JP2018044577A - Vehicle driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a cost of a planetary gear mechanism low in a vehicle driving device using a gear device which amplifies a torque difference and performs distribution by using a planetary gear mechanism.SOLUTION: A gear device 30 which distributes a torque to right and left races comprises planetary gear mechanism 30L, 30R having three elements and two degrees of freedom formed by combining two concentrically with right and left middle gears 13L, 13R, internal gears R, R, planetary carriers C, Cprovided concentrically with the internal gears R, R, sun gears S, Sprovided concentrically with the internal gear R, Rand a plurality of planetary gears P, Pare provided. A first binding member 31 which binds one side planetary carrier Cand the other side sun gear Sand a second binding member 32 which binds one side sun gear Sand the other side planetary carrier Care provided. The planetary gears P, Pare supported freely rotatably by a carrier pin 33 onto the planetary carriers C, Cand both ends of the carrier pin 33 are held between output side small diameter gears 13b of the middle gear shafts 13L, 13R and collars 40.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vehicle drive device capable of amplifying a torque difference and transmitting drive torque from two independent electric motors to left and right drive wheels.

  In vehicles such as electric vehicles, electric motors are arranged on the left and right drive wheels, respectively, and each electric motor is controlled independently to give an appropriate drive torque difference between the left and right drive wheels. It is known to control. For example, when each electric motor is independently connected to the left and right drive wheels via a speed reducer, the rotation speed of each electric motor is reduced by the speed reducer and the output torque of each electric motor ( The driving force is increased by each reduction gear and transmitted to the left and right drive wheels. Here, in order to make the vehicle turn right and turn left in the same manner, each electric motor has the same output characteristics, and each reduction gear has the same reduction ratio.

  The output torques of the left and right electric motors transmitted to the left and right drive wheels are increased according to the reduction ratio of the speed reducer. However, the ratio of the difference between the output torques of the left and right drive wheels is the same as the ratio of the difference between the output torques of the left and right electric motors because the reduction ratio of the left and right reduction gears is the same. The ratio of the torque difference is not increased.

  However, in order to achieve smooth turning of the vehicle and to suppress changes in vehicle behavior such as extreme understeer and extreme oversteer, the left and right drive is more than the ratio of the difference in output torque applied from the left and right electric motors. It may be effective to increase the ratio of the difference in output torque transmitted to the wheels.

  Patent Document 1 and Patent Document 2 include a gear device in which two three-element and two-degree-of-freedom planetary gear mechanisms are coaxially combined between two electric motors and left and right drive wheels. A vehicle drive device is disclosed that can amplify the difference between torques applied to the left and right driving wheels and amplify the difference. In the vehicle drive devices described in Patent Literature 1 and Patent Literature 2, it is possible to obtain a driving torque difference larger than the output torque difference given from the left and right electric motors.

  Moreover, in patent document 1 and patent document 2, it does not mention concretely about arrangement | positioning of the gear apparatus in a vehicle drive device. The applicant of the present application has already filed a patent application for a vehicle drive device in which the gear device for amplifying the torque difference is reduced in size and weight (Japanese Patent Application No. 2006-023529).

  The vehicle drive device (prior application example) for which the applicant of the present application has applied for a patent has the configuration shown in FIGS. 11 and 12.

  As shown in FIG. 11, the vehicle drive device 201 of the prior application example includes two electric motors 202L and 202R that are mounted on the vehicle and can be independently controlled, two electric motors 202L and 202R, and left and right drive wheels. A gear device 300 that is provided between the two electric motors 202L and 202R and distributes the torques of the two electric motors 202L and 202R to the left and right wheels, and speed reducers 203L and 203R that transmit the torques of the two electric motors 202L and 202R to the drive wheels. Yes. The reduction gears 203L and 203R are connected to electric motors 202L and 202R, input gear shafts 212L and 212R having an input gear 212a, output gear shafts 214L and 214R connected to driving wheels and having an output gear 214a, and an input And intermediate gear shafts 213L and 213R that transmit power between the gear shafts 212L and 212R and the output gear shafts 214L and 214R. The intermediate gear shafts 213L and 213R are provided with an input-side large-diameter gear 213a that meshes with the input gear 212a and an output-side small-diameter gear 213b that meshes with the output gear 214a.

  The two electric motors 202L and 202R are electric motors having the same output characteristics and are accommodated in the motor housings 204L and 204R.

  The input gear shafts 212L and 212R, the intermediate gear shafts 213L and 213R, and the output gear shafts 214L and 214R are offset from each other.

As shown in FIGS. 11 and 12, the gear device 300 that distributes torque from the two electric motors 202L and 202R to the left and right wheels is coaxial with a pair of left and right intermediate gear shafts 213L and 213R arranged coaxially. It consists of a planetary gear mechanism with three elements and two degrees of freedom in combination. As shown in the enlarged view of FIG. 12, the planetary gear mechanisms 300L and 300R constituting the gear device 300 include internal gears R _L and R _R respectively connected to the input-side large-diameter gear 213a of the intermediate gear shafts 213L and 213R. , internal gear R _L, R _R and the sun gear S _L provided coaxially, S _R and internal gear R _L, R _R and the sun gear S _L, a plurality of planetary gears P of the revolution gear meshing with S _{R L} , P _R , planetary carriers C _L , C _R provided coaxially with the internal gears R _L , R _R , one planet carrier C _L (the left side of the figure in FIG. 12), and the other sun gear S _R The first coupling member 231 that couples (the right side of the figure in FIG. 12), one sun gear S _L (the left side of the figure in FIG. 12) and the other planet carrier C _R (the right side of the figure in FIG. 12). a second coupling member 232 for coupling, internal gear R _L, linked to R _R, the input gear shaft 21 The intermediate gear shafts 213L and 213R that are in mesh with the input gear 212a of the L and 212R, the input side large-diameter gear 213a, and the output gear shafts 214L and 214R that are in mesh with the output gear 214a of the intermediate gear shafts 213L and 213R are the output-side small gear 213b. The intermediate gear shafts 213L and 213R have a configuration in which the output side small-diameter gear 213b is connected to the planetary carriers C _L and C _R.

Planet carrier C _L, C _R, as shown in FIG. 12, the planetary gears P _L, a carrier pin 233 which supports the P _R, the carrier flange on the outboard side which is connected to the outboard side end portion of the carrier pin 233 234a and an inboard carrier flange 234b connected to the inboard end.

  The carrier flange 234a on the outboard side includes a hollow shaft portion 235 extending toward the outboard side, and the end portion on the outboard side of the hollow shaft portion 235 is supported by the housing 209 via the rolling bearing 220b.

  The carrier flange 234b on the inboard side includes a hollow shaft portion 236 extending toward the inboard side, and the end portion on the inboard side of the hollow shaft portion 236 is supported by the housing 209 via the rolling bearing 220a.

11 and 12, the output side small diameter gear 213b is integrally formed on the outer peripheral surface of the hollow shaft portion 235 of the carrier flange 234a.
The planetary gears P _L and P _R are supported by carrier pins 233 via needle roller bearings 237.

Wherein each carrier flange 234a, the outer peripheral surface and the inner gear R _L of 234b, between the R _R, rolling bearings 239a, are arranged 239b.

  A collar 240 is disposed between the carrier flange 234b on the inboard side and the rolling bearing 220a that supports the hollow shaft portion 236 of the carrier flange 234b on the inboard side.

11 and in the prior application example shown in FIG. 12, the right end portion of the second coupling member 232 composed of a hollow shaft, the hollow shaft 236 and the spline of the carrier flange 234b of the inboard side of the planet carrier C _R They are connected by fitting.

As described above, the planetary gears P _L and P _R are rotatably held via the needle roller bearings 237 by the carrier pins 233 provided on the planet carriers C _L and C _R. The carrier pins 233 are fixed to the planetary carriers C _L and C _{R so} as not to rotate, and further, the movement of the carrier pins 233 needs to be restricted so as not to come off in the axial direction.

  In the above-mentioned prior application examples, the method for fixing the carrier pin is not disclosed. As a method for fixing the carrier pin to the planet carrier, the following method is generally known.

