JP2018155327A - Vehicle drive unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of part items, processing man-hours and assembling man-hours by making a second coupling member which is constituted of a hollow shaft of a gear device incorporated into a vehicle drive unit, and a first coupling member inserted into the hollow shaft difficult to be displaced to an axial direction and a radial direction, to secure the rotation accuracy of the first coupling member and the second coupling member, to reduce noise, and to elongate lives of a bearing and a gear.SOLUTION: A first coupling member 31 and a second coupling member 32 of a gear device 30 incorporated into a vehicle drive unit 1 are spline-connected to planetary carriers C, Cat one-side end parts so as to be transmittable in torque, and rotatably supported to planetary carriers C, Cwhich are not the spline-fit planetary carriers C, Cat the other end parts via bearings 49, 72 which are fit to external peripheral faces of the end parts.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 drive sources to left and right drive wheels.

  In a vehicle such as an electric vehicle, 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, thereby reducing the turning moment of the vehicle. It is known to control. For example, when each electric motor is independently connected to the left and right drive wheels via a reduction gear, the rotational speed of each electric motor is reduced by the respective reduction gear, and the output torque of each electric motor is It is increased by each reducer 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.

  By the way, when it is desired to make a difference between the output torques of the left and right drive wheels, a difference is made between the output torques of the left and right electric motors, and the output torques of the left and right electric motors are transmitted to the left and right drive wheels via a reduction gear.

  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 planetary gear mechanisms having three elements and two degrees of freedom are coaxially arranged between two drive sources 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.

  The applicant of the present application has already filed a patent application for a vehicle drive device that is smaller and lighter than the gear device that increases the torque difference in Patent Document 1 and Patent Document 2 (Japanese Patent Application No. 2006-023529). ).

  The vehicle drive device (prior application example 1) for which the applicant of the present application has applied for a patent has the configuration shown in FIGS.

Planetary gear 210L constituting the gearing 300 in the vehicle driving apparatus 200 of Sakinegairei 1, 210R, respectively internal gear R _L, and R _R, the internal gear R _L, planetary provided on R _R coaxial a carrier C _L, and C _R, the internal gear R _L, R _R and the sun gear S _L provided coaxially, and S _R, a plurality of planetary gears P _L as a revolving wheel, and P _R.

Gear 300, one of the planet carrier C _L and the other of the first coupling member 211 for coupling the sun gear S _R, a second coupling member for coupling one of the sun gear S _L and the other planet carrier C _R 212, the first coupling member 211 and the second coupling member 212 are arranged coaxially, and of the first coupling member 211 and the second coupling member 212, the second coupling member 212 is a hollow shaft, The coupling member 211 has a shaft inserted into the second coupling member 212 having a hollow shaft, and the shaft passing between the two planetary gear devices 210L and 210R has a double structure, and the planetary gear device 210L, internal gear R _L of 210R, the input gear 213 R _R a reduction gear, the internal gear R _L, a structure for coupling engaged with the external gear 217 provided on the R _R.

  The vehicle drive device 200 of the prior application example 1 can amplify the torque difference between the drive motors 101L and 101R that drive the left and right wheels and output the amplified torque to the wheels.

  That is, the driving force of the drive motors 101L and 101R is transmitted by the reduction gear train of the three-axis two-stage reduction gear, and the gear device 300 is formed by coaxially connecting the two planetary gear devices 210L and 210R located on the second axis. The difference in input torque is amplified and output to the left and right wheels.

When there is no difference in the rotational speed of the wheels, the insides of the two planetary gear devices 210L and 210R (sun gears S _L and S _R , planetary gears P _L and P _R ) of the gear device 300 are relatively rotated. First, the planetary gear devices 210L and 210R rotate together. When there is a difference in the rotational speed of the wheels, the insides of the two planetary gear devices 210L and 210R of the gear device 300 rotate, and the sun gears S _L and S _R , the internal gears R _L and R _R rotate relative to each other. The planetary gears P _L and P _R rotate and revolve.

JP 2015-21594 A Japanese Patent No. 4907390

  By the way, as described above, the first coupling member 211 and the second coupling member 212 are arranged coaxially, the second coupling member 212 is inserted through the hollow shaft, and the other first coupling member 211 is inserted through the hollow shaft. It has a double structure consisting of two axes.

Axis as the inner double structure, i.e., the first coupling member 211 is attached to the planet carrier C _L and the right sun gear S _R of the left end portion of the left side of the first coupling member 211 is a planet carrier splined against C _L rotation, reverse side, i.e., the rolling bearing 215 (deep groove ball bearing) against the inner circumferential surface of the carrier flange 214 on the outboard side of the right end portion and the other of the planet carrier C _R It is supported freely.

Then, the shaft comprising an outer, i.e., the second coupling member 212 is attached to the right side of the planet carrier C _R and the left of the sun gear S _L, the first coupling member 211 with respect to two radial needle roller bearing The radial position is regulated by 216a and 216b, and the axial position is regulated by two thrust roller bearings 218a and 218b for the first coupling member 211. A collar 219 is accommodated between the two radial needle roller bearings 216a and 216b.

  However, positioning the second coupling member 212 using the four rolling bearings 216a, 216b, 218a, and 218b is a good surface suitable as a rolling surface where the rolling surfaces of those bearings are positioned. In addition to the need for finishing to the roughness, if the collar 219 between the two radial needle roller bearings 218a, 218b is included, there are problems that the number of parts, the number of processing steps, the number of assembly steps are large, and the manufacturing cost is high.

  Further, if there is a misalignment between the first coupling member 211 and the second coupling member 212, the gear will be misaligned, that is, its axis will deviate from its ideal position and rotate.

