is rotatably supported with respect to the case 50 by an output bearing 72. In the illustrated example, the input shaft 15 is supported by a pair of input bearings 71. Further, the output shaft 16 is supported by a pair of output bearings 72.

In addition, in this application, "drive connection" refers to a state in which two rotating elements are connected so that driving force can be transmitted, and a state in which the two rotating elements are connected so that they rotate integrally, or a state in which the two rotating elements are connected so that they rotate integrally. It is used as a concept that includes a state in which two rotating elements are connected so that driving force can be transmitted via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at variable speeds, and include, for example, shafts, gear mechanisms, belts, chains, and the like. Furthermore, such a 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.

The planetary gear mechanism 20 includes a sun gear 21 connected to rotate integrally with the input shaft 15 , a carrier 30 supporting a pinion 22 and connected to rotate integrally with the output shaft 16 , and a case 50 . A ring gear 25 is fixed to the ring gear 25. In this embodiment, the sun gear 21 is formed at the end of the input shaft 15. In this embodiment, the outer peripheral portion of the ring gear 25 is fixed to the case 50. In the illustrated example, ring gear 25 is an internal gear. Further, in this embodiment, the sun gear 21 and the input shaft 15 that rotate integrally function as the input member 10n of the drive transmission device 10. Further, in this embodiment, the carrier 30 and the output shaft 16 that rotate integrally function as the output member 10t of the drive transmission device 10. Note that the input member 10n of the drive transmission device 10 and the input shaft 15 may be separate members and may be drivingly connected to each other. Further, the output member 10t of the drive transmission device 10 and the output shaft 16 may be separate members and may be drivingly connected to each other.

Here, the direction along the rotational axis Xc of the carrier 30 is defined as the axial direction X. Further, the direction perpendicular to the rotational axis Xc is defined as a radial direction R, and the direction of rotation around the rotational axis Xc is defined as a circumferential direction C. Further, a direction along the vertical direction is defined as an up-down direction Z. Further, in the axial direction X, the side where the output shaft 16 is arranged with respect to the input shaft 15 (the right side in FIG. 2) is defined as a first axial side X1, and the opposite side is defined as a second axial side X2.

The planetary gear mechanism 20 may be a single pinion type or a double pinion type. In this embodiment, a single pinion type planetary gear mechanism is used, and each of the pinions 22 distributed in a plurality along the circumferential direction C is configured to mesh with both the sun gear 21 and the ring gear 25. . The plurality of pinions 22 are each supported by a pinion shaft 23 fixed to the carrier 30 via a pinion bearing 73. Thereby, each of the plurality of pinions 22 is configured to be freely rotatable around the pinion shaft 23 (that is, freely rotatable) and rotatably around the rotation axis Xc of the carrier 30 (that is, freely revolve).

A scraping part 35 for scraping up oil inside the case 50 is provided on the outer circumference of the carrier 30. In this embodiment, the scraping part 35 is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part 32 provided on the carrier 30. Specifically, the scraping part 35 is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange part 32. Here, the helical direction of the helical gear-shaped portion is such that oil is blown toward the first side X1 in the axial direction by the rotation of the scraping portion 35 while the vehicle 11 is moving forward. .

When the portion of the carrier 30 that supports the pinion shaft 23 is the carrier body portion 31, the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31. In this embodiment, the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31 and to also protrude on the first axial side X1 (right side in FIG. 2). Further, the flange portion 32 is formed in an annular shape. The flange portion 32 may be integrally formed with the same member as the carrier body portion 31, or may be a separate member from the carrier body portion 31 and connected to rotate integrally with the carrier body portion 31. good. For example, the flange portion 32 and the carrier body portion 31 may be fastened together with bolts, or may be integrally fixed by welding or the like. Alternatively, the flange portion 32 and the carrier body portion 31 may be connected to rotate integrally by spline engagement or the like. Further, the flange portion 32 may be fixed to the carrier body portion 31 such that the central axis of the scraping portion 35 is coaxial with the rotation axis Xc of the carrier body portion 31, or the central axis of the scraping portion 35 may be The flange portion 32 may be fixed to the carrier body portion 31 such that the flange portion 32 has an eccentric positional relationship with respect to the rotation axis Xc of the carrier body portion 31. In this embodiment, the flange portion 32 is a separate member from the carrier body portion 31, and is integrated with the carrier body portion 31 by welding. FIG. 4 is an enlarged view of the upper part of the drive transmission device 10. As shown in FIG. FIG. 5 is an enlarged view of the lower part of the drive transmission device 10. As shown in FIG.

The scraping part 35 is arranged on one side of the ring gear 25 in the axial direction X. In this embodiment, with respect to the ring gear 25 in the axial direction X, the side on which the scraping portion 35 is arranged is the first axial side X1, and the opposite side is the second axial side X2. In the illustrated example, the scraping portion 35 and the ring gear 25 are arranged adjacent to each other in the axial direction X without any other member being sandwiched between them. Note that another member, such as a rib provided on the case 50 or another member, may be arranged between the scraping part 35 and the ring gear 25.