  A method of fixing the carrier pin by caulking both ends of the carrier pin to the planet carrier, a method of inserting and fixing the fixing pin from the radial direction of one end of the carrier pin and the planet carrier, and a method of attaching using a separate part such as a retaining ring. It is.

JP 2015-21594 A Japanese Patent No. 4907390

  In the above-described caulking method, there is a caulking process when assembling the gear device, so that a caulking machine is required, and the caulking process increases, which may increase the cost. Further, in the method using the fixing pins, it is necessary to make holes for the fixing pins in each of the planet carrier and the carrier pin, so that it is necessary to ensure the hole position accuracy, and the cost of the fixing pins is generated. In addition, there are various problems such as an increase in cost in parts dedicated to fixing the carrier pin, such as a retaining ring.

  By the way, the planetary gear mechanism is more complicated in configuration than the parallel shaft gear reducer, and therefore the production cost is high. In a vehicle drive device using a gear device that amplifies a torque difference using a planetary gear mechanism, it is desired to reduce costs as much as possible.

  An object of the present invention is to reduce the cost of a planetary gear mechanism constituting a gear device in a vehicle drive device using a gear device that amplifies and distributes a torque difference using a planetary gear mechanism.

  In order to solve the above problems, the present invention provides two electric motors mounted on a vehicle and independently controllable, two speed reducers disposed between the two electric motors, and the two speed reducers. And a gear device that distributes torque from two electric motors to the left and right wheels, wherein the speed reducer is connected to the electric motor and includes an input gear shaft that includes an input gear, and a drive An output gear shaft including an output gear coupled to a ring; and an intermediate gear shaft provided between the input gear shaft and the output gear shaft and including an input-side large-diameter gear and an output-side small-diameter gear; Is composed of a planetary gear mechanism having three elements and two degrees of freedom provided coaxially with the pair of left and right intermediate gear shafts. The planetary gear mechanism is coaxial with the internal gear and the internal gear. A planet carrier provided, and A first coupling member having a sun gear provided coaxially with the gear and a plurality of planetary gears as revolving gears, and coupling one planet carrier of the two planetary gear mechanisms and the other sun gear; A second coupling member that couples one sun gear and the other planet carrier, and an internal gear of the gear device is coupled to an input-side large-diameter gear of an intermediate gear shaft of the speed reducer, and the gear The planetary carrier of the planetary gear mechanism of the device is connected to the output side small-diameter gear of the intermediate gear shaft, and the planetary carrier extends to the inboard side with a carrier flange on the outboard side having a shaft portion extending to the outboard side. An inboard carrier flange having a shaft portion and a carrier pin inserted into a hole provided in each of the carrier flanges, and the end portion of the shaft portion of each carrier flange is An output side small gear of the intermediate gear shaft of the speed reducer is provided on the outer peripheral surface of the shaft portion of one carrier flange, and rotatably supported by the housing of the vehicle drive device via a rolling bearing. A collar is disposed between the rolling bearing that supports the end of the shaft portion of the shaft and the other carrier flange, and both ends of the carrier pin are sandwiched between the output-side small-diameter gear and the collar, and the axial direction of the carrier pin It is characterized by restricting movement.

  In addition, a notch is provided at the collar side end of the carrier pin, and when the carrier pin is attached to the carrier flange, the notch is disposed on the inner diameter side of the carrier flange, and the collar is notched. Abutting on the inner diameter side of the portion, the rotational movement of the carrier pin is restricted.

  Further, the output side small-diameter gear of the intermediate gear shaft is provided separately from the shaft portion of the carrier flange on the outboard side, and is provided on the shaft portion by spline fitting.

  Further, the output side small-diameter gear of the intermediate gear shaft may be provided separately from the shaft portion of the carrier flange on the inboard side and provided by spline fitting to the shaft portion.

  Further, the number of teeth of the output side small-diameter gear is set so that the tooth tip circle diameter of the output side small-diameter gear of the intermediate gear shaft overlaps with the hole into which the carrier pin of the planetary carrier is inserted as viewed from the axial direction. That's fine.

  The vehicle drive device of the present invention is incorporated in two electric motors mounted on a vehicle and independently controllable, two speed reducers arranged between the two electric motors, and the two speed reducers. A vehicle drive device comprising a gear device that distributes torque from two electric motors to the left and right wheels, wherein the speed reducer is connected to the electric motor, and is connected to an input gear shaft having an input gear, and to the drive wheels. A three-element two-degree-of-freedom planetary gear mechanism provided in combination with a pair of left and right output gear shafts having the output gear. The planetary gear mechanism includes an internal gear, a planet carrier provided coaxially with the internal gear, a sun gear provided coaxially with the internal gear, and a plurality of planetary gears as revolution gears. And said two A first coupling member that couples one planet carrier of the planetary gear mechanism to the other sun gear, and a second coupling member that couples one sun gear to the other planet carrier, The internal gear is connected to the output gear of the output gear shaft of the reduction gear, the planet carrier of the planetary gear mechanism of the gear device is connected to the output shaft portion of the output gear shaft, and the planet carrier is an outboard A carrier flange on the outboard side having a shaft portion extending to the side, a carrier flange on the inboard side having a shaft portion extending to the inboard side, and carrier pins inserted into holes respectively provided in the carrier flange. The end portions of the shaft portions of the respective carrier flanges are rotatably supported by the housing of the vehicle drive device via respective rolling bearings. Collars are respectively disposed between the rolling bearing that supports the end of the shaft portion of the lunge and the carrier flange, and both ends of the carrier pin are sandwiched between the two collars to restrict axial movement of the carrier pin. It is characterized by.

  An idler gear may be provided between the input gear and the output gear.

  Further, when the carrier pin is provided on at least one of the inboard side and the outboard side of the carrier pin, and the carrier pin is assembled to the planetary carrier, the collar on the notch side is attached to the carrier pin. The rotational movement of the carrier pin is restricted by contacting the inner diameter side of the notch.

  As described above, according to the present invention, in the gear device that amplifies and distributes the torque difference using the planetary gear mechanism, the carrier pin is moved in the axial direction by sandwiching both ends of the carrier pin with the constituent members of the gear device. Can be regulated.

  Further, when a notch is provided at one end of the carrier pin and the carrier pin is installed on the planetary carrier, the collar enters the inner diameter side of the notch of the carrier pin, so that the rotational movement of the carrier pin can be restricted.

  By using an output-side small gear or a collar as a component of the gear device that sandwiches the carrier pin, it is not necessary to manufacture a dedicated part for fixing the carrier pin, so that an increase in cost can be suppressed. Furthermore, since there is no caulking process or dedicated component assembling process, and only the assembling process of the gear device is required, an increase in assembling cost can be suppressed.

1 is a cross-sectional plan view showing an embodiment of a vehicle drive device according to the present invention. It is the cross-sectional top view which expanded a part of FIG. It is sectional drawing of the III-III line of FIG. It is a schematic diagram which shows the principal part of FIG. The carrier pin used for this invention is shown, (a) is a left view, (b) is a front view. It is explanatory drawing which shows an example of the electric vehicle of the rear-wheel drive system which mounts the vehicle drive device which concerns on this invention, and has shown the gear structure with the skeleton figure. It is a velocity diagram for demonstrating the torque difference amplification factor by the gear apparatus incorporated in the vehicle drive device which concerns on this invention. It is the cross-sectional top view to which the gear apparatus part which shows 2nd Embodiment of the vehicle drive device which concerns on this invention was expanded. It is a cross-sectional top view which shows 3rd Embodiment of the vehicle drive device which concerns on this invention. It is the cross-sectional top view which expanded a part of FIG. It is a cross-sectional top view which shows the vehicle drive device of a prior application example. It is the cross-sectional top view which expanded a part of FIG.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  As shown in FIG. 1, the two-motor type vehicle drive device 1 according to the present invention has a reduction gear housing 9 that accommodates two reduction gears 3 </ b> L and 3 </ b> R in parallel on the left and right sides. A structure is adopted in which the motor housings 4L and 4R of the two electric motors 2L and 2R are fixedly arranged on the outboard side of the vehicle.

