WO2017163871A1 - Vehicle drive device - Google Patents

Abstract

The present invention addresses the problem of reducing the radial dimension of a gear device 30 mounted in a vehicle drive device 1. In a vehicle drive device, planetary gear mechanisms 30L, 30R which constitute a gear device 30 for distributing, to left and right wheels, power supplied from two electric motors 2L, 2R have: internally toothed gears R_L, R_R; planetary carriers C_L, C_R provided coaxially with the internally toothed gears R_L, R_R; sun gears S_L, S_R provided coaxially with the internally toothed gears R_L, R_R; and planetary gears P_L, P_R as revolving gears. Externally toothed gears 13a as speed reduction mechanisms are connected to the internally toothed gears R_L, R_R, and the internally toothed gears R_L, R_R are supported by the planetary carriers C_L, C_R through bearings 39. The vehicle drive device is characterized in that a hardened raceway surface of the bearing 39 is formed on at least one of the facing surfaces of the internally toothed gear R_L, R_R and the planetary carrier C_L, C_R.

Description

Vehicle drive device

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 vehicles such as electric cars, 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 wheels, thereby controlling the turning moment of the vehicle It is known to do. When it is effective to generate a large difference in driving torque between the left and right drive wheels in order to achieve smooth turning of the vehicle and to suppress changes in vehicle behavior such as extreme understeer and extreme oversteer There is. For this reason, it is desirable to amplify the difference between the torques output from the two electric motors and transmit them to the left and right drive wheels.

In Patent Document 1 and Patent Document 2, a differential that is a torque difference amplifying mechanism in which two planetary gear structures with three elements and two degrees of freedom are coaxially arranged between two drive sources and left and right drive wheels. A vehicle drive device comprising the device is disclosed.

The vehicle driving device disclosed in FIG. 5A of Patent Document 1 (hereinafter referred to as Conventional Technology 1) has a configuration as shown in the skeleton diagram shown in FIG.

The vehicle drive device 100 includes left and right electric motors 102L and 102R mounted on the vehicle, left drive wheels 104L and right drive wheels 104R, a differential device 105 and reduction gear trains 106L and 106R provided therebetween. , 107L, 107R.

The electric motor 102L and the electric motor 102R operate with electric power from a battery (not shown) mounted on the vehicle, are individually controlled by an electronic control device (not shown), and can generate and output different torques. .

The output shaft 102aL of the electric motor 102L and the output shaft 102aR of the electric motor 102R are connected to the coupling members 111 and 112 of the differential device 105 through the reduction gear trains 106L and 106R, respectively. The output from the differential device 105 is given to the left and right drive wheels 104L, 104R via the reduction gear trains 107L, 107R.

The differential device 105 is configured by combining two identical planetary gear mechanisms 110L and 110R with three elements and two degrees of freedom on the same axis.

As the planetary gear mechanisms 110L and 110R, for example, single-pinion type planetary gear mechanisms are employed. The single-pinion type planetary gear mechanism includes a sun gear S _L , S _R and internal gears R _L , R _R provided on the same axis, and these sun gears S _L , S _R and internal gears R _L , R _R. A plurality of planetary gears P _L and P _R and planetary gears P _L and P _R are rotatably supported, and are provided coaxially with the sun gears S _L and S _R and the internal gears R _L and R _R. was planet carrier C _L, is composed of a C _R, the planetary gear P _L, P _R is engaged the sun gear S _L, S _R and the internal gear R _L, in the R _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.

As shown in FIG. 9, the differential 105 includes a first planetary gear mechanism 110L having a sun gear S _L , a planet carrier C _L , a planetary gear P _L, and an internal gear _RL , as well as a sun gear S _R , a planetary gear. carrier C _R, and a second planetary gear mechanism 110R having a planetary gear P _R and the internal gear R _R is configured by combining coaxially.

Then, the sun gear S _L of the first planetary gear mechanism 110L and the internal gear R _R of the second planetary gear mechanism 110R is coupled by a first coupling member 111, and the internal gear R _L of the first planetary gear mechanism 110L second The sun gear S _R of the planetary gear mechanism 110R is coupled by the second coupling member 112.

The torque TM1 generated by the electric motor 102L is input to the first coupling member 111 via the reduction gear train 106L, and the torque TM2 generated by the electric motor 102R is input to the second coupling member 112 by the reduction gear train 106R. Is input through. Further, the planet carrier C _R of the planetary carrier C _L and the second planetary gear mechanism 110R of the first planetary gear mechanism 110L, respectively reduction gear train 107L, through 107R left and right drive wheels 104L, the output is connected to the 104R It is taken out.

Next, the vehicle drive device disclosed in Patent Document 2 (hereinafter referred to as Conventional Technology 2) has a configuration as shown in the skeleton diagram shown in FIG.

In FIG. 10, in order to make the difference from the prior art 1 easier to understand, the electric motors 102L and 102R are arranged on the left and right to make the same figure as in the prior art 1, and the same components are denoted by the same reference numerals. ing.