As shown in FIG. 3, the lower end Tf of the rotational trajectory of the scraping unit 35 is located below the lower end Tp of the revolutional trajectory of the pinion 22 Z2. In the illustrated example, the lower end Tf is shown as the lower end of the outer edge Cf on the rotation locus of the rake-up portion 35, and the lower end Tp is shown as the lower end of the tip circle Cp on the revolution locus of the pinion 22. In this embodiment, as described above, the scraping portion 35 is formed on the outer circumferential surface of the flange portion 32 that protrudes outward in the radial direction R with respect to the carrier body portion 31. Therefore, the scraping portion 35 is provided at the outermost peripheral edge of the carrier 30. Note that if the lower end Tf of the rotation locus of the rake-up portion 35 is located below the lower end Tp of the revolution locus of the pinion 22, the scraping portion 35 is located at the outermost peripheral edge of the carrier 30. It does not need to be provided, and may be provided, for example, on the outer periphery of a portion of the carrier 30 that is located inside the outermost periphery.

In this embodiment, the input shaft 15 is integrally formed with the sun gear 21 of the planetary gear mechanism 20. The output shaft 16 is connected to the carrier 30 so as to rotate together with the carrier 30. In the illustrated example, the output shaft 16 includes an output shaft main body portion 16a formed in the shape of a shaft, and an output shaft flange portion 16b formed in the shape of a flange. In this example, the output shaft flange portion 16b is formed to protrude outward in the radial direction R from the end of the output shaft main body portion 16a on the second axial side X2. Further, the output shaft flange portion 16b is formed into a disk shape. A first spline engagement portion 16c for connecting to the carrier 30 is formed on the outer peripheral surface of the output shaft flange portion 16b. Further, in this embodiment, a second spline engagement portion 32a that engages with the first spline engagement portion 16c is formed on the inner circumferential surface of the flange portion 32 of the carrier 30.

As described above, in this embodiment, the flange portion 32 is formed to protrude toward the first axial side X1 with respect to the carrier body portion 31. A second spline engagement portion 32 a is formed on the inner peripheral surface of the protruding portion of the flange portion 32 . In the example shown in FIGS. 4 and 5, a snap ring 36 is locked to the second spline engagement portion 32a. The snap ring 36 is disposed on the first axial side X1 with respect to the first spline engagement portion 16c, and the output shaft flange portion 16b is sandwiched between the snap ring 36 and the carrier body portion 31 in the axial direction X. It is arranged according to the following. As a result, in this embodiment, the carrier main body portion 31, the flange portion 32, and the output shaft flange portion 16b are integrated.

In this embodiment, the parking gear 40 is arranged on the second axial side X2 with respect to the carrier 30 and the ring gear 25. In this example, the parking gear 40 is fixed to the input shaft 15 so as to rotate integrally with the input shaft 15. Specifically, the parking gear 40 is connected to the input shaft 15 by spline engagement so as to rotate together with the input shaft 15.

An oil supply path Rt is formed in the case 50 to flow the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication. The oil supply path Rt may be configured by a groove or rib provided on the inner surface of the case 50, a through hole formed in the case 50, the inner surface of the case 50 itself, or a combination of some or all of these. In this embodiment, from the opposing inner circumferential surface 53, the upper recess 54, the oil receiving surface 54a, the side wall surface 55, the oil groove 57, the protruding part 58, the protruding outer circumferential surface 58a, the protruding end surface 58b, and the first communicating oil passage 61, which will be described later. The fourth communicating oil passage 64 and the like function as an oil supply route Rt.

In this embodiment, the lubrication required portion 70 includes a first input bearing 71a and a second input bearing 71b, which are a pair of input bearings 71 that rotatably support the input shaft 15 with respect to the case 50, and the output shaft 16. A first output bearing 72a and a second output bearing 72b, which are output bearings 72 rotatably supported with respect to the case 50, are included. Furthermore, in this embodiment, the lubrication-requiring locations 70 include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30. Further, a meshing portion between the pinion 22 and the ring gear 25, a meshing portion between the pinion 22 and the sun gear 21, etc. may be included. Further, in this embodiment, the input bearing 71 and the output bearing 72 are also included in the locations 70 requiring lubrication.

As shown in FIG. 2, in this embodiment, the case 50 includes a first case part 50a and a second case part 50b that are liquid-tightly fastened to each other with bolts 42. The internal space of the case 50 is a liquid-tight space, and the lower part of the case 50 serves as an oil storage section for storing oil. In this embodiment, the oil in the case 50, that is, the oil in the oil storage section, is scooped up by the scooping section 35 and is supplied to the lubrication required location 70 through the oil supply path Rt. Note that the case 50 is a non-rotating member.

