JP4275638B2 - Vehicle drive device - Google Patents

Description

  The present invention relates to a vehicle driving device that transmits a driving force of an electric motor to left and right axles of a vehicle via a differential device, and in particular, an electric motor for driving an axle and a power transmission mechanism including the differential device are coaxial with the axle. The present invention relates to a vehicle drive device.

  As a vehicle drive device, a device has been devised in which the left and right axles of a vehicle are connected to a differential device, and a driving force is transmitted to the differential device by an electric motor arranged coaxially on the outer periphery of one axle. (For example, refer to Patent Document 1).

In this drive device, an electric motor for driving an axle and a planetary gear type speed reducer that decelerates the drive rotation of the electric motor are arranged coaxially on the outer peripheral side of one axle, and the electric motor, the planetary gear type speed reducer, and a differential device are arranged. Housed in an integral housing. In a planetary gear type reduction gear, a sun gear is connected to a rotor of an electric motor disposed on the outer periphery of one axle, and a planetary gear is engaged with a ring gear fixed to the sun gear and a housing, and a planetary carrier is a differential of a differential gear. Connected to the case. Therefore, the driving force of the electric motor is decelerated to the set reduction ratio, is input to the differential device through the planetary carrier, and is output to the left and right axles of the vehicle via the differential device.
In this drive device, since the electric motor for driving the axle and the planetary gear type reduction gear are coaxially arranged on one axle, the entire device can be arranged compactly around the axle.
U.S. Pat. No. 4,418,777

However, in this conventional vehicle drive device, the rotor of the electric motor and the differential device are connected so as to always have a constant reduction ratio via the planetary gear type reduction gear, so that the axle rotates when the vehicle travels. Accordingly, the rotor of the electric motor always rotates. For example, in a situation where the rotational speed of the axle is faster than the driving range of the electric motor, the rotor is forcibly rotated by the rotation of the axle.
Under such circumstances, the rotor of the electric motor is forcibly rotated at a high speed, so that the loss of the electric motor increases and an originally undesired friction may act on the axle.

  Therefore, the present invention can arbitrarily control the power connection / disconnection between the electric motor and the axle without causing an increase in the size of the apparatus, and maintains a compact structure for preventing over-rotation of the electric motor and reducing axle friction. An object of the present invention is to provide a vehicle drive device that can be realized as it is.

In order to achieve the above object, the invention described in claim 1 includes an electric motor for driving an axle (for example, an electric motor 2 in an embodiment described later), and a planetary gear type speed reducer (for example, a speed reducing drive rotation of the electric motor). , A planetary gear reducer 12 in an embodiment described later, and a differential device (for example, an axle 10A, 10B in an embodiment described later) that distributes the output of the planetary gear reducer to the left and right axles of the vehicle (for example, A differential device 13) in a later-described embodiment, and the planetary gear type reduction gear and the motor are coaxially arranged on the outer peripheral side of one axle connected to the differential device. A sun gear (for example, a sun gear 21 in an embodiment described later) and a planetary carrier (for example, a planetary carrier 23 in an embodiment described later) of the planetary gear reducer are connected to the electric gear. And a ring gear of the planetary gear type reduction gear are connected to a rotor (for example, a rotor 15 in an embodiment to be described later) and a differential case (for example, a differential case 31 in an embodiment to be described later). Braking means (for example, a housing that is rotatably accommodated in a fixed housing (for example, a housing 11 in an embodiment described later), and applies a braking force to the ring gear by engaging the ring gear and the housing between the ring gear and the housing (for example, A hydraulic clutch 28 in an embodiment to be described later is provided, and this braking means is configured by a hydraulic clutch so that oil discharged from an oil pump (for example, an oil pump 40 in an embodiment to be described later) is supplied to an accumulator (for example, an after-mentioned Via the accumulator 42) in the embodiment The supply to the hydraulic clutch, and be arranged coaxially to and annularly the accumulator on the outer peripheral side of the one axle.