As shown in FIG. 10, the vehicle drive device 100 is provided between a first electric motor 102L and a second electric motor 102R mounted on the vehicle, a left drive wheel 104L and a right drive wheel 104R, and these. A differential device 105 and reduction gear trains 106L and 106R are provided.

The first electric motor 102L and the second electric motor 102R operate with electric power from a battery (not shown) mounted on the vehicle, and are individually controlled by an electronic control device (not shown) to generate different torques. Can be output. The output shaft 102aL of the first electric motor 102L and the output shaft 102aR of the second electric motor 102R are connected to the sun gears S _L and S _R of the differential device 105 via reduction gear trains 106L and 106R, respectively. The output from the differential device 105 is given to the left and right drive wheels 104L, 104R.

Like the prior art 1, the differential device 105 of the prior art 2 is configured by combining two identical planetary gear mechanisms 110L and 110R with three elements and two degrees of freedom on the same axis. As the planetary gear mechanisms 110L and 110R, for example, single-pinion type planetary gear mechanisms are employed.

Then, the planet carrier C _L of the first planetary gear mechanism 110L and the internal gear R _R of the second planetary gear mechanism 110R is coupled by a first coupling member 111, the internal gear R _L of the first planetary gear mechanism 110L When the planet carrier C _R of the second planetary gear mechanism 110R is coupled by the second coupling member 112.

The first electric motor 102L torque TM1 generated in is input to the sun gear S _L of the first planetary gear mechanism 110L via a reduction gear train 106L, torque TM2 generated by the second electric motor 102R is decelerated It is input to the sun gear S _R of the second planetary gear mechanism 110R through a gear train 106R.

Also, the first coupling member 111 and the second coupling member 112 are connected to the left and right drive wheels 104L and 104R, respectively, and outputs are taken out.

In the prior art 2, the electric motor 102L, input from 102R, the sun gear S _L, the sun gear S _R, and the drive wheels 104L, output to 104R, the carrier C _L and the internal gear R _R, and the carrier C _R It becomes an internal gear R _L.

As described above, in the conventional techniques 1 and 2 described above, when the two electric motors 102 </ b> L and 102 </ b> R generate different torques TM <b> 1 and TM <b> 2 and give the input torque difference ΔTIN, the input is performed in the differential device 105. The torque difference ΔTIN is amplified, and a driving torque difference ΔTOUT larger than the input torque difference ΔTIN can be obtained.

In the prior art 1 and the prior art 2, since the torque difference is amplified by connecting the internal gears R _L and R _R constituting the two planetary gear mechanisms and the coupling member, either the right or left inner gear is used. Since one of the coupling members that connect the gears R _L and R _R to another member always has a larger diameter than the other internal gears R _L and R _R , there is a problem that the apparatus becomes large.

For this reason, 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 amplifies the torque difference between the prior art 1 and the prior art 2 (Japanese Patent Application No. 2016- No. 023529).

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

A planetary gear mechanism 300L constituting the gear device 300 in the vehicle driving apparatus 201 of Sakinegairei 1, 300R, respectively internal gear R _L, and R _R, the internal gear R _L, planet carrier provided on R _R coaxial a C _L, and C _R, the internal gear R _L, the sun gear provided on R _R coaxial S _L, and S _R, the planetary gear 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 231 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 232, the first coupling member 231 and the second coupling member 232 are arranged coaxially, and among the first coupling member 231 and the second coupling member 232, the second coupling member 232 is a hollow shaft, The coupling member 231 has a shaft inserted through the hollow shaft, and the shaft passing between the two planetary gear mechanisms 300L and 300R has a double structure, and the internal gear R _{L of the} planetary gear mechanisms 300L and 300R. , R _R and the input gear 213 of the speed reduction mechanism are engaged with and connected to external gears 217 provided on the internal gears R _L , R _R.

Also, Patent Document 3 discloses a vehicle drive device (prior art 3) provided with a differential device that is a torque difference amplification mechanism.

As shown in the skeleton diagram of FIG. 13, the vehicle drive device of Prior Art 3 includes first and second drive sources M 1 and M 2, left and right drive wheels WL and WR, both drive sources M 1 and M 2, A differential device 302 interposed between the drive wheels WL and WR. The differential device 302 includes a continuous pinion 320 having a plurality of planetary gears connected to one shaft, and a continuous pinion. The rotating mechanism includes sun gears 324 and 325 that mesh with the planetary gears 321 and 322 of 320, a carrier 323 that pivotally supports the continuous pinion 320, and an internal gear 327 that meshes with the planetary gear 322 of the continuous pinion 320. . A drive source M1, a drive source M2, and left and right drive wheels WL, WR are connected to the differential device 302. The drive source M1 is connected to the internal gear 327 via the hollow shaft 311, and the drive source M2 is connected to the hollow shaft 312. Are connected to the second sun gear 325, the left driving wheel WL is connected to the carrier 323 via the shaft 313L, and the right driving wheel WR is connected to the first sun gear 324 via the shaft 313R.