Preferably, the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state is lower than the lower end Tp of the revolution locus of the pinion 22 and lower than the lower end Tf of the rotation locus of the scraping part 35. The oil amount is set so that the upper side Z1 is also reached. Here, the steady running state is a state in which each rotating member inside the drive transmission device 10 is rotating at a speed that stabilizes the oil level height L1 in the case 50 as the vehicle 11 runs. be. With such a setting, the stirring of oil by the pinion 22 can be suppressed to a small level. Further, it is preferable that the oil level height L2 in the case 50 when the vehicle 11 is stopped for a long period of time is set to be equal to or higher than the pinion bearing 73. Here, the long-term stopped state is a state in which most of the oil in the case 50 falls into the oil storage part and the oil level height L1 in the case 50 is the highest. With such a setting, oil can be supplied to the pinion bearing 73 even if the engine has been stopped for a long period of time. Therefore, when the vehicle 11 starts running after being stopped for a long time, the plurality of pinion bearings 73 provided on the carrier 30 can be immersed in oil in order in the rotational direction, and oil is supplied to the pinion bearings 73. It can be in a state where

As shown in FIG. 3, in this embodiment, the case 50 includes an opposing inner circumferential surface 53 that faces the scraping portion 35 from the outside in the radial direction R. This opposing inner circumferential surface 53 is arranged above the rotational axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X. It has a receiving surface 54a. By providing such an oil receiving surface 54a, the oil scraped up by the scraping part 35 is received at the upper side Z1 of the scraping part 35, and the oil is flowed from there along the oil supply route Rt using gravity. be able to. In the illustrated example, the oil receiving surface 54a is arranged to be perpendicular to the tangent to the outer edge Cf. More specifically, the oil receiving surface 54a is arranged to be perpendicular to the tangent at the upper end of the outer edge Cf. In this embodiment, an upper recess 54 is formed in the opposing inner circumferential surface 53 in which a portion facing the upper end region of the rotation locus of the scraping portion 35 is recessed upward Z1 compared to other portions, and the periphery of the upper recess 54 is recessed. The side surface in the direction serves as an oil receiving surface 54a. Preferably, oil receiving surfaces 54a are provided on both sides of the upper recess 54 in the circumferential direction C, but only on one side in the circumferential direction C, for example, the oil receiving surface 54a is provided in the direction in which the oil scraped up during forward rotation hits. Only one may be provided.

As shown in FIG. 4, in this embodiment, the case 50 is disposed on the first axial side X1 with respect to the carrier 30, and includes a side wall surface 55 facing the second axial side X2. An oil groove 57 is formed in this side wall surface 55 and communicates with a location 70 requiring lubrication. The oil groove 57 is open toward the second axial side X2. In this way, the oil scraped up by the scraping part 35 can be efficiently guided to the oil groove 57, and a large amount of oil can be easily supplied to the parts 70 requiring lubrication through the oil groove 57. In this embodiment, the oil receiving surface 54a and the oil groove 57 are connected to form an oil supply path Rt communicating with the location 70 requiring lubrication. Further, in this example, the oil groove 57 is formed in the shape of a concave groove that is recessed toward the first axial side X1 with respect to the side wall surface 55.

As shown in FIG. 5, in this embodiment, the drive transmission device 10 further includes an oil receiver 80. The oil receiver 80 is fixed to the carrier 30. Further, the oil receiving portion 80 is disposed on the inner side in the radial direction R than the scraping portion 35 and is formed to open toward the inner side in the radial direction R. Further, in this embodiment, the scraping part 35 is arranged between the ring gear 25 and the side wall surface 55 in the axial direction X, and the oil receiving part 80 is arranged between the carrier 30 and the side wall surface 55 in the axial direction X. It is located. The oil receiving portion 80 may be directly fixed to the carrier 30, or may be indirectly fixed to the carrier 30 with an integrally rotating member interposed therebetween. In this embodiment, the oil receiver 80 is fixed to the output shaft flange 16b that rotates integrally with the carrier 30. Furthermore, in this embodiment, the oil receiving portion 80 is formed continuously over the entire circumference. More specifically, the oil receiving portion 80 is formed in an annular shape, and as shown in FIGS. 4 and 5, the cross-sectional shape becomes axially first as it goes inward in the radial direction It has a shape that is inclined toward the side X1.

In this embodiment, the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R, and the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2. It further includes a protrusion 58 arranged to overlap the receiving part 80. In this embodiment, the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2. Here, regarding the arrangement of two members, "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, the virtual straight line is two Refers to the existence of an area that intersects both of the two members.

In the present embodiment, the protruding portion 58 includes a protruding outer circumferential surface 58a facing outward in the radial direction R, and a protruding end surface 58b, which is an end surface of the protruding portion 58 facing the second axial side X2. In the illustrated example, a portion of the second cylindrical portion 52 of the case 50 that is closer to the second axial side X2 than the side wall surface 55 is the protruding portion 58 . Further, an oil cutting groove 59 that opens toward the lower side Z2 is provided in a portion of the protruding outer circumferential surface 58a facing the lower side Z2 and adjacent to the first axial side X1 with respect to the protruding end surface 58b. .

