JP2018048685A - Planetary gear device and driving device for vehicle using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To elongate a service life of needle roller bearings 37 by improving supply of a lubricant to the needle roller bearings 37 by guiding the lubricant reaching outer peripheral faces of thrust plates 38 mounted on side faces of planetary gears P, P, into the needle roller bearings 37 rotatably supporting the planetary gears P, P.SOLUTION: The outer peripheral shape of each of thrust plates 38 is the shape formed by combining a large-diameter portion positioned at an outer diameter side with respect to an outer diameter raceway surface 37b of the needle roller bearing 37 disposed on a gear supporting shaft 33, and sliding between width surfaces of the planetary gears P, Pand carrier flanges 34a, 34b in a contact manner, and a small-diameter portion positioned at an inner diameter side with respect to the outer diameter raceway surface 37b of the needle roller bearing 37 disposed on the gear supporting shaft 33. A communication portion 38b communicated to an accommodation space of the needle roller bearing 37, is disposed between the small diameter portion of the thrust plate 38 positioned at an inner diameter side with respect to the outer diameter raceway surface 37b of the needle roller bearing 37 and the outer diameter raceway surface 37b of the needle roller bearing 37.SELECTED DRAWING: Figure 11

Description

  The present invention relates to a planetary gear device used for a reduction gear of a vehicle drive device, and more particularly to a planetary gear device that improves the supply of lubricating oil to a needle roller bearing that supports the planetary gear and extends the life of the needle roller bearing. It is about.

  As a planetary gear device used for a reduction gear of various rotary drive devices for vehicles and the like, for example, there is one disclosed in Patent Document 1.

  As shown in FIG. 23, the planetary gear device of Patent Document 1 includes an internal gear R, a sun gear S provided coaxially with the internal gear R, and a planetary gear as a revolving gear meshing with the internal gear R and the sun gear S. It consists of a gear P and a planet carrier C provided coaxially with the internal gear R.

  Further, Patent Document 2 and Patent Document 3 include a gear device in which two planetary gear devices having three elements and two degrees of freedom are coaxially arranged between two drive sources and left and right drive wheels. There is disclosed a vehicle drive device that can amplify a difference in torque applied from a drive source and apply the amplified difference to left and right drive wheels.

  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 in Patent Document 2 and Patent Document 3 (Japanese Patent Application No. 2006-023529). ).

  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.

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 for driving 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 rotation 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 and the internal gears R _L and R _R rotate relative to each other. The planetary gears P _L and P _R rotate and revolve.

Utility Model Registration No. 2507561 JP 2015-21594 A Japanese Patent No. 4907390 JP 2008-88993 A JP 2000-337484 A

Meanwhile, the planetary gear unit 210L, 210R, as shown in FIGS. 24 and 25, the planetary gears P _L, via a needle roller bearing 220 in gear support shaft 218 in the center of the P _R, the planetary gear P _L and P _R are rotatably supported. Both ends of the gear support shaft 218 are inserted and fixed to a pair of carrier flanges 221 of the planetary carriers C _L and C _R.

Between the pair of carrier flanges 221 and the planetary gears P _L and P _R , a gear support shaft 218 as shown in FIGS. 26 and 27 is provided inside to facilitate the rotation of the planetary gears P _L and P _R. A thrust plate 222 passing through is attached.

As shown in FIG. 27, the needle roller bearing 220 that rotatably supports the planetary gears P _L and P _R with respect to the gear support shaft 218 is an inner ring raceway surface 220a constituted by the outer diameter surface of the gear support shaft 218. When the planetary gears P _L, and the outer ring raceway surface 220b formed by the radially inner surface of the P _R, and a plurality of needle rollers 220c that are accommodated between the inner ring raceway surface 220a and the outer ring raceway surface 220b, a plurality of It comprises a retainer 220d that holds the needle rollers 220c at equal intervals.

As shown in FIGS. 26 and 27, the thrust plate 222 is formed in a ring shape having a through hole 223 through which the gear support shaft 218 passes, and the outer diameter of the thrust plate 222 is a planet constituting the outer ring raceway surface 220b. gear P _L, is larger than the inner diameter surface of the P _R, the thrust plate 222 is in sliding contact between the width surface and the planetary gears P _L, the width surface of the P _R of the carrier flange 221.