  As a result, the meshing state of the gear tooth surfaces changes, and an abnormal noise is generated or a sound (noise) generated by the rotation is increased.

  In addition, if the position of the gear in the axial direction is greatly displaced, there is a concern that contact with other components or the meshing area of the tooth surface may be reduced, resulting in excessive tooth surface pressure and early damage.

  Accordingly, the present invention reduces the number of parts, processing man-hours, and assembly man-hours while making it difficult for the gear shaft hollow shaft incorporated in the vehicle drive device and the shaft inserted through the hollow shaft to be displaced in the axial direction and the radial direction. It is another object of the present invention to ensure the rotational accuracy of the gear shaft, reduce noise, and extend the life of rolling bearings and gears.

  In order to solve the above-described problems, the present invention is provided with two drive sources mounted on a vehicle and independently controllable, left and right drive wheels, and between the drive source and the drive wheels. In a vehicle drive device comprising: a gear device that distributes torque from one drive source to the left and right wheels; and a reduction device that transmits the torque of the two drive sources to the drive wheel, the reduction device is connected to the drive source. At least one input gear shaft having an input gear, an output gear shaft connected to a drive wheel and having an output gear, and an intermediate gear shaft for transmitting torque between the input gear shaft and the output gear shaft by meshing of the gears. One or more gears constituting the reduction gear are external gears, and the gear device that distributes torque from the two drive sources to the left and right wheels is coaxial with a pair of left and right gear shafts arranged coaxially. 3 elements 2 free combined above 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 revolution gears. A first coupling member for coupling one planet carrier and the other sun gear of the two planetary gear mechanisms, and a second coupling for coupling one sun gear and the other planet carrier. The first coupling member is coaxially disposed inside the second coupling member, which is a hollow shaft, and both the first coupling member and the second coupling member can transmit torque at one end. The planetary carrier is connected to the planetary carrier by spline fitting, and the planetary carrier which is not the planetary carrier which is spline-fitted at the other end is rotated via a bearing fitted to the outer peripheral surface of each end. To be supported freely Characterized in that it was.

  The rolling bearings that fit into the planet carrier and support the first coupling member and the second coupling member both have an interference fit with the inner circumferential surface of the planet carrier, and the outer circumferential surface of the first coupling member or the second coupling member. A clearance fit is preferred.

  Moreover, a deep groove ball bearing can be used as a rolling bearing fitted to one end of each of the first coupling member and the second coupling member.

  A convex portion is provided on the outer peripheral surface of the second coupling member, and the second coupling member is brought into contact with the spline hole by causing the convex portion to abut the end of the planet carrier on which the second coupling member is spline-fitted. The axial direction can be restricted so as not to enter too much.

  A retaining ring is provided in the spline hole of the planetary carrier in which the first coupling member is spline-fitted, and the retaining ring and the end of the first coupling member abut against each other, so that the first coupling member is splined. The axial direction can be restricted so as not to go too far.

The outer diameter surface of the first coupling member in the vicinity of the spline portion of the planet carrier to which the first coupling member is spline-fitted, or the second coupling member in the vicinity of the spline portion of the planet carrier to which the second coupling member is spline-fitted. By providing an inlay portion for inlay alignment between at least one outer diameter surface of the outer diameter surface and the inner diameter surface of the planet carrier, alignment of the first coupling member and the second coupling member can be enhanced.
The spigot part can be a clearance fit rather than an interference fit.

  As described above, the first coupling member and the second coupling member of the gear device incorporated in the vehicle drive device are both connected to the planet carrier by spline fitting so that torque can be transmitted at one end, and the other end The planetary carrier that is not the spline-fitted planet carrier is rotatably supported via the rolling bearings fitted to the outer peripheral surfaces of the respective end portions, so that the axial direction and the radial direction are supported. Misalignment hardly occurs and alignment is high.

  Thereby, the number of parts, processing man-hours, and assembly man-hours can be reduced, the rotation accuracy of the gear shaft can be ensured, noise can be reduced, and the life of the rolling bearings and gears can be extended.

It is a cross-sectional top view which shows embodiment of the vehicle drive device of this invention. It is an enlarged view of the gear apparatus part of embodiment of FIG. It is a perspective view at the time of attaching the oil guide member used for the planetary gear apparatus in the embodiment of FIG. 1 on the left side. It is a perspective view at the time of attaching the oil guide member used for the planetary gear apparatus in the embodiment of FIG. 1 on the right side. It is explanatory drawing of the electric vehicle which showed the gear structure of the vehicle drive device which concerns on embodiment of FIG. 1 with the skeleton figure. It is a speed diagram for demonstrating the torque difference amplification factor by the gear apparatus incorporated in the vehicle drive device which concerns on embodiment of FIG. It is a cross-sectional top view which shows 2nd Embodiment of the vehicle drive device of this invention. It is an enlarged view of the gear apparatus part of embodiment of FIG. It is a cross-sectional top view which shows the vehicle drive device of a prior application example. FIG. 10 is an enlarged view of the gear device portion of the prior application example of FIG. 9.

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

  The electric vehicle AM shown in FIG. 5 is a rear wheel drive system, and includes a chassis 60, drive wheels 61L and 61R as rear wheels, front wheels 62L and 62R, and a two-motor vehicle drive device 1 according to the present invention. , A battery 63, an inverter 64, and the like. In FIG. 5, the gear structure of the vehicle drive device 1 is shown with the skeleton figure.

  The vehicle drive device 1 is provided between two electric motors 2L and 2R, which are mounted on a vehicle and can be controlled independently, and left and right drive wheels 61L and 61R and the two electric motors 2L and 2R. Two left and right reduction gears 3L and 3R are provided.

