JP2013130213A - Power transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission mechanism capable of extracting power for a driven apparatus from a planetary gear mechanism while preventing the device from being lengthened in a rotational axis direction.SOLUTION: A ring gear 24B is non-rotatably provided, and an extension portion 32 connected, on one end side, to the ring gear 24B, and extending to one side in a rotational axis direction of a planetary gear type speed reducer 12B is provided. The extension portion 32 has a slit 33B penetrating an outer periphery and an inner periphery in at least a part thereof in a circumferential direction. A drive gear 45 is provided on a radially inner side of the extension portion 32 and on one side in the rotational axis direction with respect to an engagement portion between a planetary gear 22B and the ring gear 24B. At least a part of driven gear 42 is arranged inside the slit 33B in the extension portion 32. The planetary gear type speed reducer 12B is arranged on a power transmission path between a wheel RWr and an electric motor 2B of a vehicle 3.

Description

  The present invention relates to a power transmission mechanism including a drive source, a planetary gear mechanism connected to the drive source so as to be able to transmit power, and a driven device connected to the planetary gear mechanism so as to be able to transmit power.

  Patent Document 1 describes a drive device that is mounted on a vehicle and includes a planetary gear device. In this planetary gear device, an annular gear is fixed to the outer edge of the side plate of the carrier by welding, and the annular gear meshes with the input gear of the oil pump device, so that the oil pump is disposed radially outside the ring gear. The driving force to the device can be transmitted.

JP 2007-139061 A

  However, in the drive device described in Patent Document 1, the ring gear of the planetary gear device rotates on the outer side in the radial direction of the carrier and the inner side in the radial direction of the oil pump device, so that the annular gear fixed to the carrier and the input gear of the oil pump As a result, the meshing part cannot be overlapped with the ring gear in the direction of the rotation axis, and the entire apparatus has been elongated in the direction of the rotation axis.

  The present invention has been made in view of the above problems, and provides a power transmission mechanism capable of taking out the power of a driven device from a planetary gear mechanism while preventing the device from becoming longer in the rotational axis direction. There is.

In order to achieve the above object, the invention described in claim 1
A drive source (for example, an electric motor 2B of an embodiment described later);
A planetary gear mechanism (for example, a planetary gear type speed reducer 12B in an embodiment described later) connected to the drive source so as to be capable of transmitting power;
A driven device (for example, an oil pump 40 according to an embodiment described later) connected to the planetary gear mechanism so as to be capable of transmitting power;
With
The planetary gear mechanism is
A sun gear (for example, a sun gear 21B in an embodiment described later);
A plurality of planetary gears meshing with the sun gear (e.g., planetary gears 22B in an embodiment described later);
A planetary carrier that supports the planetary gear (for example, a planetary carrier 23B in an embodiment described later);
A ring gear meshing with the outer peripheral side of the planetary gear (for example, a ring gear 24B in an embodiment described later);
Have
On the power transmission path between the planetary gear mechanism and the driven device, a plurality of gears meshing with each other are disposed,
The plurality of gears are
A drive gear disposed relatively on the planetary gear mechanism side on the power transmission path;
A driven gear (for example, a driven gear 42 in an embodiment described later) that is disposed relatively to the driven device side on the power transmission path and meshes with the driving gear;
A power transmission mechanism (for example, a driving device 1 according to an embodiment described later),
The ring gear is disposed so as not to rotate,
One end side is connected to the ring gear, and an extending portion (for example, an extending portion 32 in an embodiment described later) extending to one side in the rotation axis direction of the planetary gear mechanism is disposed.
The extending portion has a penetrating portion (for example, a slit 33B in an embodiment described later) penetrating the outer peripheral surface and the inner peripheral surface in at least a part of the circumferential direction.
The drive gear is arranged on the radially inner side of the extending portion and on one side in the rotational axis direction with respect to the meshing portion of the planetary gear and the ring gear,
The driven gear is at least partially disposed in the penetrating portion of the extending portion,
The planetary gear mechanism is arranged on a power transmission path between a wheel (for example, a wheel RWr of an embodiment described later) of the vehicle (for example, a vehicle 3 of an embodiment described later) and the drive source. .

In addition to the structure of Claim 1, the invention of Claim 2 is
Another drive source (for example, an electric motor 2A in an embodiment described later);
Another planetary gear mechanism (for example, a planetary gear speed reducer 12A according to an embodiment described later) connected to the other drive source so as to be capable of transmitting power;
With
The other planetary gear mechanism is
Other sun gear (for example, the sun gear 21A in the embodiment described later),
A plurality of other planetary gears that mesh with the other sun gear (for example, planetary gears 22A in an embodiment described later);
Another planetary carrier that supports the other planetary gear (for example, a planetary carrier 23A in an embodiment described later);
Another ring gear meshing with the outer peripheral side of the other planetary gear (for example, a ring gear 24A in an embodiment described later);
Have
The other ring gear is connected to one side of the extending portion in the rotational axis direction,
The other planetary gear mechanism is arranged on a power transmission path between another wheel of the vehicle (for example, a wheel LWr in an embodiment described later) and the other drive source.

In addition to the structure of Claim 2, the invention of Claim 3 is
The extending portion is formed so as to be divisible in the direction of the rotation axis by a dividing line (for example, a dividing line P in an embodiment described later) extending in a direction intersecting the rotation axis.

In addition to the structure of Claim 3, the invention of Claim 4 is
The penetrating portion is formed including the dividing line.

In addition to the structure of any one of Claims 2-4, the invention of Claim 5 is
The driven device is arranged on the radially outer side of at least one of the planetary gear mechanism and the other planetary gear mechanism.

In addition to the structure of Claim 5, the invention of Claim 6 is
The driven device is arranged on a radially outer side of the other planetary gear mechanism.

In addition to the structure of any one of Claims 2-6, the invention of Claim 7 is
The planetary carrier and the other planetary carrier are arranged adjacent to each other, or the sun gear and the other sun gear are arranged adjacent to each other,
Between the adjacently arranged elements, at least a part of the drive gear and an axial restriction member that restricts movement of the adjacently arranged elements in the rotational axis direction (for example, an embodiment described later) The thrust bearing 35) is arranged.

In addition to the structure of Claim 7, the invention of Claim 8 is
The drive gear is formed in a hollow ring having a gap (for example, a gap 45S in an embodiment described later) in the center,
The outer diameter of the axial direction regulating member is formed smaller than the diameter of the gap of the drive gear,
The axial restriction member is disposed in the gap,
A part of the drive gear disposed between the adjacent elements (for example, a fixing portion 47 in the embodiment described later) has a maximum width in the rotational axis direction of the axial direction regulating member. It is characterized by being formed smaller than the maximum width in the rotation axis direction.