  FIG. 27 shows a part of the thrust plate 222 cut out so that the needle rollers 220c, the cage 220d, and the outer ring raceway surface 220b hidden in the thrust plate 222 can be seen.

  By the way, in the planetary gear devices 210L and 210R used in the vehicle drive device 200 of the prior application example 1, a part of the gears of the planetary gear devices 210L and 210R or parallel to the gear tooth surfaces and the rolling bearings are lubricated. The oil level is set so that part of the gear of the shaft gear reducer is immersed in the lubricating oil stored in the lower part of the reducer, and oil bath lubrication and splash lubrication by gear rotation are performed.

However, as in the vehicle driving apparatus 200 of Sakinegairei 1, two planetary gear 210L, the gear 300 coupled coaxially in the 210R, the interior of the planetary gear when the vehicle is stopped P _L, the P _R Even if the oil surface height is set so that the gear support shaft 218 is immersed in the lubricating oil, the internal gears R _L and R _{R of the} gear device 300 also rotate as large gears of the intermediate gear shaft, so the rotating internal gear R _L, R _R is cause to wade through the lubricant oil pooled in the bottom of the reducer housing, in particular, during high-speed running of the vehicle in the state in which the planetary gears P _L, the gear support shaft 218 of the P _R is not Hitakara the lubricant Become.

Further, the thrust plate 222 positioned between the planet gears P _L, P _R and the carrier flange 221 for holding the planetary gears P _L, the P _R in a predetermined axial extent, the planetary gear P _L, P _R and the carrier The clearance with the flange 221 is small.

Further, the planetary gear P _L, to hold uniform the P _R, as shown in FIGS. 26 and 27, the thrust plate 222 has a circular shape, the outer diameter of the thrust plate 222, the outer ring raceway surface 220b The planetary gears P _L and P _R that are formed are larger than the inner diameter surfaces of the planetary gears P _L and P _R , and the thrust plate 222 blocks the accommodation space of the needle rollers 220 c between the outer ring raceway surface 220 b and the inner ring raceway surface 220 a in the needle roller bearing 220. It is peeling off.

Therefore, the internal gear R _L, R _R and planet carrier C _L, C _R is a planetary gear unit for rotation therewith 210L, oil bath lubrication and splashing lubrication 210R, needle rollers for supporting the planetary gears P _L, the P _R Lubricating oil is difficult to be supplied to the housing space of the bearing 220, and the needle roller bearing 220 may be damaged early due to poor lubrication.

  Conventionally, in a planetary gear device, Patent Document 4 discloses a technique in which a groove is provided in a thrust plate disposed on the width surface of a planetary gear and lubricating oil is supplied through the groove of the thrust plate.

Even if a groove is provided in the thrust plate as in Patent Document 4, in the case of the planetary gear devices 210L and 210R in which the internal gears R _L and R _R and the planetary carriers C _L and C _R rotate together, In particular, when the vehicle is traveling at a high speed, the rotating internal gears R _L and R _R scrape the lubricating oil stored in the lower part of the reducer housing, so that the thrust plate is not immersed in the lubricating oil. Even if there is a groove, lubricating oil is not contained in the needle roller bearing 220 that supports the planetary gears P _L and P _R, and a lubricating effect cannot be obtained. In addition, performing the grooving on the thin thrust plate has a problem that the degree of difficulty of the processing is high in the first place.

  Further, in Patent Document 5, an oil reservoir hole is provided in the thrust plate, and the lubricating oil flowing from the needle roller bearing side of the inner peripheral portion of the planetary gear toward the thrust plate is held in the oil retaining hole of the thrust plate. Thus, a technique for improving the lubrication of the sliding surface between the thrust plate and the planetary gear or the planet carrier is disclosed.

  However, in the technique of Patent Document 5, the lubricating oil scattered from the outer peripheral surface of the thrust plate cannot be guided to the needle roller housing space between the outer ring raceway surface and the inner ring raceway surface of the needle roller bearing. In particular, in a planetary gear device of a vehicle drive device in which both the internal gear and the planet carrier rotate, the lubricating oil that has been scraped and scattered from the oil sump at the lower part of the reducer housing by the rotation of the gears is applied to the inner wall of the reducer housing. Since it adheres and flows along the rib provided on the inner wall of the speed reducer housing, even if this lubricating oil reaches the outer peripheral surface of the thrust plate, the technique disclosed in Patent Document 5 uses the lubricating oil as the outer ring raceway of the needle roller bearing. It cannot guide to the accommodation space of the needle roller between the surface and the inner ring raceway surface.