  The drive torque of the two-motor type vehicle drive device 1 is transmitted to the left and right drive wheels 61L and 61R via a drive shaft composed of constant velocity joints 65a and 65b and an intermediate shaft 65c.

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

  The left and right electric motors 2L and 2R in the two-motor type vehicle drive device 1 use the same standard electric motors having the same maximum output, and are housed in the motor housings 4L and 4R as shown in FIG. Yes.

  As shown in FIG. 1, 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 motor housing bodies 4aL, The inner side surface of 4aR is composed of inner side walls 4cL and 4cR separated from the reduction gears 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 reduction gears 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 perpendicular 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).

  A plurality of bolts 10 are used to fix side faces 9bL and 9bR of the reduction gear housing 9 on the side of 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. 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).

  As shown in FIG. 1, the central housing 9a is provided with a partition wall 11 at the center. The speed reducer housing 9 is divided into left and right parts by the partition wall 11, and left and right accommodation chambers for housing the two speed reducers 3L and 3R are provided in parallel.

  As shown in FIG. 1, the reduction gears 3L and 3R are provided substantially symmetrically and mesh with the input gear shafts 12L and 12R having the input gear 12a to which power is transmitted from the motor shaft 5a. Intermediate gear shafts 13L and 13R having an output side small diameter gear 13b meshing with the input side large diameter gear 13a and the output gear 14a, and an 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 the drive wheels 61L, 61R via a shaft 65c (FIG. 5). 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 speed reducer 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 are stepped gear shafts having an input-side large-diameter gear 13a meshed with the input gear 12a and an output-side small-diameter gear 13b meshed 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. The bearing fitting holes 19a and 19b have a stepped shape having a wall portion with which the outer rings of the rolling bearings 20a and 20b abut. The bearing fitting holes 19a are formed with a first coupling member 31 and a second coupling member which will be described later. It penetrates so that the coupling member 32 may pass.

  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.

  The gear unit 30 is composed of a pair of left and right intermediate gear shafts 13L and 13R arranged on the same axis and two planetary gear mechanisms 39L and 39R with two elements on the same axis.

As shown in the enlarged view of FIG. 2, the planetary gear mechanisms 39L and 39R constituting the gear device 30 have 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} , 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. 2), and the other sun gear S _R (A right side of the figure in FIG. 2), a first coupling member 31 that couples to one side, one sun gear S _L (the left side of the figure in FIG. 2), and the other planet carrier C _R (the right side of the figure in FIG. 2). a second coupling member 32 for coupling the inner gear R _L, linked to R _R, an input gear 12a of the input gear shaft 12L, 12R The intermediate gear shafts 13L and 13R have input side large diameter gears 13a, and the output gear shafts 14L and 14R output gears 14a and the intermediate gear shafts 13L and 13R output side small diameter gears 13b. The output side small-diameter gear 13b of 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.

  The embodiment shown in FIGS. 1 and 2 is an example in which the gear device 30 is combined with the intermediate gear shafts 13L and 13R. However, if the gear shaft is arranged coaxially, the output gear shafts 14L and 14R or It can also be combined with the input gear shafts 12L and 12R.

In the embodiment shown in FIGS. 1 and 2, the internal gear R _L, the input-side large diameter gear 13a which is connected to R _R is the internal gear R _L, but are formed integrally with the R _R, formed separately May be.

Further, in the embodiment shown in FIGS. 1 and 2, the planet carrier C _L, output-side small-diameter gear 13b is coupled to the C _R, the planet carrier C _L, although formed integrally with the C _R, separately It may be formed. The input side large diameter gear 13a and the output side small diameter gear 13b are both external gears having gear teeth on the outer periphery.

As shown in FIG. 2, the planetary carriers C _L and C _R are composed of a carrier pin 33 that supports the planetary gears P _L and P _R , and an outboard side (outside of the vehicle) connected to an end of the carrier pin 33 on the outboard side. ) Carrier flange 34a and an inboard side (vehicle inner side) carrier flange 34b connected to the inboard side end.

  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 speed reducer 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.

  In the embodiment shown in FIGS. 1 and 2, the output-side small-diameter gear 13b is integrally formed on the outer peripheral surface of the hollow shaft portion 35 of the carrier flange 34a.

As shown in FIG. 2, the planetary gears P _L and P _R are supported by carrier pins 33 via needle roller bearings 37.

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 50a, are disposed 50b.

  In addition, a stepped portion 40 is formed on the inboard side outer diameter surface of the inboard carrier flange 34b. The stepped portion 40 contacts the end surface of the inner ring of the rolling bearing 20a that supports the hollow shaft portion 36 of the carrier flange 34b.

  The first coupling member 31 and the second coupling member 32 that couple the two planetary gear mechanisms 39L and 39R 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 second coupling member 32 consists of a hollow shaft is provided in carrier flanges 34b and separate the inboard side of the right-hand planet carrier C _R.

The second coupling member 32 provided on the carrier flange 34b and another body, a spline portion 41 provided on the inner surface of the outer diameter surface and the carrier flange 34b of the right end portion of the second coupling member 32, the planet carrier C _R On the other hand, it is connected so that torque can be transmitted by spline fitting.

The outer diameter surface of the spline portion 41 near the second coupling member 32, as shown in FIG. 2, to form a convex portion 79 which an end face of the hollow shaft portion 36 of the inboard side of the planet carrier C _R is abutted. The second coupling member 32, as the convex portion 79 of the outer surface is that abuts the end face of the hollow shaft portion 36 of the inboard side of the planet carrier C _R, the second coupling member 32 is not too enters the spline hole, Movement to the right in the axial direction is restricted.