In addition to the structure of Claim 8, the invention of Claim 9 is
At least one element of the adjacently arranged elements has a protrusion (for example, 36A and 36B in the embodiments described later) protruding in the rotation axis direction,
The protrusion restricts the radial movement of the axial restriction member,
The gap in the rotation axis direction formed on the side of the protrusion in the rotation axis direction (for example, the gap 36S in the embodiment described later) is formed on the side of the drive gear in the rotation axis direction. It is characterized by being formed smaller than the gap in the rotation axis direction (for example, the gap 47S in the embodiment described later).

In addition to the structure of any one of Claims 1-9, the invention of Claim 10 is
The drive gear is connected to the planetary carrier.

In addition to the structure of Claim 10, the invention of Claim 11 is
The planetary carrier includes a rotation shaft of the planetary gear (for example, a rotation shaft 28B in an embodiment described later) and an arm portion (for example, an inner arm portion 29B in an embodiment described later) that supports the rotation shaft,
The drive gear for driving the driven device is fixed to the outer side in the radial direction of the arm portion.

In addition to the structure of Claim 10 or 11, the invention of Claim 12 is
The planetary carrier is connected to the wheels of the vehicle.

In addition to the structure described in any one of claims 1 to 12, the invention described in claim 13 includes:
The drive gear is formed integrally with the planetary gear mechanism.

In addition to the structure of Claim 13, the invention of Claim 14 is
The drive gear is formed separately from the planetary gear mechanism, and is fixed to the sun gear or the planetary carrier of the planetary gear mechanism,
The drive gear and the sun gear or the planetary carrier are arranged to overlap in the radial direction.

In addition to the structure of Claim 14, the invention of Claim 15 is
The drive gear and the sun gear or the planetary carrier are disposed so as to overlap in the rotation axis direction.

In addition to the structure of Claim 15, the invention of Claim 16 is
The drive gear includes a tooth portion (e.g., a tooth portion 46 in an embodiment described later) disposed radially outside the sun gear or the planetary carrier, and extends radially inward from the tooth portion, A fixed portion (for example, a fixed portion 47 of an embodiment described later) disposed on one side of the rotation axis direction of the sun gear or the planetary carrier,
The tooth portion is arranged to overlap the sun gear or the planetary carrier in the rotation axis direction,
The fixing part is arranged to overlap with the sun gear or the planetary carrier in a radial direction.

In addition to the structure of any one of Claims 2-9, the invention of Claim 17 is
The power transmission mechanism is housed in a housing (for example, a case 11 in an embodiment described later),
The ring gear and the other ring gear are formed separately from the casing, and are disposed on the inner periphery of the casing so as not to rotate relative to the casing.

In addition to the structure of any one of Claims 1-17, the invention of Claim 18 is
The rotation axis of the planetary gear mechanism, the rotation axis of the drive gear, and the rotation axis of the driven gear are arranged in parallel to each other.

In addition to the structure of any one of Claims 1-18, the invention of Claim 19 is
The driven device is an auxiliary device of a vehicle.

According to the first aspect of the present invention, the ring gear is disposed so as not to rotate, one end side thereof is connected to the ring gear, the extending portion extending to one side in the rotation axis direction of the planetary gear mechanism is disposed, and the extending portion is At least a part of the circumferential direction has a penetrating portion that penetrates the outer peripheral surface and the inner peripheral surface, and at least a part of the driven gear is disposed in the penetrating portion of the extending portion. Therefore, it is possible to extract the power of the driven device from the planetary gear mechanism while preventing the device from being elongated in the direction of the rotation axis.
In addition, since the ring gear is not rotatable, it is sufficient that the through portion in which at least a part of the driven gear is disposed is formed at least in a part of the extension portion in the circumferential direction, and the entire circumference of the extension portion is sufficient. It is not necessary to form over the entire area.
In addition, since the extending portion is disposed on one side in the rotational axis direction with respect to the meshing portion of the ring gear and the planetary gear, even if another member approaches from one side in the rotational axis direction, the extending portion causes the ring gear and the planetary gear to be connected. The meshing part can be protected.
In addition, the drive gear is disposed radially inward of the extension part and on one side in the rotation axis direction from the meshing part of the planetary gear and the ring gear, so that the drive gear that rotates is stationary on the ring gear and the extension part. Interference can be prevented.

  According to the second aspect of the present invention, since the two planetary gear mechanisms are disposed opposite to each other on both sides of the extending portion in the rotation axis direction, the movement of the two planetary gear mechanisms in the rotation axis direction is restricted. Therefore, it is possible to prevent an increase in the direction of the rotation axis.

  According to the third aspect of the present invention, since the extending portion is formed so as to be divided in the direction of the rotation axis by the dividing line extending in the direction intersecting the rotation axis, the rotation axis is improved while improving the assemblability and workability. An increase in the direction can be prevented.

  According to invention of Claim 4, since a penetration part is formed including a parting line, a penetration part can be easily formed in an extension part.

  According to the fifth aspect of the present invention, the driven device is disposed on the outer side in the radial direction of at least one of the planetary gear mechanism and the other planetary gear mechanism. Can do.

  According to the sixth aspect of the present invention, the driven device is disposed on the radially outer side of the other planetary gear mechanism, so that it is possible to prevent the driven device from becoming longer in the rotational axis direction.

  According to the seventh aspect of the present invention, the planetary carrier and the other planetary carrier are arranged adjacent to each other, or the sun gear and the other sun gear are arranged adjacent to each other, and between the elements arranged adjacent to each other. Are arranged with at least a part of the drive gear and an axial direction regulating member for regulating movement of the adjacently arranged elements in the rotational axis direction. Therefore, by making use of the space between adjacently arranged elements, it is possible to prevent an increase in the direction of the rotation axis.

According to the invention described in claim 8, the drive gear is formed in a hollow annular shape having a gap in the center, the outer diameter of the axial direction regulating member is smaller than the diameter of the gap in the drive gear, and the axial direction regulating member Is disposed in the gap. Therefore, it is possible to arrange the axial direction restricting member by utilizing the gap in the center of the drive gear, and it is possible to prevent an increase in the direction of the rotation axis.
Further, a part of the drive gear disposed between adjacent elements is formed such that the maximum width in the rotation axis direction is smaller than the maximum width in the rotation axis direction of the axial direction regulating member. Therefore, even when adjacent elements are close to each other in the rotation axis direction, the drive gear and other planetary gear mechanisms can be prevented from contacting each other.