Furthermore, in this embodiment, the carrier 30 is formed with an in-carrier oil passage 38 that communicates the oil receiver 80 and the pinion bearing 73. Therefore, the oil scraped up by the scraping part 35 flows toward the lower side Z2 along the side wall surface 55 or the oil groove 57 and reaches the protruding outer circumferential surface 58a. The oil that has reached the protruding outer circumferential surface 58a flows toward the lower side Z2 in the circumferential direction C along the protruding outer circumferential surface 58a, and also flows toward the lower side Z2 along the protruding end surface 58b. The oil falling from the protruding outer circumferential surface 58a or the protruding end surface 58b is received by the oil receiving portion 80. Note that the oil cutting grooves 59 provided on the protruding outer circumferential surface 58a prevent the oil that has reached the lower ends of the protruding outer circumferential surface 58a and the protruding end surface 58b from flowing toward the side wall surface 55 on the lower side Z2 than the protruding portion 58. fulfill the function of The oil received by the oil receiver 80 is guided to the carrier oil passage 38 by the shape of the oil receiver 80 and is supplied to the pinion bearing 73 through the carrier oil passage 38 .

In this embodiment, the carrier oil passage 38 includes a space 23a formed in the pinion shaft 23, an axial through hole 38a that communicates the space 23a with the oil receiver 80, and a space 23a and the pinion shaft. A radial through hole 38b that communicates with the outer circumferential surface of 23 in the radial direction R is provided. The oil discharged from the radial through hole 38b is supplied to the pinion bearing 73. The axial through hole 38a passes through the carrier body portion 31 and the output shaft flange portion 16b in the axial direction X.

In the present embodiment, the case 50 includes a first cylindrical portion 51 that supports the input bearing 71 from the outside in the radial direction R, and a second cylindrical portion that supports the output bearing 72 from the outside in the radial direction R. A shaped portion 52 is provided. A first communication oil passage 61 is formed in the first cylindrical portion 51 . The first communicating oil passage 61 communicates between a portion of the outer circumferential surface of the first cylindrical portion 51 facing upward Z1 and an inner circumferential surface that supports the input bearing 71 . Further, a second communication oil passage 62 is formed in the second cylindrical portion 52, which communicates between the portion of the outer circumferential surface of the second cylindrical portion 52 facing the upper side Z1 and the inner circumferential surface that supports the output bearing 72. There is.

In this way, a part of the oil that has been scraped up by the scraping part 35 and has reached the part of the outer circumferential surface of the first cylindrical part 51 facing the upper side Z1 enters the first communicating oil passage 61. The oil that has entered the first communication oil passage 61 then reaches the input bearing 71. Thereby, the input bearing 71 can be lubricated. Further, the scraped up part 35 reaches the part of the outer circumferential surface (i.e., the protruding outer circumferential surface 58a) of the second cylindrical part 52 facing the upper side Z1 along the side wall surface 55 or the oil groove 57 as described above. A portion of the oil enters the second communication oil passage 62. The oil that has entered the second communicating oil passage 62 then reaches the output bearing 72. Thereby, the output bearing 72 can be lubricated. Thereby, each bearing can be lubricated, for example, without providing oil passages inside the input shaft 15 and the output shaft 16. Note that the oil supply path Rt for the oil that reaches the first cylindrical portion 51 may be a path that runs along the inner surface of the case 50, or a path that passes through a through hole or an oil groove (not shown) in the case 50. Also good. Further, the oil scooped up by the parking gear 40 may reach the input bearing 71 via the first communication oil passage 61.

In the present embodiment, the first cylindrical portion 51 includes a third communication oil passage 63 that communicates between the portion of the outer circumferential surface of the first cylindrical portion 51 facing the lower side Z2 and the inner circumferential surface that supports the input bearing 71. is formed. Further, a fourth communication oil passage 64 is formed in the second cylindrical portion 52, which communicates the portion of the outer circumferential surface of the second cylindrical portion 52 facing the lower side Z2 with the inner circumferential surface that supports the output bearing 72. has been done. The first communication oil passage 61 and the third communication oil passage 63 are provided on the inner peripheral surface of the first cylindrical portion 51 so as to open on opposite sides in the axial direction X with the second input bearing 71b interposed therebetween. ing. Further, the second communication oil passage 62 and the fourth communication oil passage 64 are configured to open on opposite sides in the axial direction It is provided.

In this way, the oil supplied from the first communication oil passage 61 to lubricate the second input bearing 71b is sent to the lower side Z2 than the first cylindrical part 51 via the third communication oil passage 63. Can be discharged. Similarly, the oil supplied from the second communication oil passage 62 and after lubricating the first output bearing 72a is discharged to the lower side Z2 than the second cylindrical part 52 via the fourth communication oil passage 64. I can do it. Therefore, the oil after lubricating the second input bearing 71b and the first output bearing 72a can be appropriately discharged and circulated within the case 50. Note that the oil supplied from the first communicating oil passage 61 to lubricate the first input bearing 71a is discharged from the end of the first axially first side X1 of the first cylindrical portion 51. Similarly, the oil supplied from the second communicating oil passage 62 and lubricating the second output bearing 72b is discharged from the end of the second cylindrical portion 52 on the second axial side X2.

In this embodiment, an input side oil seal 81 is arranged between the inner circumferential surface of the first cylindrical portion 51 and the outer circumferential surface of the input shaft 15 to prevent oil from leaking out of the case 50. . Furthermore, an output side oil seal 82 is arranged between the inner circumferential surface of the second cylindrical portion 52 and the outer circumferential surface of the output shaft 16 to prevent oil from leaking out of the case 50.