  Therefore, according to the present invention, the lubricating oil that is scraped and spattered from the oil sump at the lower part of the reduction gear housing adheres to the inner wall of the reduction gear housing, and follows the ribs provided on the inner wall of the reduction gear housing. The needle roller that supports the planetary gear by allowing this lubricating oil to be guided to the needle roller housing space between the outer ring raceway surface and the inner ring raceway surface of the needle roller bearing when flowing. It is intended to improve the supply of lubricating oil to the bearing and extend the life of the needle roller bearing.

  In order to solve the above-described problems, the present invention includes an internal gear, a sun gear provided coaxially with the internal gear, a plurality of planetary gears as revolution gears meshing with the internal gear and the sun gear, and a planetary gear. A planetary carrier having a gear support shaft rotatably supported via a needle roller bearing, and a planetary carrier having a carrier flange sandwiching both sides of the planetary gear and having both ends of the gear support shaft inserted and fixed. In a planetary gear device in which a thrust plate is provided between the flange and the width surface of the flange, the outer peripheral shape of the thrust plate is positioned on the outer diameter side of the outer diameter raceway surface of the needle roller bearing provided on the gear support shaft. A combination of a large diameter portion that is in sliding contact between the width surface of the gear and the width surface of the carrier flange, and a small diameter portion that is located on the inner diameter side of the outer diameter raceway surface of the needle roller bearing provided on the gear support shaft, Outside needle roller bearings Between the thrust plate small-diameter portion and the needle roller outer 径軌 road surface of the bearing which is located on the inner diameter side than the raceway surface, and wherein the forming the communicating portion communicating with the accommodating space of the needle roller bearings.

  The planetary gear device is accommodated in a housing, and a hollow shaft portion for supporting the planet carrier with respect to the housing is provided at an axis center of the planet carrier, and the lubricating oil flowing on the wall surface of the housing is supplied to the thrust plate on the hollow shaft portion. You may provide the lubricating oil channel | path supplied to the outer-diameter part.

  The sun gear may be supported on the inner diameter portion of the hollow shaft portion via a rolling bearing, and the lubricating oil passage supplied to the outer diameter portion of the thrust plate may be provided so as to pass through the rolling bearing supporting the sun gear.

  A lubricating oil is provided between the hollow shaft portion and the sun gear, and a spline portion for transmitting torque is provided. The spline portion is provided with a missing tooth portion, and the missing tooth portion supplies lubricating oil to the outer diameter portion of the thrust plate. You may make it comprise a channel | path.

  An oil receiving member that collects the lubricating oil flowing on the wall surface of the housing and supplies the lubricating oil into the hollow shaft portion may be provided on the wall surface of the housing that faces the hollow shaft portion.

  A step portion may be provided on the inner diameter surface of the hollow shaft portion, and an oil guide pipe may be provided on the oil receiving member to guide the lubricating oil collected beyond the step portion to the inside in the axial direction.

  Two planetary gear devices according to the present invention are coaxially combined between two drive sources mounted on a vehicle and independently controllable and left and right drive wheels, a specific element of one planetary gear device, A gear unit for amplifying a torque difference between the left and right drive wheels and transmitting torque from two drive sources by mutually connecting a specific element of the other planetary gear unit by a first coupling member and a second coupling member. And a vehicle drive device in which an external gear as a speed reducer is connected to the internal gear of the planetary gear device.

  As described above, according to the present invention, the accommodation space of the needle roller bearing that rotatably supports the planetary gear on the outer diameter portion of the thrust plate provided between the width surface of the planetary gear and the width surface of the carrier flange. Since the communicating portion that communicates with the thrust roller is formed, lubricating oil supplied to the outer diameter portion of the thrust plate can be introduced into the accommodation space of the needle roller bearing through the communicating portion, so that the needle roller bearing that supports the planetary gear can be Thus, the supply of lubricating oil can be improved, and the life of the needle roller bearing can be extended.