In the case of the present invention, when a braking force is applied to the ring gear by the braking means, the ring gear is fixed to the housing, and the driving force input to the sun gear from the rotor of the motor is reduced to the set reduction ratio by the planetary gear type reduction gear and differentially generated. Is transmitted to the differential case of the device. The driving force transmitted to the differential case is distributed to the left and right axles of the vehicle by a differential device. Further, when the application of the braking force from the braking means is cut off, the ring gear freely rotates with respect to the housing. Therefore, for example, when the braking force application by the braking means is interrupted in a situation where the rotational speed of the axle is faster than the drive request of the electric motor, the ring gear idles in the housing according to the excess rotation on the axle side, and the axle side Rotation is not input to the motor side.
Further, in this case, it is possible to install an accumulator having a sufficient volume without increasing the space projecting outward in the radial direction of the apparatus.

According to a second aspect of the present invention, in the first aspect of the present invention, the planetary gear of the planetary gear mechanism (for example, the planetary gear 22 in an embodiment described later) is engaged with a first gear (for example, a large diameter) that meshes with the sun gear. A small-diameter second gear (for example, a second gear 27 in the later-described embodiment) is integrally provided on an axial side portion of the first gear 26 in the later-described embodiment, and the outer periphery of the second gear. The ring gear is arranged on the side to engage both gears, and the braking means is arranged between the side portion of the ring gear and the housing.
In this case, since the ring gear is disposed on the outer peripheral side of the second gear having a small diameter of the planetary gear, the outer diameter can be reduced as compared with the case where the ring gear is disposed on the outer peripheral side of the first gear that is directly meshed with the sun gear. . Therefore, it is possible to dispose the braking means between the ring gear and the housing while keeping the outer diameter of the housing accommodating the ring gear small.

The invention according to claim 3 is the invention according to claim 1 or 2, wherein the oil pump is arranged annularly and coaxially on the outer peripheral side of the one axle.
In this case, it is possible to install an oil pump having a sufficient capacity without increasing the space projecting radially outward of the apparatus.

The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein an electric motor for driving the oil pump (for example, an electric motor 41 for driving a pump in an embodiment described later) is the one. It was made to arrange annularly and coaxially on the outer peripheral side of the axle.
In this case, an electric motor for driving the pump can be installed without increasing the projecting space outward in the radial direction of the apparatus.

The invention according to claim 5 is the invention according to any one of claims 1 to 4 , wherein the axle driving motor, the planetary gear type reduction gear, and the differential device are accommodated in a continuous common housing, The housing is provided with a continuous oil reservoir (for example, an oil reservoir 70 in an embodiment described later) straddling the lower regions of the electric motor, the planetary gear reducer, and the differential, and is stored in the oil reservoir. The oil is supplied to a hydraulic circuit for cooling the electric motor and / or operating an actuator (for example, a hydraulic circuit 39 in an embodiment described later).
In this case, a continuous oil reservoir is provided across each subregion of the motor, planetary gear reducer, and differential, so lubrication and actuator operation can be performed without providing a separate oil pan outside the housing. A sufficient amount of oil can be stored.

According to a sixth aspect of the present invention, in the fifth aspect of the present invention, the hydraulic circuit is formed integrally with a wall of the housing (for example, an end wall 17 in an embodiment described later).
In this case, since the hydraulic circuit is formed using the wall of the housing, it is not necessary to separately add a member for forming the hydraulic circuit, and the entire apparatus can be downsized accordingly.

According to this invention, it is possible to switch between fixing and free rotation of the ring gear by the braking means interposed between the ring gear and the housing, thereby controlling the power connection / disconnection between the electric motor and the axle. While maintaining this compact structure, it is possible to prevent excessive rotation of the electric motor and reduce axle friction. In addition, according to the present invention, since the accumulator is arranged annularly and coaxially on the outer peripheral side of one axle, a sufficient pressure accumulating capacity can be ensured without increasing the amount of protrusion of the device radially outward. Can do.