In this embodiment, the scraping part 35 is arranged on one side of the ring gear 25 in the axial direction An oil supply path Rt is formed in the case 50 and flows the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication.

In the present embodiment, the opposing inner circumferential surface 53 is disposed above the rotation axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X. An oil receiving surface 54a is provided.

In this embodiment, the parts 70 requiring lubrication include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30, and the carrier 30 includes a carrier that communicates the oil receiver 80 with the pinion bearing 73. An inner oil passage 38 is formed.

In this embodiment, the oil groove 57 opens toward the second axial side It is formed in a gear shape and is oriented such that oil is blown toward the first side X1 in the axial direction by rotation of the scraping portion 35 while the vehicle 11 is moving forward.

[Second embodiment]
A drive transmission device 10 according to a second embodiment will be described below with reference to FIG. 6. In this embodiment, the drive transmission device 10 includes an oil pump 110, the third communicating oil passage 63 is not formed in the first cylindrical part 51, and the fourth communicating oil passage 63 is not formed in the second cylindrical part 52. This embodiment differs from the first embodiment in that a communicating oil passage 64 is not formed. Below, the explanation will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.

In the present embodiment, the drive transmission device 10 includes an oil pump 110 that sucks oil in the case 50 and supplies oil to the oil supply path Rt. The oil pump 110 is supported by a first case part 50a and a second case part 50b. It is preferable that the oil pump 110 supplies oil to the oil supply path Rt via an oil cooler (not shown). Further, a suction port (not shown) through which the oil pump 110 sucks oil in the case 50 is arranged at a lower side Z2 than the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state. is preferred.

In this embodiment, the parking pole 41 that rotates around the rotation axis Xc selectively engages with the parking gear 40. Furthermore, in this embodiment, the oil pump 110 is arranged so as to overlap the parking gear 40, the parking pole 41, or the parking gear 40 and the parking pole 41 when viewed in the radial direction R.

In this embodiment, the oil pump 110 is a mechanical oil pump that is driven as the input shaft 15 or the output shaft 16 rotates. Further, in this embodiment, the drive transmission device 10 includes a pump drive gear 111 that rotates integrally with the carrier 30 and drives the oil pump 110. In this example, the pump drive gear 111 is fixed to the carrier body 31 by welding or the like. Further, the pump drive gear 111 is disposed between the carrier body 31 and the parking gear 40 in the axial direction X.

In this embodiment, the oil pump 110 is configured to supply oil to the oil supply path Rt while the vehicle 11 is moving forward. Further, the scraping portion 35 is formed in the shape of an external helical gear formed on the outer peripheral surface of the flange portion 32 provided on the carrier 30, and is rotated by the rotation of the scraping portion 35 while the vehicle 11 is moving backward. It is formed in such a direction that the oil is blown toward the first side X1 in the axial direction. In this way, while the vehicle 11 is moving forward, the oil pump 110 can supply a large amount of oil to the oil supply path Rt, and even while the vehicle 11 is moving backward, the oil scraped up by the scooping part 35 can be removed from the oil groove 57. A large amount of oil can be supplied to the oil supply path Rt.

In this embodiment, the input shaft 15 is supported by a pair of input bearings 71 arranged on both sides of the sun gear 21 in the axial direction X. Further, the output shaft 16 is supported by a double-row output bearing 72. Further, the outer ring of the output bearing 72 is fixed to the case 50 by a locking member 78. The locking member 78 is disposed on the second axial side X2 of the output bearing 72 and holds the outer ring of the output bearing 72 between the wall surface of the case 50 on the first axial side X1 of the output bearing 72.

In this embodiment, the output shaft 16 and the carrier 30 are fixed by welding or the like so that they rotate together. In the illustrated example, the output shaft flange portion 16b and the flange portion 32 are fixed by welding or the like, and the flange portion 32 and the carrier body portion 31 are fixed by welding or the like. Further, the output shaft flange portion 16b supports the pinion shaft 23 and functions as a part of the carrier 30. In other words, a portion of the output shaft 16 functions as a portion of the carrier 30.

In the present embodiment, the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R. Further, a female thread is formed on the inner diameter side of the protrusion 58, and is screwed into a male thread formed on the outer peripheral surface of the cylindrical locking member 78. Further, an oil passage (a spline in the illustrated example) is formed on the inner circumferential side of the cylindrical locking member 78 to allow oil supplied to the output bearing 72 to flow into the oil receiver 80 . The oil received by the oil receiver 80 is supplied to the space 23a formed within the pinion shaft 23 due to the shape of the oil receiver 80.

In this embodiment, the pinion 22 is formed with a pinion through hole 38c that communicates the inner circumferential surface of the pinion 22 with the outer circumferential surface of the pinion 22 in the radial direction R. The oil supplied to the pinion bearing 73 is supplied to the meshing portion between the sun gear 21 and the pinion 22 through the pinion through hole 38c.

[Other embodiments]
Next, other embodiments of the drive transmission device 10 will be described.