Further, the left end portion of the second coupling member 32, i.e., the spline is engaged the end which is not a planet carrier C _R and the carrier flange 34a on the outboard side of the planet carrier C _L on the left side of the planetary gear mechanism 39L It is rotatably supported by a rolling bearing 72 located on the inner diameter surface of the. The rolling bearing 72 is a deep groove ball bearing. The inner surface of the outboard side of the carrier flange 34a of the planetary carrier C _L, shoulder 75 is provided with an end face of the outer ring of the outboard side of the rolling bearing 72 hits.

  Further, a shoulder portion 76 is provided on the outer diameter surface of the left end portion of the second coupling member 32 so as to contact the end surface on the inboard side of the inner ring of the rolling bearing 72.

The second coupling member 32, the rolling bearing 72 to hit and the shoulder portion 75 of the carrier flange 34a of the shoulder 76 and the planet carrier C _L of the second coupling member 32 via the (deep groove ball bearings), to move in the left In addition to being restricted, machining tolerances of each part are appropriately allowed so that the rolling bearing 72 (deep groove ball bearing) is not subjected to excessive preload (pushing in the axial direction).

That is, the axial direction of the stopper of the second coupling member 32, the convex portion 79 of the outer surface in the vicinity of the spline portion 41 side, carried out by the above-described rolling bearing 72 (deep groove ball bearings), the planet carrier C _L flange The inner diameter surface of 34a and the outer diameter surface of the rolling bearing 72 (deep groove ball bearing) are interference-fitted (tight fitting with tightening allowance), and the outer diameter surface of the second coupling member 32 and the rolling bearing 72 (deep groove ball). By making the inner diameter surface of the bearing) a clearance fit (loose fit with a clearance), axial displacement due to processing tolerances at the fitting portion of the second coupling member 32 and the rolling bearing 72 is allowed. be able to.

Further, the outer diameter surface vicinity of the spline portion 41 of the second coupling member 32 is provided with a socket portion 71 for centering with respect to the inner diameter surface of the planetary carrier C _R of the carrier flange 34b hollow shaft portion 36 provided on and which eliminates the rattling of the spline portion 41 splined to the planet carrier C _R by spigot portion 71, to enhance the alignment of the second coupling member 32.

A sun gear S _L that meshes with the planetary gear P _L of the left planetary gear mechanism 39L is provided separately from the second coupling member 32 on the outer diameter surface of the left end portion of the second coupling member 32.

This separate sun gear S _L is spline-fitted by a spline portion 73 to the outer diameter surface of the left end portion of the second coupling member 32, and a circlip 74 is provided on the spline portion 73 in the axial direction. I'm keeping it from coming off.

By providing the sun gear S _L at the left end of the second coupling member 32 separately from the second coupling member 32, the sun gear _SL and the second coupling member 32 are in a floating state. The rotation accuracy of the aligned second coupling member 32 can be maintained high.

On the other hand, the right end portion of the first coupling member 31 that is inserted into the hollow of the second coupling member 32, a hollow shaft portion extending outboard side of the carrier flange 34a of the planetary carrier C _R of the right planetary gear mechanism 39R 35 is supported by a rolling bearing 49 constituted by a deep groove ball bearing.

Rolling bearing 49 has its outer diameter surface, an interference fit against the inner surface of the carrier flange 34a of the planetary carrier C _R of the right planetary gear mechanisms 39R and (tight fitting with a tightening margin), the inner surface The position of the first coupling member 31 in the axial direction due to machining tolerances at the fitting portion between the first coupling member 31 and the rolling bearing 49 by making a clearance fit (loose fitting with a clearance) with respect to the outer diameter surface of the first coupling member 31. The deviation is allowed.

Rolling bearing 49 on the outer diameter portion of the right end portion of the first coupling member 31 which is supported on a carrier flange 34a of the right planetary carrier C _R by (deep groove ball bearing) is a planetary gear of the right planetary gear mechanism 39R P _R It is provided sun gear S _R meshing with.

Left end of the first coupling member 31, a spline portion 42 formed in the inner diameter surface of the carrier flange 34a of the planetary carrier C _L of the left side of the planetary gear mechanism 39L, splined a first coupling member 31 to the planet carrier C _L They are connected together and positioned in the axial direction by a retaining ring 78.

The outer diameter surface of the vicinity of the splined portion 42 of the first coupling member 31, the socket portion 90 for performing centering against the radially inner surface of the carrier flange 34a of the planetary carrier C _L provided, the planet carrier by socket portion 90 C _L On the other hand, the spline portion 42 that is spline-fitted is free from backlash, and the alignment of the first coupling member 31 is enhanced.

The first coupling member 31, similar to the second coupling member 32, the rolling bearing 49 located on the inner peripheral surface of the carrier flange 34a of the planetary carrier C _R of the right planetary gear mechanism 39R (deep groove ball bearings), the left the planetary gear mechanism 39L of the planet carrier C _L snap ring 78 provided on the splined portion 42 of the inner periphery of the carrier flange 34a of, along with the axial movement of the first coupling member 31 is restricted, the rolling bearing 49 (deep groove In order to prevent an excessive preload from being applied to the ball bearing), misalignment is allowed depending on the machining tolerance of each part.