An embodiment of the present invention will be described below with reference to FIGS.
A drive device 1 according to the present invention uses an electric motor 2 as a drive source for driving an axle, and is used, for example, in a vehicle 3 having a drive system as shown in FIG.
A vehicle 3 shown in FIG. 2 is a hybrid vehicle having a drive unit 6 in which an internal combustion engine 4 and an electric motor 5 are connected in series. The power of the drive unit 6 is transmitted to the front wheel Wf side via a transmission 7. Thus, the power of the drive device 1 according to the present invention provided separately from the drive unit 6 is transmitted to the rear wheel Wr side. The electric motor 5 of the driving unit 6 and the electric motor 2 of the rear wheel Wr side driving device 1 are connected to the battery 9 via a PDU 8 (power drive unit), and supply power from the battery 9 and from each of the electric motors 5 and 2 to the battery 9. Energy regeneration is performed through the PDU 8.

  FIG. 1 is a longitudinal sectional view of the entire drive device 1. In FIG. 1, 10A and 10B are left and right axles on the rear wheel side of the vehicle. The housing 11 of the drive device 1 is provided so as to cover the outer peripheral side of one axle 10B from a substantially intermediate position between the two axles 10A and 10B, and is supported and fixed together with the axle 10B below the rear portion of the vehicle 3 (see FIG. 2). Yes. The housing 11 is generally formed in a substantially cylindrical shape, and includes an electric motor 2 for driving an axle, a planetary gear type speed reducer 12 that decelerates driving rotation of the electric motor 2, and an output of the speed reducer 12. Is arranged so as to be coaxial with the axle 10B.

  A stator 14 of the electric motor 2 is fixedly installed on the inner periphery of the end of the housing 11 on the wheel side (right side in FIG. 1), and an annular rotor 15 is rotatably accommodated and arranged on the inner peripheral side of the stator 14. . A cylindrical shaft 16 that surrounds the outer peripheral side of the axle 10B is coupled to the inner peripheral portion of the rotor 15 and is intermediate between one end wall 17 (wall) of the housing 11 so that the cylindrical shaft 16 is coaxial with the axle 10B. The wall 18 is supported via a bearing 19. A resolver 20 is provided between the outer circumference of one end of the cylindrical shaft 16 and the end wall 17 of the housing 11 to feed back the rotational position information of the rotor 15 to a control controller (not shown) of the electric motor 2. ing.

  The planetary gear type speed reducer 12 includes a sun gear 21, a plurality of planetary gears 22 meshed with the sun gear 21, a planetary carrier 23 that supports these planetary gears 22, and a ring gear 24 meshed with the outer peripheral side of the planetary gear 22. The driving force of the electric motor 2 is input from the sun gear 21, and the reduced driving force is output through the planetary carrier 23.

  The sun gear 21 is integrally formed on the outer periphery of a sleeve 25 coaxially disposed on the outer peripheral side of the axle 10B, and one end of the sleeve 25 is coupled to the cylindrical shaft 16 on the electric motor 2 side so as to be integrally rotatable. The planetary gear 22 includes a large-diameter first gear 26 that is directly meshed with the sun gear 21, and a second gear 27 that is smaller in diameter than the first gear 26. The first gear 26 and the second gear 27 Are integrally formed in a state of being coaxial and offset in the axial direction. The ring gear 24 is rotatably disposed at an axial side position of the first gear 26 in the housing 11, and an inner peripheral surface thereof meshes with a second gear 27 having a small diameter. In the case of this embodiment, the maximum radius of the ring gear 24 is set to be smaller than the maximum distance of the first gear 26 from the center of the axle 10B. The ring gear 24 is held so as to be integrally rotatable with a rotary drum 29 of a hydraulic clutch 28 described later, and is supported in the housing 11 via the rotary drum 29 so as to be rotatable.