JP 2015-21594 A Japanese Patent No. 4907390 JP 2011-237019 A

By the way, in each of the differential gears that are the torque difference amplification mechanism, two planetary gear mechanisms are coaxially combined.

Between the internal gears R _L , R _R and the planet carriers C _L , C _R which are the rotating elements of the two planetary gear mechanisms, a bearing for supporting the rotation is required.

In the prior arts 1 to 3, no specific example of a bearing that supports rotation is shown, but in the prior application example 1, as shown in FIGS. 11 and 12, a deep groove ball bearing is used as this bearing. .

That is, the deep groove ball bearing 220 is disposed between the internal gears R _L and R _R and the planetary carriers C _L and C _R.

The deep groove ball bearing 220 includes an inner ring 220a, a rolling element 220b, and an outer ring 220c. The bearing elements such as the inner ring 220a, the rolling element 220b, and the outer ring 220c are arranged between the inner gears R _L and R _R and the planetary carriers C _L and C _R. Since it is necessary to arrange them, the radial dimension increases by the thickness of the inner ring 220a and the outer ring 220c.

Since the vehicle drive device is mounted on the vehicle body, it is advantageous to reduce the mounting space and secure a wide cabin space, and it is essential to reduce the size and weight of the gear device that amplifies the torque difference.

Therefore, an object of the present invention is to reduce the size in the radial direction of a torque difference amplification mechanism incorporated in a vehicle drive device.

In order to solve the above-described problems, the present invention provides a three-element and two-degree-of-freedom planetary gear mechanism coaxially between two drive sources mounted on a vehicle and independently controllable and left and right drive wheels. Two combinations, a specific element of one planetary gear mechanism and a specific element of the other planetary gear mechanism are connected to each other by a first coupling member and a second coupling member to drive left and right from two driving sources. A differential device for amplifying and outputting a torque difference is provided on the ring, and the planetary gear mechanism is provided with an internal gear, a planet carrier provided coaxially with the internal gear, and provided coaxially with the internal gear. A vehicle drive device having a sun gear and a planetary gear as a revolving gear, an external gear as a speed reduction mechanism connected to the internal gear, and the internal gear supported by the planet carrier via a bearing The opposing surface of the internal gear and the planet carrier On at least one side, characterized in that the formation of the raceway surface of the bearing that is hardened.

The bearing surface of the hardened bearing may be formed on the inner diameter surface of the internal gear, or the raceway surface of the hardened bearing may be formed on the outer diameter surface of the planet carrier.

The material of the internal gear or planetary carrier is case-hardened steel, and the raceway surface of the bearing can be formed by carburizing and quenching.

Further, the material of the internal gear or planet carrier may be medium carbon steel, and the raceway surface of the bearing may be formed by induction hardening.

The teeth of the internal gear may also be induction hardened.

The bearing can be a deep groove ball bearing, and the cage of the deep groove ball bearing can be a resin crown.

A cylindrical roller bearing with a cage may be used as the bearing, and a thrust washer may be disposed near the outer end of the raceway surface.

As the bearing, a slide bearing may be used, and a stepped portion for arranging the slide bearing on the raceway surface may be provided.

As described above, according to the present invention, at least one of the outer ring and the inner ring is formed by directly forming the hardened raceway surface of the bearing on at least one of the opposing surfaces of the inner gear and the planetary carrier. Since it can be omitted, the radial dimension can be reduced by the thickness of the inner ring or the outer ring.

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 an enlarged view which shows other embodiment of the gear apparatus enclosed with the dashed-two dotted line of FIG. It is an enlarged view which shows other embodiment of the gear apparatus enclosed with the dashed-two dotted line of FIG. It is an enlarged view which shows other embodiment of the gear apparatus enclosed with the dashed-two dotted line of FIG. FIG. 5 is an enlarged view showing another embodiment of the gear device surrounded by a two-dot chain line in FIG. 1. FIG. 6B is a partially enlarged view of the plain bearing taken along line bb in FIG. 6A. 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 skeleton figure which shows the gear structure of the vehicle drive device which concerns on the prior art 1. FIG. It is a skeleton figure which shows the gear structure of the vehicle drive device which concerns on the prior art 2. FIG. It is a cross-sectional top view which shows embodiment of the vehicle drive device which concerns on the prior application example 1. FIG. FIG. 4 is an enlarged view of a gear device portion of Prior Application Example 1. FIG. 10 is a skeleton diagram showing a gear configuration of a vehicle drive device according to Prior Art 3.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

The electric vehicle AM shown in FIG. 7 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 are provided. In FIG. 7, the gear structure of the vehicle drive device 1 is shown with the skeleton figure.

A vehicle drive device 1 shown in FIG. 1 includes two electric motors 2L and 2R that are mounted on a vehicle and can be controlled independently, and left and right drive wheels 61L and 61R and two electric motors 2L and 2R. 2 left and right reduction gears 3L and 3R provided between them.