It is a cross-sectional top view which shows embodiment of the drive device for vehicles incorporating the planetary gear apparatus of this invention. It is an enlarged view of the gear apparatus part of embodiment of FIG. 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 velocity diagram for demonstrating the torque difference gain by the gear apparatus integrated in the vehicle drive device which concerns on embodiment of FIG. It is an enlarged view of the spline part formed in the inner surface of the hollow shaft part of the planetary carrier in embodiment of FIG. FIG. 2 is a partially enlarged view showing a lubricating oil supply path to a needle roller bearing that supports a planetary gear in the left planetary gear device of the embodiment of FIG. 1. FIG. 3 is a partially enlarged view showing a lubricating oil supply path to a needle roller bearing that supports a planetary gear in the right planetary gear device of the embodiment of FIG. 1. It is sectional drawing of AA of FIG. 1 which shows arrangement | positioning of the gearwheel of embodiment of FIG. It is an enlarged side view of the planetary gear of the embodiment of FIG. It is a perspective view which shows an example of the thrust board used by this invention. It is an enlarged side view which shows the state which mounted | wore the side surface of the planetary gear with the thrust board of FIG. It is a perspective view which shows the other example of the thrust board used by this invention. It is an enlarged side view which shows the state which mounted | wore the side surface of the planetary gear with the thrust board of FIG. It is a perspective view which shows the other example of the thrust board used by this invention. It is an enlarged side view which shows the state which mounted | wore the side surface of the planetary gear with the thrust board of FIG. It is sectional drawing of the BB line of FIG. 2 which shows the supply path | route of the lubricating oil of the planetary gear apparatus using the thrust board of FIG. It is a cross-sectional top view which shows other embodiment of the drive device for vehicles incorporating the planetary gear apparatus of this invention. It is an enlarged view of the gear apparatus part of embodiment of FIG. It is the elements on larger scale which show the supply path | route of the lubricating oil to the needle roller bearing which supports the planetary gear in the planetary gear apparatus of the left side of embodiment of FIG. It is the elements on larger scale which show the supply path | route of the lubricating oil to the needle roller bearing which supports the planetary gear in the planetary gear apparatus of the right side of embodiment of FIG. It is a perspective view at the time of attaching the oil receiving member used for a planetary gear apparatus in the embodiment of FIG. 17 on the left side. It is a perspective view at the time of attaching the oil receiving member used for a planetary gear apparatus in the embodiment of FIG. 17 on the right side. It is sectional drawing of the conventional planetary gear apparatus. It is a cross-sectional top view which shows the vehicle drive device of prior application example 1. FIG. 25 is an enlarged view of a gear device portion of the vehicle drive device of the first application example shown in FIG. 24. 3 is a perspective view of a thrust plate used in the vehicle drive device of Prior Application Example 1. FIG. It is an enlarged side view which shows the state which mounted | wore the side surface of the planetary gear with the thrust board of FIG.

  Hereinafter, an embodiment of the present invention will be described as a parallel shaft gear of a vehicle drive device as a torque difference amplification mechanism capable of amplifying a torque difference and transmitting a drive torque from two independent drive sources to left and right drive wheels. A planetary gear device incorporated in the reduction gear will be described as an example.

  The electric vehicle AM shown in FIG. 3 is a rear wheel drive system, and includes a chassis 60, drive wheels 61L and 61R as rear wheels, front wheels 62L and 62R, a two-motor vehicle drive device 1, a battery 63, An inverter 64 and the like are provided. In FIG. 3, the gear structure of the vehicle drive device 1 is shown in a skeleton diagram.

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

  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 including 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 system and 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 1 may be mounted on both the front wheels or the rear wheels, or mounted on one of them, and the other is another drive such as a gear device driven by an engine. It may be a device.

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

  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, It consists of inner side walls 4cL and 4cR provided on the inner side surface of 4aR. The inner walls 4cL and 4cR of the motor housings 4L and 4R are provided with openings through which the motor shaft 5a is drawn.

  As shown in FIG. 1, the electric motors 2L and 2R are of a radial gap type in which a stator 6 is provided on the inner peripheral surface of the motor housing main bodies 4aL and 4aR, and a rotor 5 is provided on the inner periphery of the stator 6 with a gap. 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 housings 4L and 4R to the speed reducers 3L and 3R, respectively. A seal member 7 is provided between the openings of the inner side walls 4cL and 4cR of the motor housings 4L and 4R 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 housings 4L and 4R (FIG. 1).