  On the other hand, the differential 13 includes a differential case 31 having a rotatable pinion 30 projecting on the inner surface side, and a pair of side gears 32a and 32b meshed with the pinions 30 and 30 in the differential case 31. The side gears 32a and 32b are coupled to the left and right axles 10A and 10B, respectively. The aforementioned planetary carrier 23 of the planetary gear type speed reducer 12 is integrally extended on the outer surface of the differential case 31. In this embodiment, the planetary carrier 23 is integrally formed with the differential case 31. However, the planetary carrier 23 and the differential case 31 may be formed of separate parts, and both may be coupled by bolt coupling or the like. The differential case 31 is supported by the end wall 34 and the intermediate wall 18 on the vehicle body center side of the housing 11 via bearings 33.

  By the way, a cylindrical space is secured between the ring gear 24 and the end wall 34 in the housing 11, and the hydraulic clutch 28 that constitutes a braking means for the ring gear 24 is disposed in the space. . As shown in FIG. 3, the hydraulic clutch 28 includes a plurality of fixed plates 35 that are spline-fitted to the inner peripheral surface of the housing 11, and a plurality of rotary plates 36 that are spline-fitted to one outer peripheral surface of the rotary drum 29. Are alternately arranged in the axial direction, and these plates 35 and 36 are pressed and released by an annular piston 37. The piston 37 is accommodated in an annular cylinder chamber 38 formed on the end wall 34 of the housing 11 so as to be able to advance and retract. The piston 37 is advanced by introduction of high-pressure oil into the cylinder chamber 38, and the oil is discharged from the cylinder chamber 38. The piston 37 is moved backward by discharging the gas. The hydraulic clutch 28 is connected to a hydraulic circuit 39 shown in FIG. 5, and the hydraulic circuit 39 will be described in detail later.

In more detail, as shown in FIG. 3, the piston 37 has a first piston wall 63 and a second piston wall 64 in the axial direction, and the piston walls 63, 64 are cylindrical inner peripheral walls. 65 is connected. Therefore, an annular space that opens radially outward is formed between the first piston wall 63 and the second piston wall 64, and this annular space is a partition fixed to the inner peripheral surface of the outer wall of the cylinder chamber 38. The member 66 is partitioned forward and backward in the axial direction. A first working chamber 67 into which high-pressure oil is directly introduced is formed between the end wall 34 of the housing 11 and the second piston wall 64, and an inner peripheral wall 65 is formed between the partition member 66 and the first piston wall 63. The second working chamber 69 is connected to the first working chamber 67 through the through hole 68. The second piston wall 64 and the partition member 66 are electrically connected to the atmospheric pressure.
In the hydraulic clutch 28, high-pressure oil is introduced into the first working chamber 67 and the second working chamber 69, and the fixed plate 35 and the rotating plate 36 are moved by the oil pressure acting on the first piston wall 63 and the second piston wall 64. They are in pressure contact with each other. Therefore, since a large pressure receiving area can be gained by the first and second piston walls 63 and 64 in the front and rear in the axial direction, a large pressure contact force between the fixed plate 35 and the rotating plate 36 can be obtained while the radial area of the piston 37 is suppressed. Obtainable.

  In the case of this hydraulic clutch 28, the fixed plate 35 is locked to the housing 11, while the rotating plate 36 integrally supports the ring gear 24, so that both plates 35 and 36 are pressed against each other by the piston 37. When the braking force is applied to the ring gear 24 by the frictional engagement between the plates 35 and 36, and the pressure contact by the piston 37 is released from this state, the ring gear 24 is allowed to freely rotate.

  On the other hand, on the outside of the end wall 17 on the wheel side of the housing 11, as shown in FIGS. 1 and 4, an oil pump 40 for supplying oil to the hydraulic clutch 28 and a lubricating system in the housing 11, and this oil An electric motor 41 for driving the pump for driving the pump 40 and an accumulator 42 for storing oil in a pre-accumulated state supplied to the hydraulic clutch 28 are provided. These are integrated into a single block and accommodated in the cover 43, and are fixed to the end wall 17 together with the cover 43.