The driving 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.

In addition, as a mounting form of the two-motor type vehicle drive device 1, a front wheel drive system or a four wheel drive system may be used in addition to the rear wheel drive system shown in FIG. In the four-wheel drive system, the vehicle drive device shown in FIG. 1 may be mounted on both the front wheels or the rear wheels, or may be mounted on one of them, and the other may be another device such as an engine-driven gear device. It may be a drive device.

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

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 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 main body 4 aL and 4 aR, and a rotor 5 is provided with a gap in 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 periphery 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 bodies 4aL and 4aR (see FIG. 1). In FIG. 1, the bearings 8a and 8b are the same, but different sizes may be combined.

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 (see FIG. 1).

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

As shown in FIG. 1, the reduction gears 3L and 3R are provided symmetrically and have large input gear shafts 12L and 12R having an input gear 12a to which power is transmitted from the motor shaft 5a, and the input gear 12a. Intermediate gear shafts 13L and 13R having both an output side small gear 13b meshing with an input side external gear 13a and an output gear 14a, and an output gear 14a. The constant velocity joint 65a is pulled out from the speed reducer housing 9. 65 is a parallel shaft gear reducer including output gear shafts 14L and 14R that transmit torque to drive wheels 61L and 61R (see FIG. 7) via an intermediate shaft 65c (see FIG. 7). 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 and 12R of the reduction gears 3L and 3R are respectively connected to bearing fitting holes 16a formed on both left and right sides of the partition wall 11 of the central housing 9a and bearing fitting holes 16b formed on the side housings 9bL and 9bR. It is rotatably supported via rolling bearings 17a and 17b. 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. In FIG. 1, the rolling bearings 17a and 17b are the same, but they may be combined in different sizes.

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 coupled by splines (including serrations, the same applies hereinafter).

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 external gear 13a meshing with the input gear 12a on the outer peripheral surface and an output side small gear 13b meshing with the output gear 14a. 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 with a wall portion with which the outer rings of the rolling bearings 20a and 20b come into contact. The bearing fitting hole 19a has a first coupling member 31 and a second coupling which will be described later. It penetrates so that member 32 may pass. In FIG. 1, the rolling bearings 20a and 20b have different sizes, but they may be combined with each other.

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 device 30 is composed of two planetary gear mechanisms 30L and 30R with three elements and two degrees of freedom, which are coaxially combined with a pair of left and right intermediate gear shafts 13L and 13R arranged coaxially.

The planetary gear mechanisms 30L and 30R constituting the gear device 30 include internal gears R _L and R _R and internal gears R _L and R _R incorporated in the large-diameter input side external gear 13a of the intermediate gear shafts 13L and 13R, respectively. A plurality of planetary gears P _L arranged equally in the circumferential direction as revolving gears meshed with the sun gears S _L , S _R and the internal gears R _L , R _R and the sun gears S _L , S _R provided coaxially with each other. , P _R and the planetary gears P _L, the P _R rotatably supported internal gear R _L, planetary provided on R _R coaxial carrier C _L, C _R and, one of the planet carrier C _L ( In FIG. 1, a first coupling member 31 that couples the other sun gear S _R (the right side of the figure in FIG. 1) with one sun gear S _L (the left side of the figure in FIG. 1) and the other sun gear S _R a planet carrier C _R second coupling member 32 for coupling the (right side in FIG. in FIG. 1), the internal gear R _L, linked to R _R, oN An input side external gear 13a of the intermediate gear shafts 13L and 13R meshing with the input gear 12a of the gear shafts 12L and 12R, and an output side small gear 13b of the intermediate gear shafts 13L and 13R meshing with the output gear 14a of the output gear shafts 14L and 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.

When a plurality of pairs of intermediate gear shafts 13L and 13R are provided, the planetary gear mechanisms 30L and 30R constituting the gear device 30 are incorporated only in any one of the pair of intermediate gear shafts 13L and 13R. The input-side external gear 13a connected to the internal gears R _L , R _R is an output-side small gear 13b provided on the drive-side intermediate gear shafts 13L, 13R among the plural pairs of intermediate gear shafts 13L, 13R, or An output-side small-diameter gear 13b that is arranged so as to mesh with the input gear 12a of the input gear shafts 12L and 12R and is coaxial with the planetary gear mechanisms 30L and 30R is formed of a plurality of pairs of intermediate gear shafts 13L and 13R. Are arranged so as to mesh with the input side external gear 13a provided on the driven intermediate gear shafts 13L, 13R or the output gear 14a of the output gear shafts 14L, 14R.

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 carrier flange that is connected to the outboard side end of the carrier pin 33. 34a and an inboard 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. It is supported by the fitting hole 19b via the rolling bearing 20b (refer FIG. 1).

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. It is supported by 19a via the rolling bearing 20a (refer FIG. 1).

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.

The planetary gears P _L and P _R are supported by the carrier pin 33 via the needle roller bearing 37.