  The speed reducer housing 9 that accommodates the two speed reducers 3L and 3R provided in parallel on the left and right sides has an end surface on the outboard side (outside the vehicle body), the inner walls 4cL of the motor housings 4L and 4R of the electric motors 2L and 2R, It is fixed to 4cR by a plurality of bolts (not shown) (FIG. 1).

  As shown in FIG. 1, the reduction gear housing 9 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 accommodating the two speed reducers 3L and 3R are provided in parallel.

  As shown in FIG. 1, the speed reducers 3L and 3R are provided substantially symmetrically, and input gear shafts 12L and 12R having an input gear 12a to which torque is transmitted from the motor shaft 5a and the input gear 12a meshing with each other. The intermediate gear shafts 13L and 13R having the output side small diameter gear 13b meshing with the side large diameter gear 13a and the output gear 14a, and the output gear 14a, the constant velocity joints 65a and 65b (FIG. 3), the intermediate shaft 65c (FIG. 3). ) Through which the output gear shafts 14L and 14R transmit torque to the drive wheels 61L and 61R (FIG. 3). The input gear shafts 12L and 12R, the intermediate gear shafts 13L and 13R, and the output gear shafts 14L and 14R of the two left and right speed reducers 3L and 3R are coaxially arranged.

  Both ends of the input gear shafts 12L and 12R of the reduction gears 3L and 3R are formed in bearing fitting holes 16a formed on both left and right sides of the partition wall 11 of the reduction gear housing 9 and inner side walls 4cL and 4cR of the motor housing main bodies 4aL and 4aR. The bearing fitting hole 16b is rotatably supported via rolling bearings 17a and 17b. In FIG. 1, the rolling bearings 17a and 17b are the same, but different sizes may be combined.

  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 sets of intermediate gear shafts 13L and 13R are arranged. In the embodiment shown in FIG. 1, the intermediate gear shafts 13L and 13R have a pair of intermediate gear shafts 13L and 13R.

  The intermediate gear shafts 13L and 13R constitute a stepped gear shaft having an input-side large-diameter gear 13a meshing with the input gear 12a and an output-side small-diameter gear 13b meshing with the output gear 14a on the outer peripheral surface. Both ends of the intermediate gear shafts 13L and 13R are formed in bearing fitting holes 19a formed on both surfaces of the partition wall 11 of the speed reducer housing 9 and bearing fitting holes 19b on the inner side walls 4cL and 4cR of the motor housing bodies 4aL and 4aR. It is supported via rolling bearings 20a and 20b. In FIG. 1, the rolling bearings 20a and 20b have different sizes, but the same size may be combined.

  The intermediate gear shafts 13L and 13R arranged coaxially amplify the difference in torque applied from the two electric motors 2L and 2R to the left and right drive wheels 61L and 61R coaxially with the intermediate gear shafts 13L and 13R. The gear device 30 for distributing is then incorporated.

  The gear unit 30 includes three-element and two-degree-of-freedom planetary gear units 39L and 39R that are coaxially combined with a pair of left and right intermediate gear shafts 13L and 13R arranged coaxially.

Planetary gear unit 39L constituting the gearing 30 in the vehicle drive device 1, 39R, respectively internal gear R _L, R _R and internal gear R _L, R _R and planet carrier C _L provided coaxially, C _R , sun gears S _L and S _R provided coaxially with the internal gears R _L and R _R, and a plurality of planetary gears P _L and P _R as revolving gears. Gear 30, one of the planet carrier C _L and the first coupling member 31 for coupling the other of 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 32, the first coupling member 31 and the second coupling member 32 are coaxially arranged, and of the first coupling member 31 and the second coupling member 32, the second coupling member 32 is a hollow shaft, The coupling member 31 has a shaft inserted through the hollow shaft, and the shaft passing between the two planetary gear devices 39L and 39R has a double structure, and the internal gear R _{L of the} planetary gear devices 39L and 39R. , R _R and the input gear 12a of the reduction gears 3L, 3R are engaged with and connected to the input-side large-diameter gear 13a connected to the internal gears R _L , R _R.

  The vehicle drive device 1 can amplify the torque difference between the electric motors 2L and 2R that drive the left and right wheels and output the amplified difference to the wheels.