Both the first coupling member 31 and the second coupling member 32 are provided with spigot portions 71 and 90 in the vicinity of the spline portions 41 and 42 at one end, and are arranged so as to be close to the same axis up to a very small gap. At the same time, the other end rolling bearings 49 and 72 (deep groove ball bearings) are supported with high precision with respect to the planetary carriers C _L and C _R. Accordingly, the sun gears S _L and S _R of the planetary gear mechanisms 39L and 39R can be rotated near the ideal state (axial center) without being swung around, so that the inner surface of the second coupling member 32 formed in a hollow space There is no need to provide a needle roller bearing or collar between the outer diameter surface of the first coupling member 31, misalignment due to run-out or misalignment is unlikely to occur, noise reduction due to gear meshing, and eccentric load It is possible to prevent the tooth surface from being damaged early (peeling, abnormal wear, etc.).

Further, the retaining ring 78 the projections 79 and the first coupling member 31, the outer periphery of the second coupling member 32 is attached to the spline portion 42 of the inner periphery of the planet carrier C _L spline fitting, axial movement Since it is regulated, the spline portions 41 and 42 into which the first coupling member 31 and the second coupling member 32 are fitted do not enter too much. Further, since the rolling bearings 49 and 72 are also restricted from moving in the axial direction by the engagement of the planetary carriers C _L and C _R , it is possible to allow both the retaining and the axial displacement due to processing tolerances. it can.

  That is, since the fitting between the first coupling member 31 and the second coupling member 32 and the rolling bearings 49 and 72 (deep groove ball bearings) supporting them is a clearance fitting, the deviation due to processing tolerances is a clearance fitting fit. The joint can be allowed to move slightly in the axial direction.

  As described above, no excessive load (preload) is applied to the rolling bearings 49 and 72 (deep groove ball bearings), and the gears move greatly in the axial direction and interfere with other parts, resulting in damage to the tooth surface. Since the meshing area is reduced and an excessive tooth surface pressure is not generated, early breakage can be prevented, and the life of the rolling bearing or gear can be extended.

In the meantime, in the embodiment shown in FIGS. 1 and 2, in order to reduce the axial dimension of the gear device 30, a concave portion 80 is provided on the inboard side surface of the planetary carriers C _L and C _R , and the concave portion 80 is provided in the concave portion 80. Among the rolling bearings 20a and 20b that support both ends of the planetary carriers C _L and C _R , a part of the in-board side rolling bearing 20a enters, and the in-board side rolling bearing 20a and the internal gears R _L and R _R. are arranged so as to partially overlap the planet carrier C _L, the rolling bearing 50a which supports against C _R, the rolling bearing 50b are axially inboard of 50b.

As described above, when a part of the inboard side rolling bearing 20a is inserted into the recess 80 on the inboard side of the planetary carriers C _L and C _R , in oil bath lubrication and splash lubrication by rotation of gears, Lubricating oil is difficult to be supplied to the inboard rolling bearing 20a.

  For this reason, in the embodiment shown in FIG. 1 and FIG. 2, of the rolling bearings 20 a and 20 b that support the gear device 30, it is difficult to supply the lubricating oil by oil bath lubrication or splash lubrication by rotation of the gear. The lubricating oil supply path is secured as follows so that the lubricating oil is supplied to the rolling bearing 20a.

  First, the first coupling member 31 is provided with a plurality of radial holes 82 and 83 that are out of phase with the axial hole 81 and serve as an oil passage for the axial center oil supply.

  A plurality of radial holes 84 having different phases are also provided in the second coupling member 32 formed of a hollow shaft.

Axial bore 81 provided in the first coupling member 31 has one end open to the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _L.

Axial bore 81 provided in the first coupling member 31 has its other end is provided so as to exceed the hollow shaft portion 36 extending inboard side of the carrier flange 34b on the inboard side of the planet carrier C _L.

Of radial holes 82, 83 provided on the first coupling member 31, the radial bore 82 of the outboard side, the inboard side of the carrier flange 34a of the left end portion and the planet carrier C _L of the second coupling member 32 It is provided so as to open to an inflow gap 85 provided between the end faces.

The other radial hole 83 provided in the first coupling member 31 is provided so as to open at an intermediate position between the left and right planetary carriers C _L and C _R.

In the radial hole 83 provided in the first coupling member 31, the lubricating oil supplied from the radial hole 83 scatters to the inner peripheral surface of the second coupling member 32 and passes through the radial hole 84 of the second coupling member 32. Thus, the axial position of the radial hole 83 of the first coupling member 31 is set to the radial hole 84 of the second coupling member 32 so that the planetary carriers C _L and C _R are easily scattered to the rolling bearing 20a on the inboard side. It is provided in the vicinity.

The radial hole 84 provided in the second coupling member 32 is provided so as to be positioned between the hollow shaft portions 36 on the inboard side of the left and right planetary carriers C _L and C _R.

  The axial position of the radial hole 84 provided in the second coupling member 32 is a position in the vicinity of the rolling bearing 20a so that the lubricating oil easily flows into the inboard rolling bearing 20a.

Then, the inner wall of the reduction gear housing 9, the lubricating oil flowing along the ribs (not shown), more and receiving, planet carrier C _L, the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the C _R In order to be able to supply, the inside of the hollow shaft portion 35 receives the lubricating oil flowing along the inner walls of the left and right side housings 9bL, 9bR facing the openings of the hollow shaft portions 35 on the outboard side of the intermediate gear shafts 13L, 13R. An oil guide member 86 that guides the lubricating oil is attached.

  As shown in FIGS. 3 and 4, the oil guide member 86 is fixed to the side housings 9bL and 9bR by screws (not shown) and has a receiving plate 86b having a funnel-shaped receiving portion 86a on the upper surface, and a bottom portion of the receiving portion 86a. And an oil guide pipe 86c that guides the lubricating oil collected into the receiving portion 86a to the inside of the hollow shaft portion 35 of the intermediate gear shafts 13L and 13R.