Here, each of the carrier flanges 34a, 34b facing surface and a planetary gear P _L of, inserting the thrust plate (not shown) between the P _R, the planetary gear P _L, even working to smooth rotation of the P _R Good.

A bearing 39 is disposed between the outer peripheral surfaces of the carrier flanges 34a and 34b and the internal gears R _L and R _R.

In the embodiment shown in FIGS. 1 and 2, a deep groove ball bearing is adopted as the bearing 39 for supporting the internal gears R _L and R _R on the carrier flanges 34a and 34b. The deep groove ball bearing includes an outer ring 39a, an inner ring 39b, and a rolling element 39c. In the embodiment shown in FIGS. 1 and 2, the raceway surface of the outer ring 39a is used as the inner diameter surface of the internal gears R _L and R _R. Formed directly.

By forming the raceway surface of the outer ring 39a directly on the inner diameter surface of the inner gears R _L and R _R , the outer ring 39a has a thickness corresponding to the thickness of the outer ring than when the outer ring of a separate part is incorporated in the inner diameter surface of the inner gears R _L and R _R The radial dimension can be reduced.

As the gears such as the internal gears R _L and R _R , in general, a case-hardened steel that has been subjected to surface hardening and quenching is used in order to sufficiently secure the tooth surface strength and tooth root strength of the teeth. On the other hand, bearings that support the rotation of gears also need to withstand high surface pressure generated on the rolling elements and raceways by the load.For example, high-carbon chromium alloy steel that has been subjected to core quenching or surface-hardened steel Hardened and hardened. That is, both the gear and the bearing need to have sufficient hardness (for example, a surface hardness of 58 HRC or more) by quenching.

In the embodiment of FIGS. 1 and 2, the internal gears R _L and R _R are, for example, case-hardened steel, and carburized and quenched as a heat treatment, and the surface hardness of the tooth portion and the bearing raceway surface is It is secured at 58HRC or higher.

In the embodiment shown in FIG. 3, a deep groove ball bearing is adopted as the bearing 39 for supporting the internal gears R _L and R _R on the carrier flanges 34a and 34b, as in the embodiment shown in FIGS. In the embodiment shown in FIG. 3, the raceway surface corresponding to the inner ring 39b of the bearing is formed directly on the outer diameter surfaces of the carrier flanges 34a and 34b.

The planetary carriers C _L and C _R provided with the carrier flanges 34a and 34b are, for example, medium carbon steel, and the bearing raceway surface is subjected to induction hardening as a heat treatment, and the surface hardness is secured to 58 HRC or more. Yes. The teeth of the output-side small-diameter gear 13b formed on the planetary carriers C _L and C _R are also heat-treated in the same manner. A portion to be induction-hardened is indicated by a thick dashed line in FIG.

In FIGS. 1 to 3, the rolling bearing 39 is the same on the outboard side and the inboard side, but a combination of different forms may be used. That is, the bearing on the outboard side directly forms the raceway surface of the outer ring 39a on the inner diameter surface of the internal gears R _L and R _R as shown in FIGS. 1 and 2, and the bearing on the inboard side is the inner ring 39a as shown in FIG. The raceway surface may be formed directly on the outer diameter surface of the carrier flanges 34a, 34b. Similarly, the bearing on the inboard side directly forms the raceway surface of the outer ring 39a on the inner diameter surface of the internal gears R _L and R _R , and the bearing on the outboard side forms the raceway surface of the inner ring 39a on the carrier flanges 34a and 34b. You may form directly on an outer diameter surface. The size of the bearing may be different between the bearing on the outboard side and the bearing on the inboard side.

Next, the embodiment shown in FIG. 4 employs a cylindrical roller bearing with a cage as the bearing 39 for supporting the internal gears R _L and R _R on the carrier flanges 34a and 34b.

In the embodiment shown in FIG. 4, the raceway surface of the outer ring 39a is an internal gear R _L, are directly formed on the inner diameter surface of the R _R, further, the raceway surface of the inner ring 39b is also directly formed on the outer peripheral surface of the carrier flange 34a, 34b Has been. A step is provided at the inner end of the raceway surface of the outer ring 39a to restrict the rolling element 39c from moving. A thrust ring 39d is provided in the vicinity of the outside of the raceway surface of the inner ring 39b. The thrust ring 39d is regulated so as not to drop off by a retaining ring 39e provided further outside. As a result, the rolling element 39c is restricted from moving in the axial direction by the step and the thrust ring 39d, and is prevented from falling off the bearing 39.

The embodiment shown in FIG. 5 employs a deep groove ball bearing as the bearing 39 for supporting the internal gears R _L and R _R on the carrier flanges 34a and 34b as in the embodiment shown in FIGS. In the embodiment shown in FIG. 1 and FIG. 2, the bearings 39 are provided on both the outboard side and the inboard side. On the other hand, in the embodiment shown in FIG. The cantilever is supported only by the bearing 39 on the board side.