  According to the ninth aspect of the present invention, at least one of the adjacently arranged elements has a protrusion protruding in the rotation axis direction, and the protrusion moves in the radial direction of the axial restriction member. The gap in the rotation axis direction formed on the side of the protrusion in the rotation axis direction is formed smaller than the gap in the rotation axis direction formed on the side of the drive gear in the rotation axis direction. Therefore, even when adjacent elements are close to each other in the rotation axis direction, the drive gear and other planetary gear mechanisms can be prevented from contacting each other.

  According to the invention described in claim 10, since the drive gear is connected to the planetary carrier having the maximum revolution radius inside the ring gear in the radial direction, the radial length thereof can be reduced.

  According to the eleventh aspect of the present invention, the planetary carrier includes the rotation shaft of the planetary gear and the arm portion that supports the rotation shaft, and the drive gear that drives the driven device is disposed radially outside the arm portion. Fixed. Therefore, it is possible to suppress the inclination of the rotation shaft of the planetary gear as compared with the case where the drive gear is disposed at a position away from the extension line of the arm portion.

  According to the twelfth aspect of the invention, since the planetary carrier is connected to the wheels of the vehicle, the driven device can be driven in accordance with the traveling state of the vehicle.

  According to the thirteenth aspect of the present invention, since the drive gear is formed integrally with the planetary gear mechanism, the meshing locations are reduced and the transmission efficiency can be improved.

  According to the fourteenth aspect of the present invention, the drive gear is formed separately from the planetary gear mechanism and is fixed to the sun gear or the planetary carrier of the planetary gear mechanism, and the drive gear and the sun gear or the planetary carrier have a diameter. It is arranged to overlap in the direction. Therefore, the drive gear is fixed to the sun gear or the planetary carrier in the direction of the rotation axis rather than in the radial direction, the contact area is increased, and the fixation of the drive gear is stabilized. In addition, since the drive gear can be strengthened against an external force from the rotation axis direction, it is possible to suppress the inclination of the tooth surface of the drive gear.

  According to the fifteenth aspect of the present invention, since the drive gear and the sun gear or the planetary carrier are disposed so as to overlap in the rotation axis direction, it is possible to prevent an increase in the length in the rotation axis direction. .

  According to the sixteenth aspect of the present invention, the drive gear includes a tooth portion disposed on the radially outer side of the sun gear or the planetary carrier, and extends radially inward from the tooth portion. A fixed portion disposed on one side in the rotational axis direction, the tooth portion is disposed so as to overlap the sun gear or the planetary carrier in the rotational axis direction, and the fixed portion overlaps the sun gear or the planetary carrier in the radial direction. Arranged. Therefore, the drive gear is formed so as to have a stepped structure in which the length in the rotation axis direction of the fixed portion is shorter than the length in the rotation axis direction of the tooth portion, so that the strength of the planetary gear mechanism that receives power from the drive source is increased. The driving gear can be fixed without dropping the gear.

  According to the invention described in claim 17, the power transmission mechanism is housed in the housing, the ring gear and the other ring gear are formed separately from the housing, and cannot be rotated relative to the housing on the inner periphery of the housing. Be placed. Therefore, the movement of the two ring gears in the direction of the rotation axis can be restricted and processing can be performed more easily.

  According to the eighteenth aspect, the rotation axis of the planetary gear mechanism, the rotation axis of the drive gear, and the rotation axis of the driven gear are arranged in parallel to each other. Therefore, the width in the rotation axis direction of the penetrating portion formed in the extending portion can be about the same as the tooth width of the driving gear and the driven gear, and the extension portion can be prevented from becoming longer in the rotating axis direction. It becomes possible.

  According to the nineteenth aspect of the present invention, since the driven device is an auxiliary device of the vehicle, a new power source for the driven device is not necessary, and the number of parts can be reduced.

1 is a block diagram illustrating a schematic configuration of a hybrid vehicle that is an embodiment of a vehicle on which a drive device according to an embodiment of the present invention can be mounted. It is a longitudinal cross-sectional view of the rear-wheel drive device which concerns on embodiment of this invention. FIG. 3 is an enlarged partial sectional view of an upper portion of the rear wheel drive device shown in FIG. 2. It is a perspective view which shows a ring gear and an extension part. It is sectional drawing which shows typically a mode that a drive gear is fixed to a planetary carrier.

A vehicle drive device as a power transmission mechanism according to the present invention uses an electric motor as a drive source for driving wheels, and is used in a vehicle having a drive system as shown in FIG. 1, for example. In the following description, the case where the vehicle drive device is used for rear wheel drive will be described as an example, but it may be used for front wheel drive.
A vehicle 3 shown in FIG. 1 is a hybrid vehicle having a drive device 6 (hereinafter referred to as a front wheel drive device) in which an internal combustion engine 4 and an electric motor 5 are connected in series at the front portion of the vehicle. While power is transmitted to the front wheels Wf via the transmission 7, the power of the drive device 1 (hereinafter referred to as a rear wheel drive device) as a power transmission mechanism provided at the rear of the vehicle separately from the front wheel drive device 6. Is transmitted to the rear wheels Wr (RWr, LWr). The rear wheel drive device 1 includes first and second electric motors 2A and 2B. The power of the first electric motor 2A is transmitted to the left rear wheel LWr, and the power of the second electric motor 2B is transmitted to the right rear wheel RWr. The electric motor 5 of the front wheel drive device 6 and the first and second electric motors 2A and 2B of the rear wheel drive device 1 are connected to the battery 9 so that power supply from the battery 9 and energy regeneration to the battery 9 are possible. Yes. In FIG. 1, reference numeral 8 denotes a control device for controlling the entire vehicle.