  In other words, the driving force of the electric motors 2L and 2R is transmitted by the reduction gear train of the three-axis two-stage reduction gear, and the gear device 30 is formed by coaxially coupling the two planetary gear devices 39L and 39R 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 39L and 39R (sun gears S _L and S _R , planetary gears P _L and P _R ) of the gear device 30 are rotated relative to each other. First, the planetary gear devices 39L and 39R rotate together. When there is a difference in the rotational speeds of the wheels, the insides of the two planetary gear devices 39L and 39R of the gear device 30 rotate, and the sun gears S _L and S _R and the internal gears R _L and R _R rotate relative to each other. The planetary gears P _L and P _R rotate and revolve.

  The gear configuration of the two-motor type vehicle drive device 1 of the embodiment shown in FIGS. 1 and 2 is as shown in the skeleton diagram of FIG.

  As shown in FIG. 3, 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, 2R increases with the gear ratio between the input gear shaft 12a of the reduction gears 3L, 3R and the input gear 12a of the intermediate gear shaft 13L, 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 devices 39L and 39R having the same three-element and two-degree-of-freedom with coaxial intermediate gear shafts 13L and 13R. As the planetary gear devices 39L and 39R, single-pinion planetary gears are used. The device is adopted.

The planetary gear devices 39L and 39R are arranged on the same axis with the sun gears S _L and S _R and the internal gears R _L and R _R and between the 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 located in the direction of the planetary gears, and planetary gears P _L , P _R rotatably supported by the planetary gears provided coaxially with the sun gears S _L , S _R and the internal gears R _L , R _R It is composed of 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 devices 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 device 39L having the sun gear S _L , the planet carrier C _L , the planet gear P _L and the internal gear R _L , and the sun gear S _R and the planet carrier C. _R, a second planetary gear unit 39R having a planetary gear P _R and the internal gear R _R is configured by combining coaxially.

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

The torque TM1 generated by the electric motor 2L in the internal gear _RL of the first planetary gear device 39L is transmitted to the intermediate gear shaft 13L through the engagement of the input gear 12a of the input gear shaft 12L and 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, and the output-side small-diameter gear 13b of the intermediate gear shaft 13L and the output gear shaft 14L The output gear 14a meshes with the output gear shaft 14L, and the drive torque TL is output to the drive wheel 61L.

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

The outputs from the electric motors 2L and 2R are given to the internal gears R _L and R _R of the two planetary gear devices 39L and 39R, and the outputs from the first coupling member 31 and the second coupling member 32 are the driving wheels 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 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, splines to the planet carrier C _L They are connected by a bond (including a serration bond). 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 devices 39L and 39R are coupled by the first coupling member 31 and the second coupling member 32.

Since the gear device 30 is configured by combining two identical single pinion type planetary gear devices 39L and 39R, 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 unit 39L is shown on the upper side, and the speed diagram of the right planetary gear unit 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 transmitted through the input-side large-diameter gears 13a meshing with the input gears 12a of the input gear shafts 12L and 12R. Since the gears R _L and R _R are input, a reduction ratio is applied, and the drive torques TL and TR taken out from the gear device 30 are transmitted to the left and right drive wheels 61L via the output-side small gears 13b that mesh with the output gear 14a. However, in order to facilitate understanding, the speed ratio and the calculation formulas shown in FIG. 4 are omitted in the following description of the speed ratio and the calculation formulas, and the internal gears R _L , R are omitted. _The torque input to _R remains TM1 and TM2, and the drive torque extracted from the gear unit 30 remains TL and TR.

Since the two planetary gear devices 39L and 39R constituting the gear device 30 use gear elements having the same number of teeth, in the velocity diagram shown in FIG. 4, the inner gear _RL and the planet carrier C _L The distance and the distance between the internal gear R _R and the planet carrier C _R are equal, and this is a. Further, the distance between the sun gear S _L and the planet carrier C _L and the distance between the sun gear S _R and the planet carrier C _R are also equal, which is b. The ratio of the length from the planet carrier C _L , C _R to the internal gear R _L , R _R and the length from the planet carrier C _L , C _R to the sun gear S _L , S _R is the ratio of the internal gear R _L , R _R It is equal to the ratio of the reciprocal number (1 / Zr) of the number of teeth Zr and the reciprocal number (1 / Zs) of the number of teeth Zs of the sun gears S _L and S _R. Therefore, 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. 4, the arrow direction is the positive direction of the moment M.
a * TR + (a + b) * TL- (b + 2a) * TM1 = 0 (1)