In the embodiment shown in FIG. 5, the raceway surface of the outer ring 39a is formed directly on the inner diameter surface of the internal gears R _L and R _R , and the raceway surface of the inner ring 39b is formed on the carrier flange 34b on the inboard side. It is formed directly on the outer peripheral surface.

Further, in the embodiment of FIG. 5, the bearings 39 are provided in a single row, but may be in a double row (not shown). As the bearing 39 of the embodiment of FIG. 5, a cylindrical roller bearing can be adopted as in the embodiment shown in FIG.

Further, in the embodiment of FIG. 5, the outboard side bearing 39 is abolished and is cantilevered only by the inboard side bearing 39, but the inboard side bearing 39 is abolished and the outboard side bearing 39 is supported. You may make it cantilever-support only by 39 (illustration omitted).

Next, the embodiment shown in FIG. 6AB employs a plain bearing as the bearing 39 for supporting the internal gears R _L and R _R on the carrier flanges 34a and 34b.

In the embodiment shown in FIG. 6AB, the sliding bearing is attached by fitting to the stepped portion provided on the outer peripheral surface of the carrier flanges 34a, 34b, and the sliding surface of the sliding bearing is attached to the inner diameter surface of the internal gears R _L , R _R. Is formed directly. The sliding surfaces of the inner diameter surfaces of the internal gears R _L and R _R are secured by heat treatment.

As shown in the partial enlarged view of FIG. 6B, axial and circumferential oil grooves 39f are formed on the outer peripheral surface of the slide bearing so that lubricating oil can be supplied to the sliding surface.

In each of the embodiments, the collar 40 is disposed between the inboard carrier flange 34b and the rolling bearing 20a that supports the hollow shaft portion 36 of the inboard carrier flange 34b.

Next, in each of the above-described embodiments, the first coupling member 31 and the second coupling member 32 that couple the two planetary gear mechanisms 30L and 30R that constitute the gear device 30 of the vehicle drive device 1 are the speed reducer housing 9. The central housing 9a is incorporated through the partition wall 11 that partitions the left and right.

The first coupling member 31 and the second coupling member 32 are arranged coaxially, and one coupling member (the second coupling member 32 in each embodiment of FIGS. 1 to 6) is a hollow shaft and the other coupling The member (the first coupling member 31 in each embodiment of FIGS. 1 to 6) has a double structure composed of a shaft inserted through the hollow shaft.

The above in each embodiment, the end portion of the right side of the planetary gear mechanism 30R side in the second coupling member 32 consists of a hollow shaft, and the hollow shaft portion 36 of the carrier flange 34b on the inboard side of the planet carrier C _R the spline 41 is provided, it is connected by spline fitting to the second coupling member 32 the planet carrier C _R.

In each embodiment, the end portion of the left planetary gear mechanism 30L side 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 from the left and right in the same manner as other reduction gear shafts.

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, which (in each embodiment the coupling member 31) coupling members on the inner diameter side are connected with the outer diameter side coupling member by (in the embodiments in which the second coupling 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 for mating is the inner diameter side It is possible to easily incorporate the coupling member (the first coupling member 31 in each embodiment).

A collar 44 and a collar 44 are provided between the outer peripheral surface of the inner diameter side coupling member (first coupling member 31 in each embodiment) and the inner peripheral surface of the outer diameter side coupling member (second coupling member 32). Needle roller bearings 45 and 46 are interposed at both ends.

The first coupling member 31 and the second coupling member 32 and the planetary carriers C _L and C _R are fitted (splines 42 and 41) with a fitting tolerance that can be slid in the axial direction. large diameter of the input-side external gear 13a meshing with this, the output gear 14a and the output-side small-diameter external gear 13b meshing with this sun gear S _L, S _R and the planetary gears P _L, P _R and the internal gear R _L, the R _R Even if at least one of the meshes has a helical gear and an axial load is generated, it is possible to prevent an uneven load on the gear tooth surface.

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 movement of the spline (splines 42 and 41) is caused by the outer diameter side coupling member (each implementation). In the embodiment, the load is supported by providing thrust bearings 47 and 48 at both ends of the second coupling member 32).

The coupling member (the first coupling member 31 in each embodiment) on the inner diameter side of the dual-structure shaft that couples the two planetary gear mechanisms 30L and 30R is a coupling member (the first coupling member 31 in each embodiment) and the planet. the spline fitting opposite axial end of the carrier (C _L in the embodiment), and supported by a deep groove ball bearing 49 relative to (C _R in the embodiments) other planet carrier.

The coupling member (the first coupling member 31 in each embodiment) on the inner diameter side of the double-structure shaft that couples the two planetary gear mechanisms 30L and 30R includes the tooth surfaces of the sun gears S _L and S _R , the planetary gear P _L, the tooth surfaces of the P _R, in order to supply the lubricating oil, etc, is provided an oil supply hole 50 to the axis. In the oil supply hole 50 of the inner diameter side coupling member (first coupling member 31 in each embodiment), the thrust bearings 47 and 48 at both ends of the outer diameter side coupling member (second coupling member 32 in each embodiment) are positioned. Radial oil supply passages 51 and 52 are provided.