  The electric vehicle AM according to the embodiment of the present invention shown in FIG. 6 is a rear wheel drive system, and includes a chassis 60, rear wheels 61L and 61R as drive wheels, front wheels 62L and 62R, and left and right rear wheels 61L and 61R. The two-motor type vehicle driving device 1 is mounted on the chassis 60 at the center position of the left and right rear wheels 61L and 61R. The driving force of the vehicle driving device 1 is as follows: It is transmitted to the left and right rear wheels 61L and 61R via the constant velocity joints 65a and 65b and the intermediate shaft 65c. In FIG. 6, the gear structure of the vehicle drive device 1 is shown in a skeleton diagram.

The torque (driving force) of the electric motors 2L, 2R is generated by the teeth of the input gear shafts 12L, 12R of the reduction gears 3L, 3R and the input-side large-diameter gear 13a composed of the external gears of the intermediate gear shafts 13L, 13R. It is increased by a number ratio and transmitted to the internal gears R _L and R _R of the gear device 30.

  Then, as shown in FIG. 6, the output-side small-diameter gear 13b composed of the external gears of the intermediate gear shafts 13L and 13R is engaged with the large-diameter output gear 14a of the output gear shafts 14L and 14R via the gear device 30 and output. The torque of the electric motors 2L, 2R is further increased by the gear ratio between the side small-diameter gear 13b and the output gear 14a, and is output to the drive wheels 61L, 61R.

  In the rear wheel drive system, the gear device 30 that amplifies the torque difference may be on the vehicle body front side or the rear side with respect to the output gear shafts 14L and 14R.

  As a mounting form of the two-motor type vehicle drive device 1, in addition to the rear wheel drive method shown in FIG. 6, either the front wheel drive method or the four wheel drive method may be used.

  1 and 6 includes two electric motors 2L and 2R that are mounted on a vehicle and can be controlled independently, left and right driving wheels 61L and 61R, and two electric motors 2L, 2R left and right reduction gears 3L, 3R provided between 2R.

As shown in FIG. 1, a speed reducer housing 9 that accommodates two speed reducers 3L and 3R provided in parallel on the left and right is a central housing 9a and left and right side housings 9bL fixed to both side surfaces of the central housing 9a. , 9bR three-piece structure.
The left and right electric motors 2L and 2R in the vehicle drive device 1 according to the present invention are accommodated in motor housings 4L and 4R as shown in FIG.

  The motor housings 4L and 4R include cylindrical motor housing bodies 4aL and 4aR, outer walls 4bL and 4bR that close the outer surfaces of the motor housing bodies 4aL and 4aR, and reduction gears on the inner surfaces of the motor housing bodies 4aL and 4aR. It consists of inner walls 4cL and 4cR separated from 3L and 3R. The inner walls 4cL and 4cR of the motor housing bodies 4aL and 4aR are provided with openings through which the motor shaft 5a is drawn.

  As shown in FIG. 1, the electric motors 2 </ b> L and 2 </ b> R are of a radial gap type in which a stator 6 is provided on the inner peripheral surface of the motor housing body 4 aL and 4 aR, and a rotor 5 is provided on the inner periphery of the stator 6. I am using something. The electric motors 2L and 2R may be axial gap types.

  The rotor 5 has a motor shaft 5a in the center, and the motor shaft 5a is drawn from the openings of the inner walls 4cL and 4cR of the motor housing main bodies 4aL and 4aR to the speed reducers 3L and 3R, respectively. A seal member 7 is provided between the openings of the inner side walls 4cL and 4cR of the motor housing bodies 4aL and 4aR and the motor shaft 5a.

  The motor shaft 5a is rotatably supported by the rolling bearings 8a and 8b on the inner walls 4cL and 4cR and the outer walls 4bL and 4bR of the motor housing main bodies 4aL and 4aR (FIG. 1).

  A reduction gear housing 9 that accommodates two reduction gears 3L and 3R provided in parallel on the left and right is divided into three pieces in a direction orthogonal to the gear shafts of the reduction gears 3L and 3R, as shown in FIG. The housing 9a has a three-piece structure including left and right side housings 9bL and 9bR fixed to both side surfaces of the central housing 9a. The left and right side housings 9bL and 9bR are fixed to the openings on both sides of the central housing 9a by a plurality of bolts (not shown).

  The side housings 9bL and 9bR of the speed reducer housing 9 are fixed to a side surface on the outboard side (outside the vehicle body) and the inner side walls 4cL and 4cR of the motor housing bodies 4aL and 4aR of the electric motors 2L and 2R by a plurality of bolts 10. Thus, the two electric motors 2L and 2R are fixedly arranged on the left and right sides of the reduction gear housing 9 (FIG. 1).

  A partition wall 11 is provided in the center of the center housing 9a. The speed reducer housing 9 is divided into left and right parts by the partition wall 11, and left and right accommodation chambers for accommodating the two speed reducers 3L and 3R are provided in parallel.

  As shown in FIG. 1, the speed reducers 3L and 3R are provided substantially symmetrically and mesh with the input gear shafts 12L and 12R having the input gear shaft 12a to which torque is transmitted from the motor shaft 5a. The intermediate gear shafts 13L and 13R having the output side small diameter gear 13b meshing with the input side large diameter gear 13a and the output gear 14a, and the output gear 14a, are pulled out from the speed reducer housing 9, and are constant velocity joints 65a and 65b. This is a parallel shaft gear reducer provided with output gear shafts 14L, 14R that transmit torque to drive wheels 61L, 61R via a shaft 65c (FIG. 6). The input gear shafts 12L and 12R, the intermediate gear shafts 13L and 13R, and the output gear shafts 14L and 14R of the left and right reduction gears 3L and 3R are coaxially arranged.

  Both ends of the input gear shafts 12L, 12R of the reduction gears 3L, 3R roll into bearing fitting holes 16a formed on both the left and right sides of the partition wall 11 of the central housing 9a and bearing fitting holes 16b formed in the side housings 9bL, 9bR. The bearings 17a and 17b are rotatably supported. The bearing fitting holes 16a and 16b have a stepped shape having a wall portion with which the outer rings of the rolling bearings 17a and 17b abut.

  The end portions on the outboard side of the input gear shafts 12L, 12R are drawn outward from the openings provided in the side housings 9bL, 9bR, and between the openings and the outer ends of the input gear shafts 12L, 12R. Is provided with an oil seal 18 to prevent leakage of the lubricating oil sealed in the reduction gear housing 9.

The input gear shafts 12L and 12R have a hollow structure, and end portions of the motor shaft 5a are inserted into the hollow input gear shafts 12L and 12R. The input gear shafts 12L, 12R and the motor shaft 5a are connected by splines (including the same for serrations).
At least one or more intermediate gear shafts 13L and 13R are arranged. In the embodiment shown in FIG. 1, the intermediate gear shafts 13L and 13R have a pair of intermediate gear shafts 13L and 13R.

  The intermediate gear shafts 13L and 13R constitute a stepped gear shaft having an input-side large-diameter gear 13a meshing with the input gear 12a and an output-side small-diameter gear 13b meshing with the output gear 14a on the outer peripheral surface. At both ends of the intermediate gear shafts 13L and 13R, rolling bearings 20a and 20b are fitted into bearing fitting holes 19a formed on both surfaces of the partition wall 11 of the central housing 9a and bearing fitting holes 19b formed on the side housings 9bL and 9bR. Is supported through. And the bearing fitting holes 19a and 19b have a stepped shape with a wall portion with which the outer rings of the rolling bearings 20a and 20b abut.

  The intermediate gear shafts 13L and 13R arranged on the same axis are connected to the intermediate gear shafts 13L and 13R so that the drive torque applied from the two electric motors 2L and 2R is a torque difference between the left and right drive wheels 61L and 61R. A gear device 30 for amplifying and distributing the signal is incorporated.

  In the embodiment of FIG. 1, the input gear 12a is integrally formed on the outer peripheral surfaces of the end portions of the input gear shafts 12L and 12R, but the input gear 12a is fitted to the input gear shafts 12L and 12R by a spline or the like. You may form in.