The following equation (2) is calculated from the balance of moment M with reference to point R _L.
-A.TL- (a + b) .TR + (b + 2a) .TM2 = 0 (2)

The following formula (3) is obtained from the 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 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 input from the electric motors 2L and 2R is 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 planet carrier C _L , and the sun gear S _L and the planet carrier 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 A driving torque difference ΔTOUT (= α · (TM2−TM1) = TR−TL) larger than the input torque difference ΔTIN can be given to the driving torques TL and TR transmitted to 61R.

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

  As shown in FIG. 1, the output gear shafts 14L and 14R have a hollow structure, and the shaft portion of the outer ring member of the constant velocity joint 65a is formed on the inner peripheral surface of the end portion on the outboard side of the hollow output gear shafts 14L and 14R. The shaft portion of the outer ring member of the constant velocity joint 65a and the inner peripheral surface of the end portion on the outboard side of the hollow output gear shafts 14L and 14R are spline-coupled (including serration coupling).

  Next, 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 65a (see FIG. 3).

  A seal member 55 is provided between the end of the output gear shafts 14L and 14R on the outboard side and the openings formed in the inner walls 4cL and 4cR of the motor housings 4L and 4R, and is enclosed in the speed reducers 3L and 3R. In addition to preventing leakage of lubricating oil, it prevents dust and muddy water from entering the reducers 3L and 3R from the outside.

  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 speed reducer housing 9 and inner walls 4cL and 4cR of the motor housings 4L and 4R. The bearing fitting hole 53b is supported by rolling bearings 54a and 54b. The bearing fitting holes 53a and 53b have a stepped shape with which the outer rings of the rolling bearings 54a and 54b come into contact. 1 and 2, the rolling bearings 54a and 54b are the same, but different sizes may be used in combination.

The planetary gears P _L and P _R of the planetary gear devices 39L and 39R are rotatably supported on the gear support shaft 33 via needle roller bearings 37 as shown in FIG. Both ends of the gear support shaft 33 are inserted and fixed to a pair of carrier flanges 34a and 34b of the planetary carriers C _L and C _R.

Since the outer peripheral surface of the gear support shaft 33 becomes the inner ring raceway surface of the needle roller bearing 37 that rotatably supports the planetary gears P _L and P _R , the high carbon chrome bearing steel (SUJ2) is all hardened and tempered, or Carburized steel (SCM420), such as carburizing and tempering, is heat treated to a surface hardness of 58 HRC or higher, and the surface is ground to a roughness suitable for the inner ring raceway surface.

Then, the planet carrier C _L, the carrier flange 34a on the outboard side of the C _R has a hollow shaft portion 35 that extends outboard, the end portion of the outboard side of the hollow shaft portion 35, the motor housing 4L It is supported via a rolling bearing 20b in a bearing fitting hole 19b formed in the inner walls 4cL and 4cR of 4R.

Of the planetary carriers C _L and C _R , the carrier flange 34b on the inboard side (inner side of the vehicle) of the left planetary carrier C _L has a hollow shaft portion 36 extending toward the inboard side. The outer diameter surface is supported by a bearing fitting hole 19a formed in the partition wall 11 of the reduction gear housing 9 via a rolling bearing 20a.

Further, the planet carrier C _L, of C _R, the carrier flange 34b on the inboard side of the right-hand planet carrier C _R (inside of the vehicle), forming the second coupling member 32 of the hollow extending inboard side together A large-diameter portion 32 a is formed on the carrier flange 34 b side of the hollow second coupling member 32, and the large-diameter portion 32 a is inserted into the bearing fitting hole 19 a formed in the partition wall 11 of the reduction gear housing 9. Is supported through.

  A collar 40 is disposed between the carrier flange 34b on the inboard side and the 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 on the outboard side. Including serration bonds).

The internal gears R _L and R _R are supported by two left and right rolling bearings 39a and 39b with respect to the planetary carriers C _L and C _R.