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. In FIG. 1, the rolling bearings 54a and 54b are the same, but they may be combined in different sizes.

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 (see FIG. 7).

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 type vehicle drive device 1 of the embodiment shown in FIG. 1 is as shown in the skeleton diagram shown in FIG.

As shown in FIG. 7, the left and right electric motors 2 </ b> L and 2 </ b> R are operated by electric power supplied via an inverter 64 from a battery 63 mounted on the vehicle. 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 is 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 large-diameter input side external 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 planetary gear mechanisms 30L and 30R having the same three-element and two-degree-of-freedom with coaxial intermediate gear shafts 13L and 13R. The planetary gear mechanisms 30L and 30R are of a single pinion type. A planetary gear mechanism is used.

The planetary gear mechanisms 30L and 30R 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 30L, 30R, when the planet carriers C _L , C _R are fixed, the sun gears S _L , S _R and the internal gears R _L , 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 30L having the sun gear S _L , the planet carrier C _L , the planet gear P _L and the internal gear _RL , and 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, coupled with the planet carrier C _L of the first planetary gear mechanism 30L and the sun gear S _R of the second planetary gear mechanism 30R form a first coupling member 31, the sun of the first planetary gear mechanism 30L a planet carrier C _R gear S _L and the second planetary gear mechanism 30R form a second coupling member 32 are coupled.

Here, the torque TM1 generated by the electric motor 2L is transmitted to the intermediate gear shaft 13L by meshing the input gear 12a of the input gear shaft 12L and the input side external gear 13a, and the torque transmitted to the intermediate gear shaft 13L is It is transmitted to the output-side small gear 13b of the intermediate gear shaft 13L via the first 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 are engaged with each other to produce an output gear shaft. Drive torque TR is output from 14L to drive wheel 61L.

The torque TM2 generated by the electric motor 2R is transmitted to the intermediate gear shaft 13R when the input gear 12a of the input gear shaft 12R and the input side external gear 13a are meshed, and the torque transmitted to the intermediate gear shaft 13R is the second torque. It is transmitted to the output-side small gear 13b of the intermediate gear shaft 13R via the planetary 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.

The outputs from the electric motors 2L and 2R are also given to the internal gears R _L and R _R of the two planetary gear mechanisms 30L and 30R, respectively, and the outputs from the first coupling member 31 and the second coupling member 32 are drive wheels. It is given to 61L and 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 has one end a rotation shaft of the (right end in the drawing) is the sun gear S _R, the other end (left end in the drawing) are provided through the sun gear S _L, connected to the planet carrier C _L Has been. 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 30L and 30R are coupled by the first coupling member 31 and the second coupling member 32.

Next, since the gear unit 30 is configured by combining two identical single pinion type planetary gear mechanisms 30L and 30R, it 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 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, in the embodiment of FIG. 1, the torques TM1 and TM2 output from the electric motors 2L and 2R are respectively connected to the internal gears via the input side external gears 13a meshing with the input gears 12a of the input gear shafts 12L and 12R. Since it is input to R _L and R _R , a reduction ratio is applied, and the drive torques TL and TR taken out from the gear device 30 are applied to the left and right drive wheels 61L and 61R via the output-side small gear 13b that meshes with the output gear 14a. Because it is transmitted to, a reduction ratio is applied. Here, for easy understanding, hereinafter, in the description of the velocity diagram and each calculation formula shown in FIG. 8, the reduction ratio is omitted, and the torque input to each of the internal gears R _L and R _R is TM1 and TM2. The drive torque remains TL and TR, and the drive torque extracted from the gear device 30 remains TL and TR.

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 R in the speed diagram. the distance between the _R and the planet carrier C _R are equal, which is referred to as 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, it can be expressed as a = (1 / Zr), 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. 8, the arrow direction M in the figure is the positive direction of the moment.
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 sum of the formulas (1) and (2).
-B. (TR-TL) + (2a + b). (TM2-TM1) = 0
(TR-TL) = ((2a + b) / b). (TM2-TM1) (3)

(2a + b) / b in the expression (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 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 and the carrier C _L , and the sun gear S _L and the carrier C _R Become.

When different torques TM1 and TM2 are generated by the two electric motors 2L and 2R to give an input torque difference ΔTIN (= (TM2−TM1)), the gear device 30 amplifies the input torque difference ΔTIN, 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)) larger than the input torque difference ΔTIN can be given to the driving torques TL and TR transmitted to 61R.

In the prior art 1 and the prior art 2, since the internal gear R is included in the left and right connecting members of the two planetary gear mechanisms of the gear device 105 that is the torque difference amplifying mechanism, the coupling that connects either the left or right internal gear and another member. One of the members must have a larger diameter than the other internal gear R.