  The gear unit 30 includes three pairs of planetary gear mechanisms 30L and 30R having two degrees of freedom coaxially combined with a pair of left and right intermediate gear shafts 13L and 13R arranged coaxially.

As shown in the enlarged view of FIG. 2, the planetary gear mechanisms 30L and 30R constituting the gear device 30 include internal gears R _L and R _R respectively connected to the input side large diameter gear 13a of the intermediate gear shafts 13L and 13R. , internal gear R _L, R _R and the sun gear S _L provided coaxially, S _R and internal gear R _L, R _R and the sun gear S _L, a plurality of planetary gears P of the revolution gear meshing with S _{R L,} and P _R, the planetary gear P _L, is connected to the P _R, the internal gear R _L, R _R and planet carrier C _L provided coaxially, and C _R, the one planet carrier C _L (FIG. 2 The first coupling member 31 that couples the left side of the figure) and the other sun gear S _R (right side of the figure in FIG. 2), one sun gear S _L (left side of the figure in FIG. 2), and the other planet carrier C a second coupling member 32 for coupling the _R (right side in FIG. in FIG. 2), the internal gear R _L, it is connected to R _R, the input gear shaft 1 The input side large diameter gear 13a of the intermediate gear shafts 13L, 13R meshing with the input gear 12a of L, 12R, and the output side small diameter gear 13b of the intermediate gear shafts 13L, 13R meshing with the output gear 14a of the output gear shafts 14L, 14R. The output side small-diameter gear 13b of the intermediate gear shafts 13L and 13R is connected to the planetary carriers C _L and C _R.

Incidentally, in the case of providing the intermediate gear shaft 13L, the 13R plurality of pairs of gears R _L among which is connected to the input side the large diameter gear 13a, R _R, an intermediate gear shaft 13L pairs, of 13R, the input gear The output side small diameter gear 13b is meshed with a gear provided on the driven side intermediate gear shafts 13L and 13R of the plural pairs of intermediate gear shafts 13L and 13R. Are arranged as follows.

In the embodiment shown in FIGS. 1 and 2, the internal gear R _L, the input side is connected to R _R large diameter gear 13a is an internal gear R _L, and is formed integrally with the R _R. By arranging the input-side large-diameter gear 13a and the internal gears R _L and R _R at axial positions that overlap each other in the radial direction, it is possible to reduce the axial dimension compared to arranging them side by side in the axial direction. The input-side large-diameter gear 13a connected to the internal gears R _L and R _R may be formed separately.

Further, in the embodiment shown in FIGS. 1 and 2, the planet carrier C _L, C _R concatenated output side small diameter gear 13b is a planet carrier C _L, is formed on the C _R and another member, by spline fitting, The planetary carriers C _L and C _R are provided with an output side small diameter gear 13b. By connecting to the planetary carriers C _L and C _R by spline fitting, the output-side small-diameter gear 13 b can be arranged so as to contact the end of the carrier pin 33.

  Further, in the embodiment shown in FIG. 2, the output side small gear 13b and the output gear 14a of the output gear shafts 14L and 14R are provided on the outboard side (outside of the vehicle) of the vehicle drive device 1, but in FIG. As shown in the illustrated embodiment, it may be provided on the inboard side (inside the vehicle) of the vehicle drive device 1.

As shown in FIG. 2, the planetary carriers C _L and C _R are inserted into the outboard carrier flange 34a, the inboard carrier flange 34b, and the holes 35a provided in the carrier flanges 34a and 34b. And carrier pins 33 that support the gears P _L and P _R.

  The carrier flange 34a on the outboard side includes a hollow shaft portion 35 extending toward the outboard side, and the end portion on the outboard side of the hollow shaft portion 35 is formed on the side housings 9bL and 9bR of the reduction gear housing 9. The fitting hole 19b is supported via a rolling bearing 20b.

  The carrier flange 34b on the inboard side includes a hollow shaft portion 36 extending toward the inboard side, and an end portion on the inboard side of the hollow shaft portion 36 is formed in a bearing fitting hole formed in the partition wall 11 of the central housing 9a. 19a is supported via a rolling bearing 20a.

The planetary carriers C _L and C _R are supported by the housing 9 by the hollow shaft portion 35 of the carrier flange 34a on the outboard side and the hollow shaft portion 36 of the carrier flange 34b on the inboard side being supported by the rolling bearings 20a and 20b. Is done.

  In the embodiment shown in FIG. 1, the output side small diameter gear 13b is provided by spline fitting on the outer peripheral surface of the hollow shaft portion 35 of the carrier flange 34a.

The planetary gears P _L and P _R are supported by the carrier pin 33 via a needle roller bearing 37 as a rolling bearing. The carrier pin 33 is inserted into a hole 35a provided in each carrier flange 34a, 34b.

Further, each carrier flange 34a, 34b facing surface and a planetary gear P _L of, inserting the thrust plate 38 between the P _R, the planetary gear P _L, thereby achieving a smooth rotation of the P _R.
Wherein each carrier flange 34a, 34b outer peripheral surface and the inner gear R _L of the, between the R _R, the rolling bearing 39a, are arranged 39 b.

  A collar 40 is disposed between the carrier flange 34b on the inboard side and the rolling bearing 20a that supports the hollow shaft portion 36 of the carrier flange 34b on the inboard side. The collar 40 is in contact with the inner ring contact surface of the rolling bearing 20a.

In this embodiment, supporting the intermediate gear shaft 13L, the output-side small-diameter gear 13b of the 13R to the opposite ends disposed on the outboard side of the carrier pin 33, the planet carrier is disposed on the inboard side C _L, the C _R It is sandwiched between collars 40 arranged on the inner ring contact surface of the rolling bearing 20a. That is, both ends of the carrier pin 33 are sandwiched between the collar 40 installed between the inboard carrier flange 34b and the rolling bearing 20a and the output-side small gear 13b to restrict the movement of the carrier pin 33 in the axial direction. ing.

The diameter of the tip circle of the output side small gear 13b of the intermediate gear shafts 13L and 13R is such that the diameter overlaps with the hole 35a into which the carrier pin 33 is inserted into the planetary carriers C _L and C _R when viewed from the axial direction. The number of teeth of the output side small gear 13b is set. In this way, by setting the number of teeth of the output-side small-diameter gear 13b, the end of the carrier pin 33 comes into contact with the output-side small-diameter gear 13b, and the movement of the carrier pin 33 in the axial direction can be reliably restricted.

As shown in FIG. 5, a notch 33 a is provided at the end of the carrier pin 33 on the collar side. The end face of the notch 33a is formed so as to coincide with the end face of the carrier flange 34b. As shown in FIG. 2, the carrier pin 33 of this embodiment has a length that slightly protrudes toward the rolling bearing 20a. Then, when installing the carrier pin 33 the planet carrier C _L, the C _R, notches 33a planetary carrier C _L, the inner diameter side of the C _R, i.e., installed so as to face the inner diameter side of the carrier flange 34b. When the output-side small-diameter gear 13b is arranged on the outboard side (FIGS. 1 and 2), the carrier pin 33 is arranged so that the notch 33a of the carrier pin 33 is located on the inboard side. Then, as shown in FIGS. 3 and 4, the outer diameter of the collar 40 is inserted into the notch 33 a of the carrier pin 33. When the collar 40 enters the notch 33a of the carrier pin 33, the rotation of the carrier pin 33 is restricted.

  Since the cutout portion 33a provided on the carrier pin 33 only needs to be formed so that the outer diameter of the collar 40 can be inserted, it is necessary to provide the cutout portion, but it is not a process that requires accuracy, so the cost is low. The increase of can be suppressed.

As described above, in the gear device 30 that is a torque difference amplification mechanism, the movement of the carrier pin 33 in the axial direction can be restricted by sandwiching both ends of the carrier pin 33 between the output-side small-diameter gear 13b and the collar 40. Then, the cutout portion 33a provided at one end of the carrier pin 33, when installing the carrier pin 33 the planet carrier C _L, the C _R, that the collar 40 enters the inner diameter side of the cutout portion 33a of the carrier pin 33, The rotational movement of the carrier pin 33 can be restricted. By using the output-side small-diameter gear 13b or the collar 40 as a member for sandwiching the carrier pin 33, it is not necessary to manufacture a dedicated part for fixing the carrier pin, and thus an increase in cost can be suppressed. Furthermore, since there is no caulking process or dedicated component assembling process and only the assembling process of the gear unit 30 is required, an increase in assembling cost can be suppressed.