  As shown in FIG. 2, the oil guide pipe 86 c of the left oil guide member 86 is inserted into the axial hole 81 provided in the first coupling member 31 and collected by the oil guide member 86. Lubricating oil is supplied into the axial hole 81 of the first coupling member 31 through the oil guide pipe 86c.

In the left planetary gear mechanism 39L, the lubricating oil flowing along the inner wall and rib of the speed reducer housing 9 flows from the rolling bearing 20b into the receiving portion 86a of the oil guide member 86 attached to the side housing 9bL. The lubricating oil collected by flowing into the receiving portion 86a of the oil guide member 86 is guided into the axial hole 81 of the first coupling member 31 through the oil guide pipe 86c. Inside supplied lubricating oil axial hole 81 of the first coupling member 31 is then in the radial direction hole 82 of the left side of the first coupling member 31 of the left end portion and the planet carrier C _L of the second coupling member 32 The inflow gap 85 provided between the carrier flange 34a and the end face on the inboard side passes through the rolling bearing 72 that supports the left end of the second coupling member 32, and is supplied to the planetary gear P _L and supplied to the planetary gear P _L. Lubricate the tooth surfaces of the internal and external gears. The lubricating oil supplied to the inside of the axial hole 81 of the first coupling member 31 scatters from the radial hole 83 on the inboard side to the inner peripheral surface of the second coupling member 32, The lubricating oil scattered on the inner peripheral surface is further scattered from the radial hole 84 of the second coupling member 32 and supplied to the rolling bearing 20a that supports the carrier flange 34b on the inboard side of the two planetary gear mechanisms 39L and 39R. The As a result, it is possible to prevent the rolling bearing 20a that supports the carrier flange 34b from being damaged early due to poor lubrication or abnormal noise.

In the other planetary gear mechanism 39R on the right side, the lubricating oil flowing along the inner wall and rib of the speed reducer housing 9 flows from the rolling bearing 20b into the receiving portion 86a of the oil guide member 86 attached to the inner wall of the side housing 9bR. The lubricating oil flowing into the receiving portion 86a of the oil guiding member 86 is guided to the inside of the hollow shaft portion 35 of the carrier flange 34a through the oil guiding tube 86c, and then supports the right end of the first coupling member 31. through the rolling bearing 49, it is supplied to the inserted outer periphery of the thrust plate 38 between the carrier flange 34a and the planetary gear P _R of the planetary carrier C _R, to lubricate the inside and the tooth surface of the external gear of the planetary gear P _R .

  Next, as shown in FIG. 1, the output gear shafts 14L and 14R have large-diameter output gears 14a, bearing fitting holes 53a formed on both surfaces of the partition wall 11 of the central housing 9a, and side housings 9bL, It is supported by rolling bearings 54a and 54b in a bearing fitting hole 53b formed in 9bR. 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 from openings formed in the side housings 9bL and 9bR, and are pulled out to the outboard side of the output gear shafts 14L and 14R. 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. 5).

  An oil seal 55 is provided between the end of the output gear shafts 14L and 14R on the outboard side and the opening formed in the side housings 9bL and 9bR, and leakage of the lubricating oil sealed in the speed reducer 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. 5, 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.

The torque of the motor shaft 5a of the electric motors 2L and 2R increases with the gear ratio between the input gear shaft 12a of the input gear shafts 12L and 12R of the reduction gears 3L and 3R and the input side large gear 13a of the intermediate gear shafts 13L and 13R. And transmitted to the internal gears R _L and R _R of the gear device 30.

  Then, the output side small gear 13b of the intermediate gear shafts 13L and 13R meshes with the large diameter output gear 14a of the output gear shafts 14L and 14R via the gear device 30, and the number of teeth of the output side small gear 13b and the output gear 14a. The torque of the motor shafts 5a of the electric motors 2L and 2R is further increased by the ratio and output to the drive wheels 61L and 61R.

  The gear device 30 is configured by combining two identical planetary gear mechanisms 39L and 39R with three elements and two degrees of freedom on coaxial intermediate gear shafts 13L and 13R. As the planetary gear mechanisms 39L and 39R, a single pinion type is used. A planetary gear mechanism is used.

The planetary gear mechanisms 39L and 39R are coaxially provided with sun gears S _L and S _R and internal gears R _L and R _R, and between these sun gears S _L and S _R and the internal gears R _L and R _R. a plurality of planetary gears P _L, P _R is close to the planetary gear P _L, provided the P _R rotatably supported by the sun gear S _L, S _R and the internal gear R _L, on R _R coaxial It is composed of planetary carriers C _L and C _R. Here, the sun gear S _L, S _R and the planetary gears P _L, P _R is the external gear having gear teeth on the outer circumference, the internal gear R _L, R _R is the internal gear having gear teeth on the inner peripheral is there. The planetary gears P _L and P _R mesh with the sun gears S _L and S _R and the internal gears R _L and R _R.

In the planetary gear mechanisms 39L and 39R, 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. In the figure, the internal gears R _L and R _R and the sun gears S _L and S _R are arranged on the opposite side to the planetary carriers C _L and C _R.

As described above, the gear device 30 includes the first planetary gear mechanism 39L having the sun gear S _L , the planet carrier C _L , the planet gear P _L, and the internal gear _RL , the sun gear S _R , and the planet carrier C. _R, a second planetary gear mechanism 39R having a planetary gear P _R and the internal gear R _R is configured by combining coaxially.

Then, coupled with the planet carrier C _L of the first planetary gear mechanism 39L and the sun gear S _R of the second planetary gear mechanism 39R form a first coupling member 31, the sun of the first planetary gear mechanism 39L gear S _L and the planet carrier C _R of the second planetary gear mechanism 39R form a second coupling member 32 are coupled.