In contrast, in the embodiment of the present invention, the torque difference distributing mechanism is a gear unit 30 two planetary gear mechanism 30L which constitutes the connection of 30R the sun gear S _L and the planet carrier C _R, the sun gear S _R And the planetary carrier C _L , a connecting member having a larger diameter than the internal gears R _L and R _R is not 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 can be made smaller and lighter. Can be

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

In addition, there is a merit that the vehicle interior space is expanded by reducing the size of the vehicle drive device 1.

In the embodiment shown in FIG. 1, the case where the electric motors 2L and 2R are used as the two drive sources and the electric motors have the same maximum output and the same output characteristics is illustrated, but the two drive sources are not limited to this. I can't.

The vehicle on which the vehicle drive device 1 is mounted is not limited to an electric vehicle or a hybrid electric vehicle, but 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 embodiment described above, and can be implemented in various forms without departing from the gist of the present invention.

1: Vehicle drive device 2L, 2R: Electric motor 3L, 3R: Deceleration device 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: Sealing members 8a and 8b: Rolling bearing 9: Reduction gear housing 9a: Central housing 9bL and 9bR: Side housing 10: Bolt 11: Partition walls 12L and 12R: Input gear shaft 12a: Input gear shafts 13L and 13R: Intermediate Gear shaft 13a: Input side external gear 13b: Output side small diameter gears 14L, 14R: Output gear shaft 14a: Output gears 16a, 16b: Bearing fitting holes 17a, 17b: Rolling bearing 18: Oil seals 19a, 19b: Bearing fitting Hole 20a, 20b: Rolling bearing 30 : Gear units 30L, 30R: planetary gear mechanism 31: first coupling member 32: second coupling member 33: carrier pins 34a, 34b: carrier flanges 35, 36: hollow shaft portion 37: bearing 39: bearing 39a: outer ring 39b: Inner ring 39c: rolling element 39d: thrust ring 39e: retaining ring 39f: oil groove 40: collar 41, 42: spline 43: large diameter portion 44: collar 45, 46: bearing 47, 48: thrust bearing 49: deep groove ball bearing 50 : Oil supply holes 51, 52: Oil supply passages 53a, 53b: Bearing fitting holes 54a, 54b: Rolling bearing 55: Oil seal 60: Chassis 61L, 61R: Drive wheels 62L, 62R: Front wheels 63: Battery 64: Inverters 65a, 65b : Constant velocity joint 65c: Intermediate shaft AM Electric vehicle C _L, C _R: planet carrier M: Moment P _L, P _R: planetary gear _{R L,} R R: internal gear S _L, S _R: sun gear TM1, TM2: torque TL, TR generated by the electric motor : Drive torque Zr: Number of teeth of internal gear Zs: Number of teeth of sun gear a, b: Distance α: Torque difference amplification factor ΔTIN: Input torque difference ΔTOUT: Drive torque difference

Claims (11)

1. Two planetary gear mechanisms with three elements and two degrees of freedom are coaxially combined between two drive sources mounted on the vehicle and independently controllable and the left and right drive wheels, and specific elements of one planetary gear mechanism And a specific element of the other planetary gear mechanism by a first coupling member and a second coupling member to amplify a torque difference from two drive sources to the left and right drive wheels and output the gear device 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 planetary gear as a revolving gear. In the vehicle drive device in which an external gear as a speed reduction mechanism is connected to the internal gear, and the internal gear is supported via a bearing with respect to the planet carrier, at least one of the opposing surfaces of the internal gear and the planet carrier On the surface of the hardened said Vehicle driving apparatus characterized by forming the raceway surface of the receiving.
2. 2. The vehicle drive device according to claim 1, wherein a raceway surface of the hardened bearing is formed on an inner diameter surface of the internal gear.
3. 2. The vehicle drive device according to claim 1, wherein a raceway surface of the hardened bearing is formed on an outer diameter surface of the planetary carrier.
4. The vehicle drive device according to any one of claims 1 to 3, wherein a material of the internal gear or the planetary carrier is case-hardened steel and has a raceway surface of the carburized and quenched.
5. The vehicle drive device according to any one of claims 1 to 3, wherein a material of the internal gear or the planet carrier is medium carbon steel and has a raceway surface of the bearing that is induction-hardened.
6. The vehicle drive device according to claim 5, wherein the teeth of the internal gear are also induction-hardened.
7. The vehicle drive device according to any one of claims 1 to 6, wherein the bearing is a deep groove ball bearing.
8. The vehicle drive device according to claim 7, wherein the cage of the deep groove ball bearing is a resin crown type.
9. The vehicle drive device according to any one of claims 1 to 6, wherein the bearing is a cylindrical roller bearing with a cage.
10. The vehicle drive device according to claim 9, wherein a thrust washer is disposed in the vicinity of an outer end portion of the track surface.
11. The vehicle drive device according to any one of claims 1 to 6, wherein the bearing is a slide bearing, and a step portion for arranging the slide bearing is provided on the bearing ring.

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