  The first coupling member 31 and the second coupling member 32 that couple the two planetary gear mechanisms 30L and 30R constituting the gear device 30 of the vehicle drive device 1 are partitions that partition the central housing 9a of the reduction gear housing 9 to the left and right. It penetrates through the wall 11 and is incorporated.

  The first coupling member 31 and the second coupling member 32 are arranged coaxially, and one coupling member (the second coupling member 32 in the embodiment of FIGS. 1 and 2) is a hollow shaft and the other coupling member. (In the embodiment of FIGS. 1 and 2, the first coupling member 31) has a double structure including a shaft inserted through the hollow shaft.

In the embodiment shown in FIGS. 1 and 2, the spline 41 on the right end portion of the second coupling member 32 constructed, and the hollow shaft portion 36 of the carrier flange 34b on the inboard side of the planet carrier C _R in the hollow shaft the provided a second coupling member 32 to the planet carrier C _R are coupled by spline-fitting.

Further, in the embodiment shown in FIGS. 1 and 2, the left end of the first coupling member 31, the spline 42 in the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _L provided, the first coupling member 31 to the planet carrier C _L are connected by spline fitting.

As described above, the two planetary gear mechanisms 30L, first coupling member 31 of the 30R and a second binding member 32, by connecting the splined to the planet carrier C _L and the planet carrier C _R, two The planetary gear mechanism can be divided into left and right, and can be incorporated into the three-piece reduction gear housing 9 together with other reduction gear shafts from the left and right.

End of the planet carrier C _L of the second coupling member 32 has, on its outer peripheral surface, the external gear meshing with the planetary gears P _L of the left planetary gear mechanism is formed, the sun the external gear of the left planetary gear mechanism A gear S _L is configured.

The first coupling member 31 inserted through the second coupling member 32 constituted by a hollow shaft has a large diameter portion 43 at an end portion on the right planetary gear mechanism 30R side, and an outer peripheral surface of the large diameter portion 43 is provided. , external gear meshing with the planetary gears P _R of the right planetary gear mechanism 30R is formed, the outer gear constitutes the sun gear S _R of the right planetary gear mechanism 30R.

Of the first coupling member 31 and second coupling member 32, the maximum diameter of the sun gear S _R are connected to the inner diameter side of the coupling member (first coupling member 31), the binding of the outer diameter side member (the second coupling by member 32) is set smaller than the minimum diameter of the spline hole of the inner surface of the hollow shaft portion 36 of the carrier flange 34b on the inboard side of the planet carrier C _R fit fitting, the inner diameter side of the coupling member (first coupling member 31 ) Can be easily incorporated.

  Between the outer peripheral surface of the inner diameter side coupling member (first coupling member 31) and the inner peripheral surface of the outer diameter side coupling member (second coupling member 32), there are needles 44 at both ends of the collar 44. The roller bearings 45 and 46 are interposed.

The first coupling member 31 and the second coupling member 32 and the planetary carriers C _L and C _R are fitted to the planetary carriers C _L and C _R (splines 41 and 42) by using a fitting tolerance slidable in the axial direction. Uneven load on the gear tooth surface due to the thrust force can be prevented.

Further, the axial movement of the first coupling member 31 and the second coupling member 32 and the planetary carriers C _L and C _R due to the sliding of the spline (splines 41 and 42) fitting portion is the outer diameter side coupling member (FIG. 1). In the embodiment of FIG. 2, the second coupling member 32) is regulated by providing thrust bearings 47 and 48 at both ends.

The coupling member (the first coupling member 31 in the embodiment of FIGS. 1 and 2) on the inner diameter side of the double-structure shaft that couples the two planetary gear mechanisms 30L and 30R is the coupling member (implementation of FIGS. 1 and 2). In the form, the shaft end opposite to the spline fitting between the first coupling member 31) and the planet carrier (C _{L in the} embodiment of FIGS. 1 and 2) is connected to the other planet carrier (the embodiment of FIGS. 1 and 2). In this case, C _R ) is supported by a deep groove ball bearing 49.

  The coupling member (the first coupling member 31 in the embodiment of FIGS. 1 and 2) on the inner diameter side of the double-structure shaft that couples the two planetary gear mechanisms 30L and 30R is provided with an oil supply hole 50 in the shaft center. Yes. The oil supply hole 50 of the inner diameter side coupling member (first coupling member 31 in the embodiment of FIGS. 1 and 2) has an outer diameter side coupling member (second coupling member 32 in the embodiment of FIGS. 1 and 2). Radial oil supply passages 51 and 52 are provided at the positions of the thrust bearings 47 and 48 at both ends.

  The output gear shafts 14L and 14R have a large-diameter output gear 14a, and are formed in bearing fitting holes 53a formed on both surfaces of the partition wall 11 of the central housing 9a and bearing fitting holes 53b formed on the side housings 9bL and 9bR. It is supported by rolling bearings 54a and 54b. The bearing fitting holes 53a and 53b have a stepped shape having a wall portion with which the outer rings of the rolling bearings 54a and 54b come into contact.

  As shown in FIG. 1, the end portions on the outboard side of the output gear shafts 14L and 14R are drawn out of the reduction gear housing 9 through openings formed in the side housings 9bL and 9bR, and the output gear shaft 14L drawn out is pulled out. The outer joint portion of the constant velocity joint 65a is splined to the outer peripheral surface of the end portion on the outboard side of 14R.

  The constant velocity joint 65a coupled to the output gear shafts 14L and 14R is connected to the drive wheels 61L and 61R via the intermediate shaft 65c and the constant velocity joint 65b (FIG. 6).

An oil seal 55 is provided between the end of the output gear shafts 14L, 14R on the outboard side and the openings formed in the side housings 9bL, 9bR, and leakage of the lubricating oil sealed in the reduction gear housing 9 and the outside Intrusion of muddy water from
The gear configuration of the two-motor vehicle drive device 1 of the embodiment shown in FIG. 1 is as shown in the skeleton diagram of FIG.

  As shown in FIG. 6, the left and right electric motors 2 </ b> L and 2 </ b> R are operated by electric power supplied from a battery 63 mounted on the vehicle via an inverter 64. The electric motors 2L and 2R are individually controlled by an electronic control device (not shown), and can generate and output different torques.

Torque from the electric motors 2L and 2R is transmitted from the input gear shafts 12L and 12R of the reduction gears 3L and 3R to the input side large gear 13a including the external gears of the intermediate gear shafts 13L and 13R, and the input gears. 12a and internal gear R _L of being increased by the gear ratio gear device 30 and the input-side large diameter gear 13a, is transmitted to the R _R.

  Then, the output side small diameter gear 13b of the intermediate gear shafts 13L and 13R is engaged with the large diameter output gear 14a of the output gear shafts 14L and 14R via the gear device 30, and the teeth of the output side small diameter gear 13b and the output gear 14a are engaged. The torque of the electric motors 2L, 2R is further increased by a number ratio and output to the drive wheels 61L, 61R.

As described above, the gear device 30 includes the first planetary gear mechanism 30L having the sun gear S _L , the planet carrier C _L , the planetary gear P _L, and the internal gear _RL , the sun gear S _R , and the planet carrier C _R. a second planetary gear mechanism 30R having a planetary gear P _R and the internal gear R _R is configured by combining coaxially.

Then, the planet carrier C _L of the first planetary gear mechanism 30L is binding and the sun gear S _R of the second planetary gear mechanism 30R to form a first coupling member 31, the sun gear S _L of the first planetary gear mechanism 30L When the planet carrier C _R of the second planetary gear mechanism 30R form a second coupling member 32 are coupled.