Torque TM1 generated by the electric motor 2L in the internal gear _RL of the first planetary gear mechanism 39L is transmitted to the intermediate gear shaft 13L by meshing the input gear 12a of the input gear shaft 12L with the input-side large-diameter gear 13a, The torque transmitted to the intermediate gear shaft 13L is transmitted to the output side small diameter gear 13b of the intermediate gear shaft 13L via the first planetary gear mechanism 39L, and the output side small diameter gear 13b and the output gear shaft 14L of the intermediate gear shaft 13L. And the output gear 14a meshes with each other, and the drive torque TL is output from the output gear shaft 14L to the drive wheel 61L.

Torque TM2 generated by the electric motor 2R to the internal gear R _R of the second planetary gear mechanism 39R includes an input gear 12a of the input gear shaft 12R and the input-side large diameter gear 13a is transmitted to the intermediate gear shaft 13R meshing, The torque transmitted to the intermediate gear shaft 13R is transmitted to the output-side small-diameter gear 13b of the intermediate gear shaft 13R via the second planetary gear mechanism 39R, and the output-side small-diameter gear 13b and the output gear shaft 14R of the intermediate gear shaft 13R. The output gear 14a meshes with the output gear shaft 14R, and the drive torque TR is output from the output gear shaft 14R to the drive wheel 61R.

Electric motor 2L, the output from the 2R, the two planetary gear mechanisms 39L, each of the internal gear R _L of 39R, given R _R, the first coupling member 31, the output from the second coupling member 32 is the driving wheel 61L , 61R.

  The 2nd coupling member 32 is comprised by the hollow shaft, the 1st coupling member 31 is penetrated in the inside, and the axis | shaft which comprises the 1st coupling member 31 and the 2nd coupling member 32 has a double structure. .

The first coupling member 31, as shown in FIGS. 1 and 2, one end is the rotation axis of (right end in the drawing) is the sun gear S _R, the other end (left end in the drawing) penetrates the sun gear S _L And is connected to the planet carrier C _L. The second coupling member 32 is a hollow shaft, one end (left end in the drawing) has a rotation shaft of the sun gear S _L, the other end (right end in the drawing) is connected to the planet carrier C _R. The first planetary gear mechanisms 39L and 39R 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 type planetary gear mechanisms 39L and 39R, and therefore can be represented by two velocity diagrams as shown in FIG. Here, for easy understanding, the two speed diagrams are shifted up and down, the speed diagram of the left planetary gear mechanism 39L is shown on the upper side, and the speed diagram of the right planetary gear mechanism 39R is shown on the lower side. Originally, in the embodiment of FIG. 1, the torques TM1 and TM2 output from the electric motors 2L and 2R are respectively input via the input-side large-diameter gears 13a meshing with the input gears 12a of the input gear shafts 12L and 12R. A reduction ratio is applied because it is input to the internal gears R _L and R _R , and the drive torques TL and TR taken out from the gear device 30 are applied to the left and right drive wheels 61L via the output-side small gear 13b meshing with the output gear 14a. However, in order to facilitate understanding, hereinafter, in the description of the speed diagram and each calculation formula shown in FIG. 4, the reduction ratio is omitted, and the internal gears R _L , The torque input to R _R remains TM1 and TM2, and the drive torque remains TL and TR.

Since the two planetary gear mechanisms 39L and 39R 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 _L and the planet carrier C _R are also equal, and this 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. 6, the arrow direction in the figure 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 present invention, the electric motor 2L, input from 2R is, R _L, R _R, and the drive wheels 61L, the output of the 61R becomes _{S R + C L, S L} + C R.

  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 61L A drive torque difference ΔTOUT (= α · (TM2−TM1)) larger than the input torque difference ΔTIN can be given to the drive torques TL and TR transmitted to the drive wheel 61R.

  In the prior art 1 and the prior art 2, since the left and right connecting members of the two planetary gear mechanisms of the gear device which is the torque difference amplifying mechanism include the internal gear, the connecting member 1 connecting either the left or right internal gear and another member is used. One must have a larger diameter than the other internal gear.

In the present invention, the connection between the two planetary gear mechanisms 39L and 39R 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. No connection member having a larger diameter than the internal gears R _L and R _R is required. For this reason, in this invention, since the torque difference distribution mechanism can be made smaller than those of the prior art 1 and the prior art 2, the vehicle drive device 1 for an electric vehicle incorporating the torque difference distribution mechanism is made smaller and lighter. Can be

  By reducing the size and weight of the vehicle driving device 1 for an electric vehicle, the degree of freedom of the vehicle body mounting layout of peripheral accessories is improved along with the vehicle body mounting layout of the vehicle driving device 1.

  Further, there is a merit that the vehicle interior space is expanded by downsizing the vehicle drive device 1.

  As described above, in the embodiment shown in FIGS. 1 and 2, the output gear 14a of the output gear shafts 14L and 14R is provided on the outboard side (outside of the vehicle) of the reduction gears 3L and 3R. As shown in the figure, the output gear 14a of the output gear shafts 14L, 14R may be provided on the inboard side (inside the vehicle) of the reduction gears 3L, 3R.

  In the embodiment shown in FIG. 1 and FIG. 2 and the embodiment shown in FIG. 7 and FIG. 8, electric motors 2L and 2R are used as two drive sources, and the same standard electric motor having the same maximum output is used. Although illustrated, two drive sources are not restricted to this.

In the embodiment shown in FIG. 1 and FIG. 2 and the embodiment shown in FIG. 7 and FIG. 8, rolling bearings which are fitted to the planetary carriers C _L and C _R and support the first coupling member 31 and the second coupling member 32. However, the present invention is not limited to this, and other types of rolling bearings such as needle roller bearings and cylindrical roller bearings, and any bearing that supports a rotating shaft such as a sliding bearing may be used. It may be of a form.