  As shown in an enlarged view in FIG. 4, the motor 41 uses a brushless motor having an annular rotor 44, and an annular stator 45 that is slightly larger than the rotor 44 is fixed to the outer surface of the end wall 17 via a bracket 46. In addition, a sleeve 47 fixed to the inner peripheral surface of the rotor 44 is supported by the end wall 17 and the bracket 46 via a bearing 48. In this state, the rotor 44 and the stator 45 are coaxially disposed on the outer peripheral side of the axle 10B.

  The oil pump 40 is a circumscribed gear pump, and a pair of gears 49 that perform a pumping action are arranged in parallel on the outer peripheral side of the electric motor 41. The rotation of the electric motor 41 is transmitted to one gear 49 of the oil pump 40 via a gear transmission mechanism 50.

  In the accumulator 42, an annular volume chamber 51 having a depth in the axial direction is formed integrally with the inner peripheral edge of the end of the cover 43. An annular piston 52 is accommodated in the volume chamber 51 so as to freely advance and retreat, and the piston 52 is urged by a pressure accumulation spring 53.

Here, the hydraulic circuit 39 of the drive device 1 shown in FIG. 5 will be described.
The hydraulic circuit 39 is configured to switch the oil discharged from the oil pump 40 to a lubrication side oil passage 57 and a clutch side oil passage 58 via an operation solenoid 55 and a switching valve 56. 57 communicates with an appropriate position in the housing 11 in order to supply oil to parts requiring lubrication, such as the electric motor 2, the speed reducer 12, and the differential device 13. The clutch-side oil passage 58 is provided with an on-off valve 59 for clutch operation, and a branch oil passage 60 that is connected to the accumulator 42 on the upstream side of the on-off valve 59 is provided. The accumulator 42 is provided to stabilize the pressure when the hydraulic clutch 28 is operated. In FIG. 5, 61 is a check valve for preventing the backflow of oil from the accumulator 42 to the switching valve 56, and 62 is a pressure for feeding back the pressure of the accumulator 42 to a controller (not shown). It is a sensor.

  In the case of this embodiment, the main part 39 </ b> A (see FIG. 5) of the hydraulic circuit 39 is formed integrally with the end wall 17 of the housing 11. Therefore, the entire drive device 1 can be downsized as compared with the case where a dedicated member for providing a separate circuit is added.

  Further, as shown in FIG. 1, an oil reservoir 70 is provided in the housing 11 so as to straddle the lower regions of the electric motor 2, the planetary gear type speed reducer 12, and the differential device 13. Further, in this embodiment, the interior of the housing 11 is divided in the axial direction by the intermediate wall 18, but through holes 71 and 72 are formed in the intermediate wall 18 so that oil and air can freely flow therethrough. Further, the through hole 71 is formed so that the stator 14 of the electric motor 2 is immersed in the oil and the oil is filled up to a position where it does not contact the rotor 15. Accordingly, since almost the entire area of the bottom of the housing 11 having a substantially circular cross section functions as an oil reservoir, sufficient oil can be stored without providing a separate oil pan.

  In this embodiment, lubricating oil supply portions a, b, and c are provided above the axle driving motor 2 in the housing 11 as shown in FIG. A cover member 73 having a plurality of dripping holes (not shown) is installed on the upper side of 14, and is devised so that the lubricating oil can be uniformly dripped onto the stator 14 through the plurality of dripping holes without concentrating on a certain location. ing.

  In the above configuration, when the axles 10A and 10B on the rear wheel Wr side are driven by the drive device 1, the oil pressure of the oil pump 40 is supplied to the hydraulic clutch 28 to turn on the clutch 28, and rotate with the fixed plate 35. The ring gear 24 is fixed to the housing 11 by frictionally engaging the plate 36. When the ring gear 24 is thus fixed, the reduction ratio of the planetary gear type reduction gear 12 is fixed, and the driving force is transmitted between the sun gear 21 and the planetary carrier 23 without loss. Accordingly, at this time, the driving force of the electric motor 2 is reduced to the set reduction ratio by the planetary gear type reduction gear 12 and transmitted to the left and right axles 10A and 10B through the differential device 13.