  The torque TM1 generated by the electric motor 2L is transmitted to the intermediate gear shaft 13L when the input gear 12a of the input gear shaft 12L and the input large-diameter gear 13a mesh with each other, and the torque transmitted to the intermediate gear shaft 13L is the first torque. It is transmitted to the output-side small gear 13b of the intermediate gear shaft 13L via the planetary gear mechanism 30L, and the output-side small gear 13b of the intermediate gear shaft 13L and the output gear 14a of the output gear shaft 14L mesh with each other from the output gear shaft 14L. A drive torque TL is output to the drive wheel 61L.

  The torque TM2 generated by the electric motor 2R is transmitted to the intermediate gear shaft 13R by meshing the input gear 12a of the input gear shaft 12R and the input large-diameter gear 13a, and the torque transmitted to the intermediate gear shaft 13R is transmitted to the second planetary shaft 13R. It is transmitted to the output-side small gear 13b of the intermediate gear shaft 13R via the gear mechanism 30R, and the output-side small gear 13b of the intermediate gear shaft 13R and the output gear 14a of the output gear shaft 14R are meshed to drive from the output gear shaft 14R. A driving torque TR is output to the wheel 61R.

Torques from the electric motors 2L and 2R are applied to the internal gears R _L and R _R of the two planetary gear mechanisms, and outputs from the first coupling member 31 and the second coupling member 32 are applied to the drive wheels 61L and 61R. Given. Two planetary gear mechanisms are coupled by the first coupling member 31 and the second coupling member 32.

By the way, the gear device 30 is configured by combining two identical single pinion planetary gear mechanisms 30L and 30R, and therefore can be represented by two velocity diagrams as shown in FIG. In the single pinion planetary gear mechanism, when the planetary carriers C _L and C _R are fixed, the sun gears S _L and S _R and the internal gears R _L and R _R rotate in opposite directions. , The internal gears R _L , R _R and the sun gears S _L , S _R are arranged on the opposite side to the planet carriers C _L , C _R.

Here, for easy understanding, the two speed diagrams are shifted up and down, the speed diagram of the left planetary gear mechanism 30L is shown on the upper side, and the speed diagram of the right planetary gear mechanism 30R is shown on the lower side. Originally, the torques TM1 and TM2 output from the electric motors 2L and 2R are respectively input to the internal gears R _L and R _R via the input large-diameter gears 13a that mesh with the input gears 12a of the input gear shafts 12L and 12R. The drive torque TL, TR extracted from the gear device 30 is transmitted to the left and right drive wheels 61L, 61R via the output side small-diameter gear 13b and the output gear 14a. In order to facilitate understanding, the speed ratio shown in FIG. 7 and the explanation of each calculation formula will be omitted, and the torque input to the internal gears R _L and R _R will be omitted. The driving torque remains TL and TR with TM1 and TM2.

Since the two planetary gear mechanisms 30L and 30R constituting the gear device 30 use gear elements having the same number of teeth, the distance between the internal gear R _L and the planet carrier C _L and the internal gear in the speed diagram. The distance between R _R and the planet carrier C _R is equal, and this is a. Further, the distance between the sun gear S _L and the planet carrier C _L and the distance between the sun gear S _R and the planet carrier C _R are also equal, which is b. The ratio of the length from the planet carrier C _L , C _R to the internal gear R _L , R _R and the length from the planet carrier C _L , C _R to the sun gear S _L , S _R is the ratio of the internal gear R _L , R _R It is equal to the ratio of the reciprocal number (1 / Zr) of the number of teeth Zr and the reciprocal number (1 / Zs) of the number of teeth Zs of the sun gears S _L and S _R. Therefore, a = (1 / Zr) and b = (1 / Zs).

The following equation (1) is calculated from the balance of moment M with reference to the point of R _R. In FIG. 7, the arrow direction is the positive direction of the moment M.

  a * TR + (a + b) * TL- (b + 2a) * TM1 = 0 (1)

The following equation (2) is calculated from the balance of moment M with reference to point R _L.

  -A.TL- (a + b) .TR + (b + 2a) .TM2 = 0 (2)

The following formula (3) is obtained from the formula (1) + formula (2).
-B. (TR-TL) + (2a + b). (TM2-TM1) = 0
(TR-TL) = ((2a + b) / b). (TM2-TM1) (3)

  (2a + b) / b in the equation (3) is the torque difference amplification factor α. When a = 1 / Zr and b = 1 / Zs are substituted, α = (Zr + 2Zs) / Zr, and the following torque difference amplification factor α is obtained.

  α = (Zr + 2Zs) / Zr

In the first embodiment of the present invention, the inputs from the electric motors 2L and 2R are the internal gears R _L and R _R , and the outputs to the drive wheels 61L and 61R are the sun gear S _R , the planetary carrier C _L , and the planetary carrier. _CR and sun gear S _L.

  Then, when different torques TM1 and TM2 are generated by the two electric motors 2L and 2R to give the input torque difference ΔTIN (= (TM2−TM1)), the input torque difference ΔTIN is amplified in the gear device 30, and the input torque difference A driving torque difference α · ΔTIN larger than ΔTIN can be obtained. That is, even if the input torque difference ΔTIN is small, the input torque difference ΔTIN can be amplified by the above-described torque difference amplification factor α (= (Zr + 2Zs) / Zr) in the gear device 30, and the left drive wheel 61L and the right drive wheel A driving torque difference ΔTOUT (= α · (TM2−TM1) = TR−TL) larger than the input torque difference ΔTIN can be given to the driving torques TL and TR transmitted to 61R.

In the first embodiment of the present invention, the connection between the two planetary gear mechanisms constituting the gear device 30 that is the torque difference distribution mechanism is the sun gear S _L and the planet carrier C _R , and the sun gear S _R and the planet carrier C _L. Therefore, a connecting member having a larger diameter than the internal gears R _L and R _R is not required. Therefore, the vehicle drive device 1 for an electric vehicle incorporating the torque difference distribution mechanism can be reduced in size and weight.

  Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 8 is an enlarged cross-sectional plan view of the gear device portion of the vehicle drive device 1 according to the second embodiment of the present invention. The embodiment shown in FIG. 8 is different from the embodiment shown in FIGS. 1 and 2 in that the output side small gear 13b provided on the intermediate gear shafts 13L and 13R and the output gear 14a of the output gear shafts 14L and 14R are replaced with a vehicle drive device. The embodiment shown in FIG. 8 is different from that of FIG. 1 only in that it is provided on the outboard side of 1 (outside of the vehicle) or on the inboard side of vehicle drive device 1 (inside of the vehicle). The same reference numerals as those in the embodiment shown in FIG.

  An output-side small-diameter gear 13b is provided by spline fitting on the outer peripheral surface of the hollow shaft portion 36 of the carrier flange 34b. The output-side small-diameter gear 13b is disposed between the rolling bearing 20a that supports the hollow shaft portion 36 of the carrier flange 34b on the inboard side and the carrier pin 33, and one end of the output-side small-diameter gear 13b and the carrier pin 33 are arranged. It abuts on one end.

The other end of the carrier pin 33 is the planetary gear P _L, contacts the collar 40 arranged planetary carrier of the opposite side of the P _R C _L, the inner ring contact surface of the rolling bearing 20b for supporting the C _R. In the second embodiment, the carrier pin 33 is sandwiched between the output side small-diameter gear 13b on the inboard side and the collar 40 arranged on the outboard side to restrict the movement of the carrier pin 33 in the axial direction.

In the second embodiment, similarly to the first embodiment, a cutout portion 33a (FIG. 5) is provided at the end of the carrier pin 33 on the collar side. When installed the carrier pin 33 the planet carrier C _L, the C _R, notches 33a planetary carrier C _L, the inner diameter side of the C _R, i.e., installed so as to face the inner diameter side of the carrier flange 34b. When the output side small-diameter gear 13b is arranged on the inboard side, the carrier pin 33 is arranged so that the notch 33a of the carrier pin 33 is located on the outboard side. Then, the outer diameter of the collar 40 is inserted into the notch 33 a of the carrier pin 33. When the collar 40 enters the notch 33a of the carrier pin 33, the rotation of the carrier pin 33 is restricted.

  Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 9 is a cross-sectional plan view of a vehicle drive device 1 according to a third embodiment of the present invention, and FIG. 10 is an enlarged cross-sectional plan view of a gear device portion of the vehicle drive device 1 according to a third embodiment of the present invention. The third embodiment shown in FIGS. 9 and 10 is different from the embodiment shown in FIGS. 1 and 2 in that the input gear 12a provided on the input gear shafts 12L and 12R and the output gear provided on the output gear shafts 14L and 14R. 14a is provided with an idler gear 70, and a gear device 30 is provided coaxially with the output gear shafts 14L and 14R. The embodiment shown in FIGS. 9 and 10 is the same as the embodiment shown in FIGS. By attaching the same reference numerals, redundant description is omitted.

  The vehicle drive device 1 shown in FIGS. 9 and 10 includes two electric motors 2L and 2R that are mounted on a vehicle and can be controlled independently, left and right drive wheels 61L and 61R, and two electric motors 2L, 2R left and right reduction gears 3L, 3R provided between 2R. An idler gear 70 is provided between the input gear 12a connected to the input gear shafts 12L and 12R of the electric motors 2L and 2R and the speed reducers 3L and 3R. As shown in FIG. 9, the idler gear 70 described above is based on the distance (L1) from the center of the motor shaft 5a of the electric motors 2L and 2R to the radial end of the stator 6 of the electric motors 2L and 2R. The diameter of the idler gear 70 is defined so that the distance (L2) from the center of the 2L, 2R motor shaft 5a to the gear device 30 is increased. And in order to shorten the dimension of the axial direction of the vehicle drive device 1, a part of gear apparatus 30 is made to overlap with the outer-diameter surface of electric motor 2L, 2R. Thus, by determining the diameter of the idler gear 70, the outer diameter surfaces of the electric motors 2L and 2R and the gear device 30 provided integrally with the speed reducers 3L and 3R do not overlap each other when viewed from the axial direction. Thus, a part of the gear device 30 can be overlapped with the outer diameter surfaces of the electric motors 2L and 2R, the useless space is compressed, and the axial dimension of the vehicle drive device 1 is reduced.

  The reduction gears 3L, 3R are provided substantially symmetrically, and input gear shafts 12L, 12R having an input gear 12a to which torque is transmitted from the motor shaft 5a, and an output gear meshing with the input gear 12a via an idler gear 70. An output gear having output gear shafts 14L and 14R having 14a, which is pulled out from the reducer housing 9 and transmits torque to the drive wheels 61L and 61R via the constant velocity joints 65a and 65b and the intermediate shaft 65c (FIG. 6). A parallel shaft gear reducer including shafts 14L and 14R.

  The idler gear 70 that meshes with the input gear 12a meshes with the output gear 14a provided on the output gear shafts 14L and 14R, and transmits the torque of the input gear 12a to the output gear 14a. Both ends of idler shafts 70L and 70R having an idler gear 70 are supported via rolling bearings 72a and 72b in bearing fitting holes 71b formed in the side housings 9bL and 9bR and bearing fitting holes 71a formed in the central housing 9a. ing. And the bearing fitting holes 71a and 71b have a stepped shape having a wall portion with which the outer rings of the rolling bearings 72a and 72b abut.

  The end portions on the outboard side of the input gear shafts 12L, 12R are drawn outward from the openings provided in the side housings 9bL, 9bR, and between the openings and the outer ends of the input gear shafts 12L, 12R. Is provided with an oil seal 18 to prevent leakage of the lubricating oil sealed in the reduction gear housing 9.

  The output gear shafts 14L and 14R have a large-diameter output gear 14a, and are formed in bearing fitting holes 53a formed on both surfaces of the partition wall 11 of the central housing 9a and bearing fitting holes 53b formed on the side housings 9bL and 9bR. It is supported by rolling bearings 54a and 54b. The bearing fitting holes 53a and 53b have a stepped shape having a wall portion with which the outer rings of the rolling bearings 54a and 54b come into contact.

  Outboard side ends of the output gear shafts 14L and 14R are drawn out of the reduction gear housing 9 through openings formed in the side housings 9bL and 9bR, and the output gear shafts 14L and 14R are pulled out to the outboard side. The outer joint portion of the constant velocity joint 65a is splined to the outer peripheral surface of the end portion.

  The constant velocity joint 65a coupled to the output gear shafts 14L and 14R is connected to the drive wheels 61L and 61R via the intermediate shaft 65c and the constant velocity joint 65b (FIG. 6).

An oil seal 55 is provided between the end of the output gear shafts 14L, 14R on the outboard side and the openings formed in the side housings 9bL, 9bR, and leakage of the lubricating oil sealed in the reduction gear housing 9 and the outside Intrusion of muddy water from
The gear unit 30 includes three-element and two-degree-of-freedom planetary gear mechanisms 30L and 30R that are coaxially combined with a pair of left and right output gear shafts 14L and 14R arranged coaxially.

As shown in the enlarged view of FIG. 10, the planetary gear mechanisms 30L and 30R constituting the gear device 30 include internal gears R _L and R _R respectively connected to the output gear 14a of the output gear shafts 14L and 14R, and the internal gears. R _L, R _R and the sun gear S _L provided coaxially, S _R and internal gear R _L, R _R and the sun gear S _L, a plurality of planetary gears P _L as a revolving gear meshing with S _R, P and _R, the planetary gear P _L, is connected to the P _R, the internal gear R _L, R _R and planet carrier C _L provided coaxially, C _R and the left one of the planet carrier C _L (in FIG. 10 FIG. ) And the other sun gear S _R (right side of the figure in FIG. 10), one sun gear S _L (left side of the figure in FIG. 10) and the other planet carrier C _R (FIG. 10). Then, the second coupling member 32 for coupling the output shaft portion 56 of the output gear shaft to the planet carrier. _L, and structure linked to C _R.
In the embodiment shown in FIGS. 9 and 10, an output gear 14a which is connected to the internal gear R _L, R _R is the internal gear R _L, and is formed integrally with the R _R.

Further, in the embodiment shown in FIGS. 9 and 10, the output shaft part 56 connected planet carrier C _L, the C _R is the planet carrier C _L, it is integrally formed with C _R. Planet carrier C _L, the outboard side of the C _R is in contact with collar 40b is provided on the inner ring of the rolling bearing 54b between the rolling bearing 54b for supporting the output gear shaft 14L, 14R. The inboard side of the collar 40b is formed to have a large diameter and abuts on one end of a carrier pin 33 described later.

As shown in FIG. 10, the planetary carriers C _L and C _R are inserted into the carrier flange 34a on the outboard side, the carrier flange 34b on the inboard side, and the holes 35a provided in both the carrier flanges 34a and 34b. And carrier pins 33 that support the gears P _L and P _R.

  The carrier flange 34a on the outboard side includes a hollow shaft portion 35 extending toward the outboard side, and the end portion on the outboard side of the hollow shaft portion 35 is formed on the side housings 9bL and 9bR of the reduction gear housing 9. It is supported by the fitting hole 53b via the rolling bearing 54b. Further, the end portion on the outboard side of the hollow shaft portion 35 is formed integrally with the output shaft portion 56 of the output gear shaft.

The carrier flange 34b on the inboard side includes a hollow shaft portion 36 extending toward the inboard side, and an end portion on the inboard side of the hollow shaft portion 36 is formed in a bearing fitting hole formed in the partition wall 11 of the central housing 9a. 53a is supported via a rolling bearing 54a.
The planetary gears P _L and P _R are supported by the carrier pin 33 via a needle roller bearing 37 as a rolling bearing.

Further, each carrier flange 34a, 34b facing surface and a planetary gear P _L of, inserting the thrust plate 38 between the P _R, the planetary gear P _L, thereby achieving a smooth rotation of the P _R.
Wherein each carrier flange 34a, 34b outer peripheral surface and the inner gear R _L of the, between the R _R, the rolling bearing 39a, are arranged 39 b.

  A collar 40 is disposed between the carrier flange 34b on the inboard side and the rolling bearing 54a that supports the hollow shaft portion 36 of the carrier flange 34b on the inboard side.