  The vehicle on which the vehicle drive device 1 is mounted is not limited to an electric vehicle or a hybrid electric vehicle, and may be, for example, a fuel cell vehicle that uses the first electric motor 2L and the second electric motor 2R as driving sources. Good.

  The present invention is not limited to the above-described embodiments, and can be further implemented in various forms without departing from the gist of the present invention.

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, 4cL, 4cR: inner wall, 5: rotor, 5a: motor shaft,
6: Stator, 7: Seal member, 8a, 8b: Rolling bearing,
9: Reduction gear housing, 9a: Central housing,
9bL, 9bR: side housing, 10: bolt, 11: partition wall,
12L, 12R: input gear shaft, 12a: input gear, 13L, 13R: intermediate gear shaft,
13a: input side large diameter gear, 13b: output side small diameter gear, 14L, 14R: output gear shaft,
14a: output gear, 16a, 16b: bearing fitting hole, 17a, 17b: rolling bearing,
18: Oil seal, 19a, 19b: Bearing fitting hole, 20a, 20b: Rolling bearing,
30: gear device, 31: first coupling member, 32: second coupling member, 33: carrier pin,
34a, 34b: carrier flange, 35, 36: hollow shaft portion, 37: needle roller bearing,
38: Thrust plate, 39L, 39R: Planetary gear mechanism, 40: Step portion,
41, 42: Spline part, 49: Rolling bearing, 50a, 50b: Rolling bearing,
53a, 53b: bearing fitting hole, 54a, 54b: rolling bearing, 55: oil seal,
60: Chassis, 61L, 61R: Drive wheel, 62L, 62R: Front wheel,
63: battery, 64: inverter, 65a, 65b: constant velocity joint,
65c: intermediate shaft, 71: spigot section, 72: rolling bearing,
73: Spline part, 74: Circlip, 75, 76: Shoulder part, 78: Retaining ring,
79: convex portion, 80: concave portion, 81: axial hole, 82, 83: radial hole,
84: radial hole, 85: inflow gap, 86: oil guide member, 86a: receiving part,
86b: backing plate, 86c: oil guide pipe, 90: spigot section,
AM: Electric vehicle, C _L , C _R : Planetary carrier, P _L , P _R : Planetary gear,
R _L , R _R : Internal gear, S _L , S _R : Sun gear

Claims (7)

Two drive sources mounted on the vehicle and independently controllable,
Left and right drive wheels,
A gear device that is provided between the drive source and the drive wheel and distributes torque from the two drive sources to the left and right wheels;
A vehicle drive device comprising: a speed reducer that transmits torque of the two drive sources to the drive wheels;
The speed reducer is
An input gear shaft coupled to the drive source and having an input gear;
An output gear shaft coupled to the drive wheel and having an output gear;
At least one intermediate gear shaft for transmitting torque between the input gear shaft and the output gear shaft by meshing of the gears;
The gear constituting the reduction gear is an external gear,
The gear device that distributes the torque from the two drive sources to the left and right wheels comprises a planetary gear mechanism having three elements and two degrees of freedom that are coaxially combined with a pair of left and right gear shafts arranged coaxially.
The planetary gear mechanism is
An internal gear,
A planet carrier provided coaxially with the internal gear;
A sun gear provided coaxially with the internal gear;
Having a plurality of planetary gears as revolution gears,
A first coupling member that couples one planet carrier of the two planetary gear mechanisms and the other sun gear;
A second coupling member for coupling one sun gear and the other planet carrier;
The first coupling member is coaxially disposed inside the second coupling member that is a hollow shaft,
The first coupling member and the second coupling member are
Both are connected to the planet carrier by spline fitting so that torque can be transmitted at one end,
A vehicle that is rotatably supported by a planet carrier that is not a planet carrier that is spline-fitted at the other end via a bearing that is fitted to the outer peripheral surface of each end. Drive device. Mates with the planet carrier,
The bearings supporting the first coupling member and the second coupling member are:
Both are interference fits to the inner circumference of the planet carrier,
The vehicle drive device according to claim 1, wherein the vehicle drive device is a clearance fit with respect to an outer peripheral surface of the first coupling member or the second coupling member. Bearings fitted to one end of each of the first coupling member and the second coupling member are
The vehicle drive device according to claim 1, wherein the vehicle drive device is a deep groove ball bearing. A convex portion is provided on the outer peripheral surface of the second coupling member,
When the convex portion abuts against the end of the planet carrier on which the second coupling member is spline-fitted,
The vehicle drive device according to any one of claims 1 to 3, wherein the second coupling member is axially restricted so as not to enter the spline hole of the spline portion too much. Attach a retaining ring to the spline hole of the spline part of the planet carrier where the first coupling member is spline-fitted,
The end of the first coupling member is abutted against this retaining ring,
The vehicle drive device according to any one of claims 1 to 4, wherein the first coupling member is axially restricted so as not to enter the spline hole of the spline portion too much.   The outer diameter surface of the first coupling member in the vicinity of the spline portion of the planet carrier to which the first coupling member is spline-fitted, or the second coupling member in the vicinity of the spline portion of the planet carrier to which the second coupling member is spline-fitted. 6. The vehicle drive device according to claim 4 or 5, wherein an inlay portion for inlay alignment is provided between at least one of the outer diameter surfaces and the inner diameter surface of the planet carrier.   The vehicle drive device according to claim 6, wherein the inlay portion is in a clearance fit rather than an interference fit.

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