Further, when the drive device 1 is running, for example, when the rotational speed of the rear wheel Wr becomes higher than the required drive speed of the electric motor 2 on a downhill or the like, the oil in the hydraulic clutch 28 is Is turned off, thereby releasing the braking of the ring gear 24. When the rotation of the ring gear 24 becomes free in this way, the ring gear 24 idles in the housing 11 in accordance with the excessive rotation on the axles 10A and 10B, and as a result, the rotor 15 of the electric motor 2 rotates on the axles 10A and 10B side. It is no longer forced by force.
Therefore, in this drive device 1, it is possible to prevent the motor 2 from excessively rotating and to prevent the occurrence of axle friction without causing a significant increase in the volume of the device.

  In particular, in this drive device 1, the planetary gear 22 of the planetary gear type reduction gear 12 is coaxially connected to a large-diameter first gear 26 meshed with the sun gear 21 and a second gear 27 smaller in diameter than the first gear 26. Since the ring gear 24 is arranged on the outer peripheral side of the second gear 27 and the ring gear 24 is meshed with the second gear 27, the diameter of the gear portion of the planetary gear 22 meshed with the sun gear 21 is set. The outer diameter of the ring gear 24 can be made sufficiently small while keeping it large. For this reason, it is possible to keep the outer diameter of the casing 11 accommodating the ring gear 24 and the hydraulic clutch 28 small, and to reduce the protrusion of the driving device 1 in the radially outward direction. Therefore, when this drive device 1 is employed, the ground clearance around the axle 10B can be easily increased.

Further, in this drive device 1, since the accumulator 42 for accumulating the supply pressure of the hydraulic clutch 28 is disposed annularly and coaxially on the outer peripheral side of the axle 10B, the amount of protrusion of the device outward in the radial direction is increased. Therefore, a sufficient pressure accumulation capacity can be ensured. Further, in the case of this driving device 1, the pump driving motor 41 is also arranged annularly and coaxially on the outer peripheral side of the axle 10B, so that the outer side in the radial direction of the motor 41 while ensuring the necessary pump driving force. The overhang to can be kept sufficiently small.

  Next, another embodiment of the present invention shown in FIGS. 6 and 7 will be described. In addition, the same code | symbol is attached | subjected to the same part as said embodiment, and description shall be abbreviate | omitted about the overlapping part.

The drive device 101 of this embodiment has substantially the same basic configuration as that of the above embodiment, but the configuration and arrangement of the oil pump 140 are different from those of the above embodiment.
The oil pump 140 is constituted by a trochoid pump, and is provided along with the electric motor 41 for driving the pump along the axial direction on the outer peripheral side of the axle 10B. Specifically, in the oil pump 140, an outer rotor 81 and an inner rotor 82 whose centers o and o ′ are offset are rotatably accommodated in a plate-like casing 80 fixed in the cover 43. A continuous pumping action is performed by a change in the interproximal volume between the rotors 81 and 82 accompanying the rotation. The inner rotor 82 is fitted and fixed to the outer periphery of the sleeve 47, receives the driving force of the electric motor 41, and rotates on the outer peripheral side of the axle 10B. In FIG. 7, reference numerals 83 and 84 denote suction ports and discharge ports formed in the casing 80.

  This drive device 101 can basically obtain the same effects as those of the above embodiment, but adopts a trochoid pump as the oil pump 140 and is arranged side by side with the electric motor 41 for driving the pump. Therefore, the outer diameter of the device can be made smaller than that of the first embodiment. Even if the oil pump 140 is a pump other than the trochoid pump, it can be radially compact if it can be arranged annularly and coaxially on the outer peripheral side of the axle 10B. When the trochoid pump is employed as described above, the entire pump is easily thinned, and therefore the shaft length of the drive device 101 can be easily shortened.