(1) In the first and second embodiments, the drive transmission device 10 is mounted on a vehicle 11 equipped with a drive source 12 such as a rotating electrical machine. Here, the drive source 12 is not limited to a rotating electrical machine, but may be an internal combustion engine or a hybrid of an internal combustion engine and a rotating electrical machine. That is, the vehicle 11 may be a car that uses only an internal combustion engine as the drive source 12, a hybrid car that uses the internal combustion engine and a rotating electric machine as the drive source 12, an electric car, or the like. Moreover, this drive transmission device 10 may be mounted on a vehicle 11 other than an automobile. The drive transmission device 10 is also suitable for use in an in-wheel motor type drive device, as shown in FIG. 7, for example.

(2) In the first and second embodiments, the configuration in which the scraping portion 35 is formed in the shape of a gear with external teeth has been described as an example. However, without being limited to such a configuration, for example, the scraping part 35 may be formed such that unevenness in the axial direction It may be provided with both unevenness in the direction R and unevenness in the axial direction X, and the unevenness may be formed so as to be lined up in the circumferential direction C.

(3) In the first and second embodiments, the oil receiving portion 80 is continuously formed over the entire circumference. However, without being limited to such a configuration, for example, a configuration may be adopted in which the oil receiving portion 80 is provided only in the vicinity of the axial through hole 38a. Further, in the first and second embodiments, the oil receiver 80 is a separate member from the carrier 30 and is fixed to the carrier 30. However, the present invention is not limited to this. The oil receiving portion 80 may be formed integrally with the carrier 30. Furthermore, the drive transmission device 10 does not need to include the oil receiver 80. Furthermore, in the first and second embodiments described above, the lubrication-requiring parts 70 are described as including the input bearing 71, the output bearing 72, and the pinion bearing 73, but these are not included in the lubrication-requiring parts 70. You don't have to.

(4) In the first and second embodiments, the case 50 includes the opposing inner peripheral surface 53, the upper recess 54, the oil receiving surface 54a, the side wall surface 55, the oil groove 57, and the protrusion 58 as the oil supply path Rt. , a configuration in which the protruding outer circumferential surface 58a, the protruding end surface 58b, and the first to fourth communicating oil passages 61 to 64 are provided has been described as an example. However, the oil supply route Rt may be configured by only a part of these without being limited to such a configuration. Further, for example, the oil supply path Rt may be configured only by the inner surface of the case 50 without providing a groove or a through hole.

(5) In the first embodiment, the rotation of the scraping unit 35 while the vehicle 11 is moving forward, and in the second embodiment, the rotation of the scraping unit 35 while the vehicle 11 is moving backward, moves the oil in the axial direction. The explanation has been given by taking as an example a configuration in which the scraping portion 35 is formed in such a direction as to fly toward the first side X1. However, without being limited to such a configuration, for example, the rotation of the rake-up portion 35 while the vehicle 11 is moving backward in the first embodiment causes the rake-up portion 35 to rotate while the vehicle 11 is moving forward in the second embodiment. The scraping portion 35 may be formed in such a direction that the oil is blown toward the first side X1 in the axial direction by the rotation of the portion 35 .

(6) In the second embodiment, the drive transmission device 10 includes the oil pump 110, and the oil pump 110 is driven by the pump drive gear 111 while the vehicle 11 is moving forward. However, the present invention is not limited to such a configuration, and, for example, the drive transmission device 10 in the second embodiment may not include the oil pump 110. Further, for example, the drive transmission device 10 may include the oil pump 110 in the first embodiment. Further, for example, the oil pump 110 may be driven with the rotation of the input shaft 15 or the output shaft 16 via a chain, a belt, or the like instead of parallel gears. Further, for example, the oil pump 110 may be an electric oil pump. Further, for example, oil may be supplied to the oil supply path Rt by the oil pump 110 while the vehicle 11 is moving backward, or while the vehicle 11 is moving forward or backward. Further, for example, oil may be supplied to the oil supply path Rt by both the oil pump 110 and the scraping section 35 while the vehicle 11 is moving forward or backward.

(7) Note that the configuration disclosed in the embodiment described above can also be applied in combination with the configuration disclosed in other embodiments, unless a contradiction occurs. Regarding other configurations, the embodiments disclosed herein are merely illustrative in all respects. Therefore, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

[Summary of this embodiment]
The outline of the drive transmission device described above will be briefly explained below.

In one aspect, the input shaft (15) is drivingly connected to the drive source (12), the output shaft (16) is drivingly connected to the wheels (14), and the rotation of the input shaft (15) is decelerated and the output shaft is A drive transmission device (10) comprising a planetary gear mechanism (20) for deceleration that transmits data to the planetary gear mechanism (20), and a case (50) that accommodates the planetary gear mechanism (20). ) includes a sun gear (21) connected to rotate integrally with the input shaft (15), and a carrier supporting the pinion (22) and connected to rotate integrally with the output shaft (16). (30), and a ring gear (25) fixed to the case (50), and a scraping part (35) for scraping up oil in the case (50) is provided on the outer periphery of the carrier (30). The scraping part (35) is provided with a ring gear (25), with the direction along the rotation axis (Xc) of the carrier (30) being the axial direction (X), and the direction along the vertical direction being the vertical direction (Z). The lower end (Tf) of the rotation trajectory of the scraping part (35) is located below (Z2) than the lower end (Tp) of the revolution trajectory of the pinion (22). An oil supply path (Rt) is formed in the case (50) to flow the oil scraped up by the scraping portion (35) to the location requiring lubrication (70).