First, the power transmission mechanism of 1st Embodiment which concerns on this invention is demonstrated based on FIGS.
FIG. 2 is a longitudinal sectional view of the entire rear wheel drive device 1, and FIG. 3 is an enlarged partial sectional view of the upper part of FIG. In the figure, reference numeral 11 denotes a case (housing) for housing the rear wheel drive device 1, and the case 11 sandwiches the central case 11 </ b> M between the central case 11 </ b> M disposed at the substantially central portion in the vehicle width direction. The side cases 11A and 11B are arranged on the left and right sides of the central case 11M, and the whole is formed in a substantially cylindrical shape. Inside the case 11 are connected axles 10A and 10B for the rear wheels Wr, first and second electric motors 2A and 2B for driving the axles, and the electric motors 2A and 2B so as to be able to transmit power to decelerate the drive rotation. The first and second planetary gear type speed reducers 12A and 12B as planetary gear mechanisms are arranged on the same axis. The axle 10A, the first electric motor 2A and the first planetary gear speed reducer 12A drive and control the left rear wheel LWr, and the axle 10B, the second electric motor 2B and the second planetary gear speed reducer 12B drive the right rear wheel RWr. Control. The axle 10A, the first electric motor 2A and the first planetary gear type speed reducer 12A, and the axle 10B, the second electric motor 2B and the second planetary gear type speed reducer 12B are arranged symmetrically in the vehicle width direction in the case 11. ing.

  The side cases 11A and 11B are respectively provided with partition walls 18A and 18B extending radially inward on the central case 11M side. Between the side cases 11A and 11B and the partition walls 18A and 18B, first and first partitions are provided. Two electric motors 2A and 2B are arranged. Further, first and second planetary gear speed reducers 12A and 12B are arranged in a space surrounded by the central case 11M and the partition walls 18A and 18B. Moreover, the arrows in FIGS. 2 and 3 indicate the positional relationship when the rear wheel drive device 1 is mounted on the vehicle.

  The first and second electric motors 2A and 2B are induction motors that do not include a permanent magnet, and the stators 14A and 14B are fixed to the partition walls 18A and 18B, respectively. 15B is rotatably arranged. Cylindrical shafts 16A and 16B surrounding the outer periphery of the axles 10A and 10B are coupled to the inner peripheral portions of the rotors 15A and 15B, and the cylindrical shafts 16A and 16B can be relatively rotated coaxially with the axles 10A and 10B. The side cases 11A and 11B are supported by end walls 17A and 17B and partition walls 18A and 18B via bearings 19A and 19B.

  The first and second planetary gear speed reducers 12A and 12B include sun gears 21A and 21B, a plurality of planetary gears 22A and 22B that mesh with the sun gears 21A and 21B, and planetary carriers that support the planetary gears 22A and 22B. 23A and 23B, and ring gears 24A and 24B meshing with the outer peripheral sides of the planetary gears 22A and 22B. The driving forces of the electric motors 2A and 2B are input from the sun gears 21A and 21B, and the reduced driving force is supplied to the planetary carrier 23A It is output to the axles 10A and 10B through 23B.

  The sun gears 21A and 21B are formed integrally with the cylindrical shafts 16A and 16B. The planetary gears 22A and 22B are large-diameter first pinions 26A and 26B that directly mesh with the sun gears 21A and 21B, and smaller diameters than the first pinions 26A and 26B, and are second meshed with the ring gears 24A and 24B. The first and second pinions 26A and 26B and the second pinions 27A and 27B are integrally formed in a state of being coaxial and offset in the rotation axis direction.

  The planetary carriers 23A and 23B support the rotation shafts 28A and 28B of the planetary gears 22A and 22B and the inner ends of the rotation shafts 28A and 28B in the rotation axis direction, and extend radially inward to be able to rotate integrally with the axles 10A and 10B. The inner arm portions 29A and 29B that are spline-fitted to the outer periphery, and the outer end portions 38A and 18B that are supported by the partition walls 18A and 18B via the bearings 37A and 37B 38B.

  The two planetary carriers 23A and 23B are arranged adjacent to each other in the rotation axis direction, and the two planetary carriers 23A and 23B are disposed between the inner arm portions 29A and 29B of the two arranged planetary carriers 23A and 23B. A thrust bearing 35 is provided as an axial direction restricting member for restricting movement of the carriers 23A and 23B in the rotational axis direction. The thrust bearing 35 has a substantially annular shape, and is formed such that the width in the rotation axis direction is substantially equal to the width in the rotation axis direction between the inner arms 29A and 29B of the two planetary carriers 23A and 23B.

  Furthermore, the inner arm portions 29A and 29B of the two planetary carriers 23A and 23B disposed adjacent to each other are provided with projections 36A and 36B that protrude inward in the rotational axis direction on the radially outer side of the thrust bearing 35. . The protrusions 36A and 36B are opposed to each other in the rotational axis direction through a slight gap 36S, and restrict the movement of the thrust bearing 35 outward in the radial direction. Note that the protrusions 36A and 36B are not necessarily provided on the two planetary carriers 23A and 23B, and may be provided on at least one of the planetary carriers 23A and 23B.

  Referring also to FIG. 4, the ring gears 24 </ b> A and 24 </ b> B have a substantially annular shape, and the first and second annular rings are connected to the inner surfaces 30 </ b> A and 30 </ b> B in the rotation axis direction and are connected to one end side. Portions 31A and 31B are formed. The first and second annular portions rotate relative to each other on a dividing line extending in a direction intersecting the rotation axis, particularly in this embodiment, a dividing line P (see FIG. 3) extending in a direction perpendicular to the rotation axis. The extending portion 32 is configured to abut in the axial direction, and the two ring gears 24 </ b> A and 24 </ b> B are arranged to face each other via the extending portion 32. In the present embodiment, the first and second annular portions 31A and 31B are formed integrally with the ring gears 24A and 24B, respectively, but may be formed separately. Moreover, although the extension part 32 can be divided | segmented into the 1st, 2nd annular part 31A, 31B by the dividing line P, you may form these 1st, 2nd annular parts 31A, 31B integrally. .

  Further, the ring gears 24A and 24B protrude radially inward from the first and second annular portions 31A and 31B (extending portions 32) and mesh with the second pinions 27A and 27B of the planetary gears 22A and 22B. Further, the second annular portion 31B is provided with a slit 33B (penetrating portion) penetrating the vertical uppermost portion of the outer peripheral surface and the inner peripheral surface so as to include the dividing line P in a part of the circumferential direction. Yes. The slit 33B has a substantially arc shape extending in the circumferential direction, and the size thereof is set so that a driven gear 42 (described later) passing through the slit 33B can rotate. The ring gears 24A, 24B and the first and second annular portions 31A, 31B (extension portions 32) are spline fitted to the central case 11M so that the relative rotation with the central case 11M is impossible. The Further, the ring gears 24A and 24B are sandwiched from the outer side in the axial direction by substantially annular retaining rings 34A and 34B fixed to the inner peripheral surface of the central case 11M, and displacement in the axial direction is restricted. The fixing of the ring gears 24A and 24B and the first and second annular portions 31A and 31B to the central case 11M is not limited to fitting, and may be complete fixing. Further, for example, by providing a tooth profile on the inner wall of the central case 11M, the central case 11M, the ring gears 24A and 24B, and the first and second annular portions 31A and 31B may be provided integrally.