In addition, this invention is not limited to the said embodiment, A various design change is possible in the range which does not deviate from the summary. For example, in the above embodiment, the drive device according to the present invention is employed on the rear wheel side, but it can also be employed on the front wheel side.
In the above-described embodiment, the multi-plate hydraulic clutch is used as the ring gear braking means, but a single-plate hydraulic clutch or an electromagnetic clutch may be used as the braking means.

1 is a longitudinal sectional view showing a drive device according to an embodiment of the present invention. The schematic block diagram which shows the layout of the vehicle to which the drive device of the embodiment is applied. Sectional drawing which expanded a part of FIG. 1 which shows the same embodiment. Sectional drawing which expanded another part of FIG. 1 which shows the same embodiment. Hydraulic circuit diagram showing the embodiment. Sectional drawing corresponding to FIG. 3 which shows other embodiment of this invention. The schematic side view of the oil pump which shows the embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,101 ... Drive device 2 ... Electric motor 10A, 10B ... Axle 11 ... Housing 11 ... Housing 12 ... Planetary gear reducer 13 ... Differential gear 15 ... Rotor 17 ... End wall (wall)
DESCRIPTION OF SYMBOLS 21 ... Sun gear 22 ... Planetary gear 23 ... Planetary carrier 24 ... Ring gear 26 ... First gear 27 ... Second gear 28 ... Friction clutch (braking means)
DESCRIPTION OF SYMBOLS 31 ... Differential case 39 ... Hydraulic circuit 40,140 ... Oil pump 41 ... Electric motor for a pump drive 42 ... Accumulator 70 ... Oil storage part

Claims (6)

An electric motor for driving the axle,
A planetary gear reducer that decelerates the drive rotation of the electric motor;
A differential device that distributes the output of the planetary gear reducer to the left and right axles of the vehicle,
In the vehicle drive device in which the planetary gear type reduction gear and the electric motor are coaxially arranged on the outer peripheral side of one axle connected to the differential device,
The sun gear and planetary carrier of the planetary gear reducer are connected to the rotor of the motor and the differential case of the differential, respectively.
The ring gear of the planetary gear type reduction gear is rotatably accommodated in a housing fixed to the vehicle body,
Between the ring gear and the housing, provided with a braking means for engaging the ring gear and the housing and applying a braking force to the ring gear ,
This braking means is constituted by a hydraulic clutch, and the oil discharged from the oil pump is supplied to the hydraulic clutch via an accumulator,
A driving apparatus for a vehicle, wherein the accumulator is arranged annularly and coaxially on an outer peripheral side of the one axle . The planetary gear of the planetary gear mechanism has a configuration in which a small-diameter second gear is integrally provided on an axial side portion of a large-diameter first gear meshed with a sun gear,
While arranging the ring gear on the outer peripheral side of the second gear and meshing both gears,
2. The vehicle drive device according to claim 1, wherein the braking means is disposed between a side portion of the ring gear and the housing. The vehicle drive device according to claim 1 or 2, wherein the oil pump is arranged annularly and coaxially on an outer peripheral side of the one axle. The vehicle drive device according to claim 1, wherein an electric motor for driving the oil pump is arranged annularly and coaxially on an outer peripheral side of the one axle. The axle drive motor, the planetary gear reducer and the differential are housed in a continuous common housing,
The housing is provided with a continuous oil reservoir across the lower regions of the electric motor, the planetary gear reducer and the differential,
The vehicle drive device according to any one of claims 1 to 4, wherein oil stored in the oil storage section is supplied to a hydraulic circuit for cooling the electric motor and / or operating an actuator. . 6. The vehicle drive device according to claim 5, wherein the hydraulic circuit is formed integrally with the wall of the housing.

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