According to this configuration, even if the oil level is below the lower end of the pinion's orbit, the scraping section can scrape up the oil and supply oil to areas that require lubrication, so the pinion is not submerged in oil. By reducing the ratio, it is easy to suppress oil agitation by the pinion. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.

In one aspect, the scraping part (35) is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part (32) provided on the carrier (30), and is perpendicular to the rotation axis (Xc). The direction is defined as the radial direction (R), and the direction of rotation around the rotational axis (Xc) is defined as the circumferential direction (C). The opposing inner circumferential surfaces (53) are disposed above (Z1) than the rotation axis Xc, and the raking portion ( 35) is preferably provided with an oil receiving surface (54a) arranged to intersect with a tangent to the outer edge (Cf) in the rotation locus.

According to this configuration, the oil scraped up by the scraping part can be received above the rotational axis of the carrier, and from there, the oil can be flowed along the oil supply path to the locations requiring lubrication using gravity. Therefore, oil can be appropriately supplied to locations that require lubrication without using an oil pump or the like.

As one aspect, in the axial direction (X), the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side. (X2), and the direction perpendicular to the rotational axis (Xc) is defined as the radial direction (R). The case (50) is arranged on the first axial side (X1) with respect to the carrier (30) and on the second axial side (X1) with respect to the carrier (30). The scraping part (35) is arranged between the ring gear (25) and the side wall surface (55) in the axial direction X, and the oil receiving part (80) (30) and the side wall surface (55) in the axial direction X, and is fixed to the carrier (30). , a protrusion formed to protrude from the side wall surface (55) toward the second axial side (X2) and arranged to overlap with the oil receiver (80) when viewed in the radial direction (R). The lubrication required portion (70) includes a pinion bearing (73) that rotatably supports the pinion (22) relative to the carrier (30), and the carrier (30) includes a portion (58) that requires lubrication. Preferably, an in-carrier oil passage (38) is formed that communicates the oil receiver (80) and the pinion bearing (73).

According to this configuration, the oil scraped up by the scraping part flows from the side wall surface to the protruding part, and the oil that flows along the outer surface of the protruding part and then falls is received by the oil receiving part. Oil is then supplied to the pinion bearing from the oil receiver. Therefore, the oil scraped up by the scraping part can appropriately lubricate the pinion bearing that supports the pinion.

As one aspect, in the axial direction (X), the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side. (X2), the case (50) is disposed on the first axial side (X1) with respect to the carrier (30), and includes a side wall surface (55) facing the second axial side (X2). (55) is formed with an oil groove (57) that communicates with the lubrication required location (70), the oil groove (57) opens toward the second axial side (X2), and the raking portion (35) is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange portion (32) provided on the carrier (30), and is configured to rotate the scraping portion (35) while the vehicle (11) is moving forward. Accordingly, it is preferable that the oil is oriented such that the oil is blown toward the first side (X1) in the axial direction.

According to this configuration, a large amount of the scraped up oil can be supplied to the oil groove. Therefore, oil can be appropriately supplied from the oil groove to locations that require lubrication.

In one embodiment, the input shaft (71) and the output shaft (72) are arranged coaxially, and the input shaft (71) and the output shaft (72) are arranged side by side in the axial direction (X), The parts (70) that require lubrication include an input bearing (71) that rotatably supports the input shaft (71) with respect to the case (50), and an input bearing (71) that rotatably supports the output shaft (72) with respect to the case (50). The case (50) includes an output bearing (72) to support, and the direction perpendicular to the rotation axis (Xc) is defined as the radial direction (R), and the case (50) supports the input bearing (71) on the outside in the radial direction (R). A cylindrical first cylindrical part (51) that supports the output bearing (72) from the outside in the radial direction R is provided. The first cylindrical portion (51) has a first communicating oil that communicates between the portion of the outer peripheral surface of the first cylindrical portion (51) facing upward (Z1) and the inner peripheral surface that supports the input bearing (71). A channel (61) is formed. The second cylindrical portion (52) also has a second cylindrical portion that communicates between the portion of the outer circumferential surface of the second cylindrical portion (52) facing upward (Z1) and the inner circumferential surface that supports the output bearing (72). Preferably, a communicating oil passage (62) is formed.

According to this configuration, a portion of the oil that has been scraped up by the scraping portion and has reached the upwardly facing portion of the outer circumferential surface of the first cylindrical portion enters the first communication oil passage. The oil that has entered the first communication oil passage then reaches the input bearing. This allows the input bearing to be lubricated. In addition, some of the oil that has been scooped up by the scraping section and has reached the upwardly facing portion of the outer circumferential surface of the second cylindrical section along the side wall surface or oil groove as described above flows into the second communicating oil passage. enter. The oil that has entered the second communication oil passage then reaches the output bearing. This allows the output bearing to be lubricated. Thereby, each bearing can be lubricated, for example, without providing oil passages inside the input shaft and the output shaft.