The carrier pin 33 is fixed to the planetary carriers C _L and C _R. In the third embodiment, the rolling bearing 54a for supporting the opposite side of the carrier flange 34b across the planetary gears P _L color 40b and gear 30 provided at both ends of the carrier pin 33 to the outboard side, the P _R Is sandwiched between collars 40 arranged on the inner ring contact surface. In this embodiment, both ends of the carrier pin 33 are sandwiched between the collar 40 installed between the carrier flange 34b on the inboard side and the rolling bearing 54a and the collar 40b on the outboard side, and the carrier pin 33 is moved in the axial direction. It is regulated.

Similarly, in the third embodiment, a notch 33a (FIG. 5) is provided at the end of the carrier pin 33 on the collar 40 side. When installed the carrier pin 33 the planet carrier C _L, the C _R, notches 33a planetary carrier C _L, the inner diameter side of the C _R, i.e., installed so as to face the inner diameter side of the carrier flange 34b. The outer diameter of the collar 40 is inserted into the notch 33 a of the carrier pin 33. When the collar 40 enters the notch 33a of the carrier pin 33, the rotation of the carrier pin 33 is restricted.

As described above, in the gear device 30 which is a torque difference amplification mechanism, the movement of the carrier pin 33 in the axial direction can be restricted by sandwiching both ends of the carrier pin 33 between the collar 40b and the collar 40. Then, the cutout portion 33a provided at one end of the carrier pin 33, when installing the carrier pin 33 the planet carrier C _L, the C _R, that the collar 40 enters the inner diameter side of the cutout portion 33a of the carrier pin 33, The rotational movement of the carrier pin 33 can be restricted. Since the collar 40b and the collar 40 for positioning the planetary carriers C _L and C _R are used as members for sandwiching the carrier pin 33, it is not necessary to manufacture dedicated parts for fixing the carrier pin, thereby suppressing an increase in cost. be able to. Furthermore, since there is no caulking process or dedicated component assembling process and only the assembling process of the gear unit 30 is required, an increase in assembling cost can be suppressed.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. The scope of the present invention is claimed. The equivalent meanings recited in the claims, and all modifications within the scope.

1: Vehicle drive device 2L, 2R: Electric motor 3L, 3R: Reduction gear 4L, 4R: Motor housing 4aL, 4aR: Motor housing body 4bL, 4bR: Outer wall 5: Rotor 6: Stator 9: Reduction gear housing 9a: Center Housing 9bL, 9bR: Side housing 11: Partition walls 12L, 12R: Input gear shaft 12a: Input gear 13L, 13R: Intermediate gear shaft 13a: Input side large gear 13b: Output side small gear 14L, 14R: Output gear shaft 14a : Output gear 30: gear device 30L: first planetary gear mechanism 30R: second planetary gear mechanism 31: first coupling member 32: second coupling member 33: carrier pin 33a: notches 40, 40b: collar 65a , 65b: constant velocity joint 65c: intermediate shaft 70: idler gear C _L, C _R: planet key Rear P _L, P _R: planetary gear _{R L,} R R: internal gear S _L, S _R: sun gear

Claims (8)

Two electric motors mounted on the vehicle and independently controllable, two speed reducers arranged between the two electric motors, and the torques from the two electric motors are incorporated into the two speed reducers. In a vehicle drive device comprising a gear device that distributes to wheels,
The speed reducer is provided between an input gear shaft connected to the electric motor and provided with an input gear, an output gear shaft provided with an output gear connected to a drive wheel, and the input gear shaft and the output gear shaft. An intermediate gear shaft provided with a side large diameter gear and an output side small diameter gear;
The gear device comprises a planetary gear mechanism having three elements and two degrees of freedom provided in combination with the pair of left and right intermediate gear shafts on the same axis.
The planetary gear mechanism includes an internal gear, a planet carrier provided coaxially with the internal gear, a sun gear provided coaxially with the internal gear, and a plurality of planetary gears as revolution gears. A first coupling member that couples one planet carrier and the other sun gear of the two planetary gear mechanisms, and a second coupling member that couples one sun gear and the other planet carrier, An internal gear of the gear device is connected to an input-side large-diameter gear of the intermediate gear shaft of the speed reducer, and a planet carrier of the planetary gear mechanism of the gear device is connected to an output-side small-diameter gear of the intermediate gear shaft;
The planetary carrier is inserted into an outboard-side carrier flange having a shaft portion extending to the outboard side, an inboard-side carrier flange having a shaft portion extending to the inboard side, and holes provided in the carrier flange, respectively. A carrier pin to be
The end portions of the shaft portions of the respective carrier flanges are rotatably supported by the housing of the vehicle drive device via respective rolling bearings,
An output side small-diameter gear of the intermediate gear shaft of the speed reducer is provided on the outer peripheral surface of the shaft portion of one carrier flange, and between the rolling bearing that supports the end portion of the shaft portion of the other carrier flange and the other carrier flange. The color is arranged in
A vehicle drive device characterized in that both ends of the carrier pin are sandwiched between the output-side small-diameter gear and the collar to restrict the movement of the carrier pin in the axial direction.   A notch is provided at the collar side end of the carrier pin, and when the carrier pin is attached to the carrier flange, the notch is disposed on the inner diameter side of the carrier flange, and the collar is formed on the notch. The vehicle drive device according to claim 1, wherein the vehicle drive device is in contact with an inner diameter side to restrict rotational movement of the carrier pin.   The output side small-diameter gear of the intermediate gear shaft is separate from the shaft portion of the carrier flange on the outboard side, and is provided by spline fitting to the shaft portion. Vehicle drive device.   The output side small-diameter gear of the intermediate gear shaft is provided separately from the shaft portion of the carrier flange on the inboard side, and is provided by spline fitting to the shaft portion. Vehicle drive device.   The number of teeth of the output-side small-diameter gear is set so that the tip diameter of the output-side small-diameter gear of the intermediate gear shaft overlaps with the hole into which the carrier pin of the carrier flange of the planetary carrier is inserted in the axial direction. The vehicle drive device according to claim 1, wherein the vehicle drive device is set. Two electric motors mounted on the vehicle and independently controllable, two speed reducers arranged between the two electric motors, and the torques from the two electric motors are incorporated into the two speed reducers. In a vehicle drive device comprising a gear device that distributes to wheels,
The speed reducer is connected to the electric motor and includes an input gear shaft provided with an input gear, and an output gear shaft provided with an output gear connected to a drive wheel,
The gear device comprises a planetary gear mechanism having three elements and two degrees of freedom provided coaxially with a pair of left and right output gear shafts having the output gear.
The planetary gear mechanism includes an internal gear, a planet carrier provided coaxially with the internal gear, a sun gear provided coaxially with the internal gear, and a plurality of planetary gears as revolution gears. A first coupling member that couples one planet carrier and the other sun gear of the two planetary gear mechanisms, and a second coupling member that couples one sun gear and the other planet carrier,
An internal gear of the gear device is connected to an output gear of an output gear shaft of the speed reducer, and a planet carrier of a planetary gear mechanism of the gear device is connected to an output shaft portion of the output gear shaft;
The planetary carrier is inserted into an outboard-side carrier flange having a shaft portion extending to the outboard side, an inboard-side carrier flange having a shaft portion extending to the inboard side, and holes provided in the carrier flange, respectively. A carrier pin to be
The end portions of the shaft portions of the respective carrier flanges are rotatably supported by the housing of the vehicle drive device via respective rolling bearings,
Collars are respectively disposed between rolling bearings supporting the end portions of the shaft portions of the respective carrier flanges and the carrier flanges,
A vehicle drive device characterized in that both ends of the carrier pin are sandwiched between the two collars to restrict axial movement of the carrier pin.   The vehicle drive device according to claim 6, wherein an idler gear is provided between the input gear and the output gear.   When the carrier pin is provided with a notch on at least one of the inboard side and the outboard side of the carrier pin, and the carrier pin is assembled to the planetary carrier, the collar on the notch side becomes the notch of the carrier pin. The vehicle drive device according to claim 6 or 7, wherein the rotational movement of the carrier pin is restricted by abutting against the inner diameter side of the notch.

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