  A drive gear 45 as a drive gear for driving a mechanical oil pump 40 to be described later is fixed to the inner arm portion 29B of one planetary carrier 23B so as to be integrally rotatable on an extension line of the inner arm portion 29B. Yes. Therefore, the drive gear 45 is formed integrally with the planetary carrier 12B of the planetary gear type speed reducer 12B. The drive gear 45 is disposed on the radially outer side of the planetary carrier 23B, and has a tooth portion 46 having a gear portion that can mesh with a driven gear 42 described later on the radially outer edge, and a radially inner side from the inner side in the rotation axis direction of the tooth portion 46. And a fixing portion 47 disposed between the planetary carriers 23A and 23B disposed adjacent to each other. The drive gear 45 is a hollow ring having a gap 45S in the center, and has a stepped structure having a substantially L-shaped cross section in which the width in the rotation axis direction of the tooth portion 46 is larger than that of the fixed portion 47. The rotation axis of the planetary gear speed reducer 12B is parallel. In this embodiment, the drive gear 45 is formed separately from the planetary carrier 23 of the planetary gear type speed reducer 12B. However, for example, the drive gear 45 is integrally formed by forming a tooth profile on the outer periphery of the planetary carrier. Also good.

  The tooth portion 46 partially overlaps the planetary carrier 23B in the rotation axis direction, and is disposed on the inner side in the rotation axis direction than the meshing portion between the ring gear 24B and the second pinion 27B of the planetary gear 22B. It is located radially inward of the ring portions 31A and 31B (extending portions 32).

  The fixing portion 47 is disposed so as to overlap the inner arm portion 29B of the planetary carrier 23 in the radial direction, and is fixed to the inner side of the inner arm portion 29B in the rotation axis direction by a bolt (not shown). The inner diameter of the fixed portion 47, that is, the diameter of the gap 45S of the drive gear 45 is formed to be larger than the outer diameter of the thrust bearing 35 and the outer diameters of the protrusions 36A and 36B, and these thrust bearing 35 and protrusions 36A and 36B. Is disposed in the gap 45S. Further, the maximum width in the rotation axis direction of the fixed portion 47 is formed to be smaller than the maximum width in the rotation axis direction of the thrust bearing 35, and the two planetary carriers 23A and 23B arranged adjacent to each other are in the rotation axis line. Even when the direction approaches, the drive gear 45 and the planetary carrier 23A are prevented from coming into contact with each other.

  Further, a gap 47S in the rotation axis direction formed between the fixed portion 47 and the planetary carrier 23A on the side in the rotation axis direction is such that the projections 36A and 36B are located on the sides in the rotation axis direction of the projections 36A and 36B. Is formed so as to be larger than the gap 36S in the rotation axis direction formed between the two. Therefore, even when the two planetary carriers 23A and 23B arranged adjacent to each other approach each other in the rotation axis direction, the drive gear 45 and the planetary carrier 23A can be prevented from contacting each other.

  Further, a mechanical oil pump 40 as an auxiliary device of the vehicle 3 is disposed in the central case 11M on the radially outer side of the planetary gear speed reducer 12A, and its shaft 41 is connected to a part of the ring gear 24B. It extends in the rotation axis direction so as to overlap in the rotation axis direction. More specifically, a driven gear 42 as a driven gear is provided on the tip end side of the shaft 41 at a position overlapping the slit 33B of the second annular portion 31B of the shaft 41 in the rotation axis direction. The shaft 41 and the driven gear 42 are integrally rotatable. The rotational axis of the driven gear 42 is parallel to the rotational axis of the planetary gear type reduction gear 12 </ b> B and the rotational axis of the drive gear 45. In order to prevent an increase in the length of the rotation line axis, it is preferable to dispose the oil pump 40 on the outer side in the radial direction of at least one of the planetary gear type speed reducers 12A, 12B. More preferably, it is arranged outside the radial speed reducer 12A.

  The driven gear 42 is set such that the width in the rotation axis direction is slightly smaller than the width in the rotation axis direction of the slit 33B of the second annular portion 31B. It extends radially inward from the annular portion 31B (extending portion 32) and meshes with a drive gear 45 fixed to the planetary carrier 23B.

  As described above, a plurality of gears on the power transmission path between the planetary gear speed reducer 12B and the oil pump 40, that is, the planets relatively on the power transmission path between the planetary gear speed reducer 12B and the oil pump 40. A drive gear 45 disposed on the gear type speed reducer 12B side and a driven gear 42 disposed relatively on the oil pump 40 side on the power transmission path are disposed.

  In the rear wheel drive device 1 configured as described above, the driving forces input to the sun gears 21A and 21B from the electric motors 2A and 2B are fixed to the ring gears 24A and 24B, so that the planetary carriers 23A and 23B are used. Output to axles 10A and 10B to rotate wheels LWr and RWr.

  Here, the planetary carrier 23B is provided with a drive gear 45 that meshes with the driven gear 42 so as to be integrally rotatable, and the oil pump 40 and the planetary gear type speed reducer 12B are connected so as to be able to transmit power. The driving force is output to the oil pump 40 via the planetary gear speed reducer 12B. The driving force transmitted to the oil pump 40 increases as the rotational speed of the electric motor 2B, the wheel RWr, etc. increases, so that more oil can be supplied in situations where each part of the vehicle 3 requires cooling, such as at high vehicle speeds. It is possible to supply.

  In the vehicle 3 of the present invention, the control device 8 determines the vehicle state based on the input shift position, vehicle speed, accelerator pedal opening, and the like. As a result of the determination, in the low vehicle speed range, EV start and EV acceleration are performed by the rear wheel drive (RWD) by the rear wheel drive device 1. In a situation where acceleration is required, such as when the accelerator pedal is depressed deeply, four-wheel drive (AWD) is performed by the front wheel drive device 6 and the rear wheel drive device 1. Furthermore, when the vehicle speed increases and high engine speed traveling with high engine efficiency is achieved, ENG traveling is performed by front wheel driving (FWD) by the front wheel driving device 6. In particular, at such a high vehicle speed, the ring gears 24A and 24B are fixed, so that the electric motors 2A and 2B are also rotated at a high speed. However, since the electric motors 2A and 2B are induction motors that do not have permanent magnets, no back electromotive force is generated, and it is possible to prevent energy efficiency from deteriorating even during high rotation.