10: Drive transmission device, 15: Input shaft, 16: Output shaft, 11: Vehicle, 12: Drive source, 14: Wheel, 20: Planetary gear mechanism, 21: Sun gear, 22: Pinion, 25: Ring gear, 30: Carrier , 32: flange part, 35: scraping part, 38: oil path in carrier, 50: case, 51: first cylindrical part, 52: second cylindrical part, 53: opposing inner peripheral surface, 54a: oil receiver surface, 55: side wall surface, 57: oil groove, 58: protrusion, 61: first communicating oil passage, 62: second communicating oil passage, 70: location requiring lubrication, 71: input bearing, 72: output bearing, 73 : pinion bearing, 80: oil receiving part, Xc: rotation axis of carrier, Rt: oil supply path, Tf: lower end of rotation trajectory of scraping part, Tp: lower end of pinion revolution trajectory

Claims

an input shaft drivingly connected to a driving source;
an output shaft drive-coupled to the wheels;
a planetary gear mechanism for decelerating the rotation of the input shaft and transmitting the rotation to the output shaft;
a case housing the planetary gear mechanism;
A vehicle drive transmission device comprising:
The planetary gear mechanism includes a sun gear connected to rotate integrally with the input shaft, a carrier supporting a pinion and connected to rotate integrally with the output shaft, and a carrier fixed to the case. a ring gear;
A scraping part for scraping up oil in the case is provided on the outer periphery of the carrier,
The direction along the rotational axis of the carrier is defined as the axial direction, and the direction along the vertical direction is defined as the vertical direction,
The scraping part is arranged on one side in the axial direction with respect to the ring gear,
The lower end of the rotation trajectory of the scraping part is arranged below the lower end of the revolution trajectory of the pinion,
A drive transmission device for a vehicle, wherein the case is formed with an oil supply path through which oil scraped up by the scraping portion flows to a location requiring lubrication.
The scraping part is formed in the shape of a gear of external teeth formed on the outer peripheral surface of a flange part provided on the carrier,
A direction perpendicular to the rotational axis is defined as a radial direction, and a direction around the rotational axis is defined as a circumferential direction,
The case includes an inner circumferential surface facing the scraping portion from the outside in the radial direction,
The opposing inner circumferential surface has an oil receiving surface that is arranged above the rotation axis and intersects with a tangent to the outer edge of the rotation locus of the scraping part when viewed in the axial direction along the axial direction. The vehicular drive transmission device according to claim 1.
In the axial direction, the side where the scraping part is arranged with respect to the ring gear is the first axial side, the opposite side is the second axial side, and the direction perpendicular to the rotational axis is the radial direction. As,
further comprising an oil receiver disposed inside the radial direction of the scraping part and formed to open toward the radial inside,
The case is disposed on the first axial side with respect to the carrier and includes a side wall surface facing the second axial side,
The scraping part is arranged between the ring gear and the side wall surface in the axial direction,
The oil receiver is disposed between the carrier and the side wall surface in the axial direction, and is fixed to the carrier,
The case is formed so as to protrude toward the second axial side from the side wall surface on the inner side of the oil receiver in the radial direction, and is configured to be in contact with the oil receiver when viewed in the radial direction along the radial direction. further comprising protrusions arranged in an overlapping manner;
The locations requiring lubrication include a pinion bearing that rotatably supports the pinion with respect to the carrier;
3. The vehicle drive transmission device according to claim 1, wherein the carrier has an in-carrier oil passage that communicates the oil receiver and the pinion bearing.
In the axial direction, the side on which the scraping part is arranged with respect to the ring gear is defined as a first axial side, and the opposite side is defined as a second axial side,
The case is disposed on the first axial side with respect to the carrier and includes a side wall surface facing the second axial side,
An oil groove communicating with the location requiring lubrication is formed on the side wall surface,
The oil groove opens toward the second axial side,
The scraping portion is formed in the shape of a helical gear with external teeth formed on the outer circumferential surface of a flange portion provided on the carrier, and the rotation of the scraping portion while the vehicle is moving moves the oil to the shaft. The vehicle drive transmission device according to any one of claims 1 to 3, wherein the vehicle drive transmission device is oriented so as to fly toward the first direction side.
The input shaft and the output shaft are arranged coaxially, and the input shaft and the output shaft are arranged side by side in the axial direction,
The locations requiring lubrication include an input bearing that rotatably supports the input shaft with respect to the case, and an output bearing that rotatably supports the output shaft with respect to the case,
The direction perpendicular to the rotational axis is defined as the radial direction,
The case includes a first cylindrical part that supports the input bearing from the outside in the radial direction, and a second cylindrical part that supports the output bearing from the outside in the radial direction. ,
A first communication oil passage is formed in the first cylindrical portion, which communicates an upwardly facing portion of the outer circumferential surface of the first cylindrical portion with an inner circumferential surface that supports the input bearing;
A second communicating oil passage is formed in the second cylindrical portion, which communicates an upwardly facing portion of the outer circumferential surface of the second cylindrical portion with an inner circumferential surface that supports the output bearing. 5. The vehicle drive transmission device according to any one of 1 to 4.