As described above, according to the drive device 1 of the present embodiment, the ring gear 24B is disposed so as not to rotate, one end side is connected to the ring gear 24B, and the extension extending inward in the rotation axis direction of the planetary gear type speed reducer 12B. The extending portion 32 is disposed, the extending portion 32 has a slit 33B penetrating the outer peripheral surface and the inner peripheral surface at least in a circumferential direction, and the driven gear 42 has at least a portion of the extending portion 32. It arrange | positions in the slit 33B. Therefore, it is possible to extract the power of the oil pump 40 from the planetary gear type speed reducer 12B while preventing the drive device 1 from being elongated in the direction of the rotation axis.
Further, since the ring gear 24B is not rotatable, it is sufficient that the slit 33B of the extending portion 32 through which the driven gear 42 penetrates is formed at least in a part of the extending portion 32 in the circumferential direction. It is not necessary to form over the entire area.
In addition, since the extending portion 32 is disposed on the inner side in the rotational axis direction with respect to the meshing portion of the ring gear 24B and the second pinion 27B of the planetary gear 22B, the extending portion is provided even if another member approaches from the inner side in the rotational axis direction. 32 can protect the meshing portion of the ring gear 24B and the second pinion 27B of the planetary gear 22B.
Further, since the drive gear 45 is disposed radially inward of the extending portion 32 and further inward in the rotational axis direction than the meshing portion of the ring gear 24B and the second pinion 27B of the planetary gear 22B, the drive gear 45 that rotates is stationary. Interference with the ring gear 24 </ b> B and the extending portion 32 can be prevented.

  Further, since the two planetary gear type speed reducers 12A and 12B are disposed opposite to each other on both sides of the extending portion 32 in the rotational axis direction, the two planetary gear type speed reducers 12A and 12B move in the rotational axis direction. Can be restricted, and further increase in the direction of the rotation axis can be prevented.

  Further, the extending portion 32 is formed so as to be divided into the first and second annular portions 31A and 31B in the rotation axis direction by the dividing line P extending in the direction intersecting the rotation axis, so that the assemblability and workability are improved. It is possible to prevent an increase in the direction of the rotation axis while improving.

  Moreover, since the slit 33B is formed including the dividing line P, the slit 33B can be easily formed in the extending portion 32.

  In addition, since the oil pump 40 is disposed on the radially outer side of at least one of the two planetary gear speed reducers 12A and 12B, it is possible to prevent the oil pump 40 from being elongated in the rotational axis direction.

  Further, since the oil pump 40 is disposed on the outer side in the radial direction of the planetary gear type speed reducer 12B, it is possible to prevent the oil pump 40 from becoming longer in the rotational axis direction.

  Further, the two planetary carriers 23A and 23B are arranged adjacent to each other, and between the two planetary carriers 23A and 23B arranged adjacent to each other, a fixed portion 47 of the drive gear 45 and 2 arranged adjacent to each other. A thrust bearing 35 that restricts movement of the planetary carriers 23A and 23B in the rotation axis direction is disposed. Therefore, by making use of the space between the two planetary carriers 23A and 23B arranged adjacent to each other, it is possible to prevent an increase in the direction of the rotation axis.

The drive gear 45 is formed in a hollow ring shape having a gap 45S in the center, the outer diameter of the thrust bearing 35 is smaller than the diameter of the gap 45S, and the thrust bearing 35 is disposed in the gap 45S. Therefore, it becomes possible to arrange the thrust bearing 35 using the gap 45S in the center of the drive gear 45, and it is possible to prevent an increase in the direction of the rotation axis.
Further, the fixed portion 47 of the drive gear 45 is formed such that the maximum width in the rotation axis direction is smaller than the maximum width of the thrust bearing 35 in the rotation axis direction. Therefore, even when the two planetary carriers 23A and 23B arranged adjacent to each other approach each other in the rotation axis direction, it is possible to prevent the drive gear 45 and the planetary gear type speed reducer 12A from contacting each other. .

  Further, at least one of the two planetary carriers 23A and 23B arranged adjacent to each other has protrusions 36A and 36B protruding inward in the rotation axis direction, and the protrusions 36A and 36B are arranged in the radial direction of the thrust bearing 35. The clearance 36S that restricts the movement and is formed on the side in the rotation axis direction of the protrusions 36A and 36B is more than the gap 45S in the rotation axis direction that is formed on the side in the rotation axis direction of the drive gear 45. Is also formed small. Therefore, even when the two planetary carriers 23A and 23B arranged adjacent to each other approach each other in the rotation axis direction, it is possible to prevent the drive gear 45 and the planetary gear type speed reducer 12A from contacting each other. .

  Further, since the drive gear 45 is connected to the planetary carrier 23B having the maximum revolution radius inside the ring gear 24B in the radial direction, the radial length thereof can be reduced.

  The planetary carrier 23B includes a rotation shaft 28B of the planetary gear 22B and an inner arm portion 29B that supports the rotation shaft 28B. A drive gear 45 that drives the oil pump 40 is disposed radially outside the inner arm portion 29B. Be placed. Therefore, it is possible to suppress the inclination of the rotation shaft 28B of the planetary gear 22B as compared with the case where the drive gear 45 is disposed at a position away from the extension line of the inner arm portion 29B.

  Further, since the planetary carrier 23B is connected to the wheel RWr of the vehicle 3, the oil pump 40 can be driven in accordance with the traveling state of the vehicle 3.

  Further, since the drive gear 45 is formed integrally with the planetary gear type speed reducer 12B, the meshing locations are reduced and the transmission efficiency can be improved.

  The drive gear 45 is formed separately from the planetary gear type speed reducer 12B, and is fixed to the planetary carrier 23B of the planetary gear type speed reducer 12B. The drive gear 45 and the planetary carrier 23B are overlaid in the radial direction. Wrapped and placed. Therefore, the drive gear 45 is fixed to the planetary carrier 23B not in the radial direction but in the rotation axis direction, and the contact area increases and the drive gear 45 is fixed stably. Further, since the drive gear 45 can be strengthened against an external force from the rotation axis direction, the inclination of the tooth surface of the drive gear 45 can be suppressed.

  In addition, since the drive gear 45 and the planetary carrier 23B are disposed so as to overlap in the rotation axis direction, it is possible to prevent the drive gear 45 and the planetary carrier 23B from being elongated in the rotation axis direction.

  Further, the drive gear 45 is provided with a tooth portion 46 disposed radially outward of the planetary carrier 23B, and extends radially inward from the tooth portion 46, and is disposed on one side of the planetary carrier 23B in the rotation axis direction. The tooth portion 46 is disposed so as to overlap with the planetary carrier 23B in the rotation axis direction, and the fixing portion 47 is disposed so as to overlap with the planetary carrier 23B in the radial direction. Accordingly, the drive gear 45 is formed to have a stepped structure in which the length in the rotation axis direction of the fixed portion 47 is shorter than the length in the rotation axis direction of the tooth portion 46, and therefore the planetary gear that receives the power from the electric motor 2B. The drive gear 45 can be fixed without reducing the strength of the speed reducer 12B.

  The drive device 1 is housed in the case 11, and the two ring gears 24 </ b> A and 24 </ b> B are formed separately from the case 11, and are disposed on the inner periphery of the case 11 so as not to rotate relative to the case 11. Therefore, the movement of the two ring gears 24A, 24B in the direction of the rotation axis can be restricted, and processing can be performed more easily.

  Further, the rotation axis of the planetary gear type reduction gear 12B, the rotation axis of the drive gear 45, and the rotation axis of the driven gear 42 are arranged in parallel to each other. Accordingly, the width in the rotation axis direction of the slit 33B formed in the extension portion 32 can be set to be about the tooth width of the drive gear 45 and the driven gear 42, and the extension portion 32 is prevented from being elongated in the rotation axis direction. It becomes possible.

  Further, since the oil pump 40 is an auxiliary machine for the vehicle 3, a new power source for the oil pump 40 is not required, and the number of parts can be reduced.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, in the above embodiment, the two planetary carriers 23A and 23B are arranged adjacent to each other, but the two sun gears 21A and 21B may be arranged adjacent to each other. In this case, between the adjacent sun gears 21A and 21B, at least a part of the drive gear 45, and a thrust bearing 35 that regulates movement of the adjacent sun gears 21A and 21B in the rotation axis direction; Is placed. Further, at least one of the sun gears 21 </ b> A and 21 </ b> B arranged adjacent to each other has a protrusion that protrudes in the rotation axis direction, and the protrusion restricts the radial movement of the thrust bearing 35.

  Further, the drive gear 45 is not necessarily limited to the configuration fixed to the planetary carrier 23B as long as the drive gear 45 is disposed on the radially inner side of the extending portion 32 and on the inner side in the rotational axis direction than the meshing portion of the planetary gear 22B and the ring gear 24B. Alternatively, the sun gear 21B may be fixed.

  Further, as long as the drive gear 45 is integrally formed with the planetary gear type speed reducer 12B, the position fixed to the planetary carrier 23B or the sun gear 21B is not limited. For example, the drive gear 45 is shown in FIGS. As shown, various fixing positions can be selected as appropriate.

  FIG. 5A shows a state in which the drive gear 45 having the tooth portion 46 and the fixing portion 47 is fixed to the planetary carrier 23B as described in the above embodiment.

  As another method for fixing the drive gear 45, as shown in FIGS. 5 (b) and 5 (c), a substantially annular drive gear 45 that is not a stepped structure is radially and rotated around the planetary carrier 23B. There is a method of fixing so as to overlap in the axial direction. Note that the outer diameter of the drive gear 45 is formed smaller than the outer diameter of the planetary carrier 23B in FIG. 5B, while it is formed larger than the outer diameter of the planetary carrier 23B in FIG. 5C. ing.

  As another method for fixing the drive gear 45, as shown in FIGS. 5D and 5E, the substantially annular drive gear 45 is not overlapped with the planetary carrier 23 in the direction of the rotation axis, and the diameter There is a method of fixing so as to overlap in the direction. In addition, the outer diameter of the drive gear 45 is formed larger than the outer diameter of the planetary carrier 23B in FIG. 5 (d), while it is formed smaller than the outer diameter of the planetary carrier 23B in FIG. 5 (e). Has been.

  Further, as another fixing method of the drive gear 45, there is a method of fixing the drive gear 45 formed in a substantially annular shape to the outer circumferential edge of the planetary carrier 23 as shown in FIG. 5 (f).

  The object to which the drive gear 45 in FIGS. 5A to 5E is fixed is not limited to the planetary carrier 23 but may be the sun gear 21B. However, when the drive gear 45 in FIGS. 5A and 5C is partially overlapped with the sun gear 21B in the rotational axis direction and the outer diameter is larger than the outer diameter of the sun gear 21B. The drive gear 45 is preferably fixed to the planetary carrier 23 because it is difficult, although not impossible to realize.

  In the present embodiment, the rotation axis of the planetary gear speed reducer 12B, the rotation axis of the drive gear 45, and the rotation axis of the driven gear 42 are arranged in parallel to each other. The axis may not be parallel to the rotation axis of the planetary gear speed reducer 12 </ b> B and the rotation axis of the drive gear 45. For example, the rotational axis of the driven gear 42 may be perpendicular to the rotational axis of the planetary gear speed reducer 12B and the rotational axis of the drive gear 45. In this case, the drive gear 45 and the driven gear 42 are helical gears. (Helical gear) or worm gear.

  Further, the power transmission from the planetary gear type reduction gear 12B to the oil pump 40 is not limited as long as it is performed by meshing a plurality of gears. For example, other gears are added to the drive gear 45 and the driven gear 42, Power transmission may be performed with three or more gears.

  It is not always necessary to provide two electric motors and planetary gear type speed reducers, and it is sufficient that at least the electric motor 2B and the planetary gear type speed reducer 12B capable of transmitting power to the oil pump 40 are provided.

Further, the output shafts of the electric motors 2A and 2B and the axles 10A and 10B do not need to be arranged coaxially.
Further, the front wheel drive device 6 may use the electric motor 5 as a sole drive source without using the internal combustion engine 4.
Further, the electric motors 2A and 2B may be permanent magnet motors.

  Further, the auxiliary device that transmits power from the planetary gear speed reducer 12B may be an auxiliary device other than the oil pump 40, for example, an air conditioner compressor or a water pump.

1 Drive unit (power transmission mechanism)
2A, 2B Electric motor (drive source)
3 Vehicle 4 Internal combustion engine 5 Electric motor 6 Drive device 7 Transmission 8 Control device 9 Battery 11 Case (housing)
11M Central case 11A, 11B Side case 12A, 12B Planetary gear type reduction gear (planetary gear mechanism)
14A, 14B Stator 15A, 15B Rotor 16A, 16B Cylindrical shaft 17A, 17B End wall 18A, 18B Bulkhead 21A, 21B Sun gear 22A, 22B Planetary gear 23A, 23B Planetary carrier 24A, 24B Ring gear 26A, 26B First pinion 27A, 27B First pinion 27A, 27B 2-pinion 28A, 28B Rotating shaft 29A, 29B Inner arm (arm)
30A, 30B Rotating axial direction inner side surfaces 31A, 31B Annular part 32 Extension part 33B Slit (penetrating part)
34A, 34B Retaining ring 35 Thrust bearing (Axial regulating member)
36A, 36B Protrusion 36S Gap 37A, 37B Bearing 38A, 38B Outer arm 40 Oil pump (driven device)
41 Shaft 42 Driven gear (driven gear)
45 Drive gear
45S Cavity 46 Tooth part 47 Fixed part 47S Gap P Dividing line Wf Front wheel Wr, RWr, LWr Rear wheel (wheel)

Claims (19)

A driving source;
A planetary gear mechanism connected to the drive source so that power can be transmitted;
A driven device connected to the planetary gear mechanism to transmit power;
With
The planetary gear mechanism is
With sun gear,
A plurality of planetary gears meshing with the sun gear;
A planetary carrier that supports the planetary gear;
A ring gear meshing with the outer peripheral side of the planetary gear;
Have
On the power transmission path between the planetary gear mechanism and the driven device, a plurality of gears meshing with each other are disposed,
The plurality of gears are
A drive gear disposed relatively on the planetary gear mechanism side on the power transmission path;
A driven gear that is relatively disposed on the driven device side on the power transmission path and meshes with the driving gear;
A power transmission mechanism having
The ring gear is disposed so as not to rotate,
One end side is connected to the ring gear, and an extending portion extending to one side in the rotation axis direction of the planetary gear mechanism is disposed,
The extending part has a penetrating part penetrating the outer peripheral surface and the inner peripheral surface in at least a part of the circumferential direction
The drive gear is arranged on the radially inner side of the extending portion and on one side in the rotational axis direction with respect to the meshing portion of the planetary gear and the ring gear,
The driven gear is at least partially disposed in the penetrating portion of the extending portion,
The planetary gear mechanism is disposed on a power transmission path between a vehicle wheel and the drive source. With other driving sources,
Another planetary gear mechanism connected to the other drive source so as to be capable of transmitting power;
With
The other planetary gear mechanism is
With other sun gear,
A plurality of other planetary gears meshing with the other sun gear;
Another planetary carrier that supports the other planetary gear;
Another ring gear meshing with the outer peripheral side of the other planetary gear;
Have
The other ring gear is connected to one side of the extending portion in the rotational axis direction,
The power transmission mechanism according to claim 1, wherein the other planetary gear mechanism is disposed on a power transmission path between another wheel of the vehicle and the other drive source.   3. The power transmission mechanism according to claim 2, wherein the extending portion is formed so as to be split in the rotation axis direction by a dividing line extending in a direction intersecting the rotation axis.   The power transmission mechanism according to claim 3, wherein the penetrating portion includes the parting line.   5. The power transmission mechanism according to claim 2, wherein the driven device is disposed on at least one radial outer side of the planetary gear mechanism and the other planetary gear mechanism. .   The power transmission mechanism according to claim 5, wherein the driven device is disposed radially outside the other planetary gear mechanism. The planetary carrier and the other planetary carrier are arranged adjacent to each other, or the sun gear and the other sun gear are arranged adjacent to each other,
Between the adjacently arranged elements, at least a part of the drive gear and an axial restriction member for restricting movement of the adjacently arranged elements in the rotational axis direction are arranged. The power transmission mechanism according to any one of claims 2 to 6. The drive gear is formed in a hollow ring having a gap in the center,
The outer diameter of the axial direction regulating member is formed smaller than the diameter of the gap of the drive gear,
The axial restriction member is disposed in the gap,
A part of the drive gear disposed between the adjacent elements is formed such that the maximum width in the rotation axis direction is smaller than the maximum width in the rotation axis direction of the axial direction regulating member. The power transmission mechanism according to claim 7. At least one of the adjacently arranged elements has a protrusion protruding in the rotational axis direction,
The protrusion restricts the radial movement of the axial restriction member,
The gap in the rotation axis direction formed on the side of the protrusion in the rotation axis direction is smaller than the gap in the rotation axis direction formed on the side of the drive gear in the rotation axis direction. The power transmission mechanism according to claim 8.   The power transmission mechanism according to claim 1, wherein the drive gear is connected to the planetary carrier. The planetary carrier includes a rotation shaft of the planetary gear, and an arm portion that supports the rotation shaft,
The power transmission mechanism according to claim 10, wherein the drive gear is fixed to the outer side in the radial direction of the arm portion.   The power transmission mechanism according to claim 10 or 11, wherein the planetary carrier is connected to the wheels of the vehicle.   The power transmission mechanism according to claim 1, wherein the drive gear is formed integrally with the planetary gear mechanism. The drive gear is formed separately from the planetary gear mechanism, and is fixed to the sun gear or the planetary carrier of the planetary gear mechanism,
The power transmission mechanism according to claim 13, wherein the drive gear and the sun gear or the planetary carrier are arranged to overlap in a radial direction.   The power transmission mechanism according to claim 14, wherein the drive gear and the sun gear or the planetary carrier are disposed so as to overlap in the rotation axis direction. The drive gear includes a tooth portion disposed radially outward of the sun gear or the planetary carrier, and extends radially inward from the tooth portion, and is one side in the rotational axis direction of the sun gear or the planetary carrier. A fixing portion disposed on the
The tooth portion is arranged to overlap the sun gear or the planetary carrier in the rotation axis direction,
The power transmission mechanism according to claim 15, wherein the fixing portion is arranged to overlap the sun gear or the planetary carrier in a radial direction. The power transmission mechanism is housed in a housing,
10. The ring gear according to claim 2, wherein the ring gear and the other ring gear are formed separately from the casing, and are disposed on the inner periphery of the casing so as not to rotate relative to the casing. The power transmission mechanism according to item 1.   The rotation axis of the planetary gear mechanism, the rotation axis of the driving gear, and the rotation axis of the driven gear are arranged in parallel to each other. The power transmission mechanism described in 1.   The power transmission mechanism according to claim 1, wherein the driven device is an auxiliary machine of a vehicle.

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