  The first coupling member 31 and the second coupling member 32 that couple the two planetary gear devices 39L and 39R that constitute the gear device 30 of the vehicle drive device 1 penetrate the partition wall 11 of the reduction gear housing 9. It has been 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, the right end portion is formed in the carrier flange 34b integral with the inboard side of the planet carrier C _R. Left end portion of the second coupling member 32, between the end face on the inboard side of the outboard side carrier flange 34a of the planetary carrier C _L, it is opposed via the inlet gap 72 of the lubricating oil.

The first coupling member 31, the left end portion, are connected by a spline section 73 to the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _L.

The spline portion 73 for connecting the hollow shaft portion 35 of the first coupling left end portion of the member 31 and the planet carrier C _L on the outboard side of the carrier flange 34a, a part of the spline teeth 73a as shown in FIG. 5 The missing tooth part 73b from which the is removed is provided.

The toothless portion 73b, as shown by the thick arrow in FIG. 6, constitutes a lubricating oil passage for lubricating oil that has flowed into the hollow shaft portion 35 of the left side of the planet carrier C _L on the outboard side of the carrier flange 34a Yes.

As shown in FIG. 2, the first coupling member 31 inserted through the second coupling member 32 configured by a hollow shaft has a large-diameter portion 74 at the right end, and an outer peripheral surface of the large-diameter portion 74. , external gear meshing with the planetary gears P _R of the right planetary gear 39R is formed, the outer gear constitutes the sun gear S _R of the right planetary gear 39R.

As described above, the two planetary gear 39L, a first coupling member 31 of 39R, by connecting the splined portion 73 with respect to the planet carrier C _L, to split two planetary gear 39L, the 39R to the left and right The two planetary gear devices 39L and 39R can be assembled into the reduction gear housing 9 from the left and right together with the 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 device 39L is formed, the outer gear of the left planetary gear device The sun gear S _L is configured.

Two planetary gear 39L, a first coupling member 31 on the inner diameter side of the axis of the double structure for connecting 39R, the end of the planetary gear unit 39L is a hollow carrier flange 34a on the outboard side of the planet carrier C _L coupled to the shaft 35 by a spline portion 73, an end portion of the planetary gear unit 39R side, is supported by a rolling bearing 49 in the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _R. This rolling bearing 49 can be constituted by an open type deep groove ball bearing.

By using an open deep groove ball bearing as a rolling bearing 49, as shown by the thick arrow in FIG. 7, and flows into the hollow shaft portion 35 of the right planetary carrier C _R on the outboard side of the carrier flange 34a lubricating oil, through a rolling bearing 49, is supplied to the inserted outer periphery of the thrust plate 38 between the carrier flange 34a and the planetary gear P _R.

Incidentally, the input gear shafts 12L and 12R, the intermediate gear shafts 13L and 13R, and the output gear shafts 14L and 14R are accommodated in the speed reducer housing 9, and FIG. 8 shows the right input gear shaft 12R, the intermediate gear shaft 13R, Although the output gear shaft 14R is shown, the arrangement of the left input gear shaft 12L, the intermediate gear shaft 13L, and the output gear shaft 14L is the same. That is, as shown in FIG. 8, the intermediate gear shafts 13 </ b> L and 13 </ b> R incorporating the gear device 30 are arranged at the lowest position, and an oil sump 75 is provided at the lower portion of the speed reducer housing 9. Bottom of the oil reservoir 75 the oil level height H of the reducer housing 9, the intermediate gear shaft 13L when the vehicle is stopped, the planetary gear P _L incorporated into 13R, as gear support shaft 33 of the P _R is immersed in lubricating oil It is set so that oil bath lubrication and splash lubrication by rotation of gears are performed.

Two planetary gear unit 39L, the gear 30 coupled coaxially in the 39R, as shown in FIG. 8, the interior of the planetary gears P _L when the vehicle is stopped, the gear support shaft 33 of the P _R is immersed in lubricating oil as rotation, even if you set the bottom of the oil reservoir 75 the oil level height H of the reducer housing 9, the internal gear R _L of the gear device 30, R _R also intermediate gear shaft 13L, as a large diameter gear of the 13R to order, internal gear that rotates R _L, R _R is cause to wade through the lubricant oil pooled in the bottom of the reducer housing 9, in particular, during high-speed running of the vehicle is the planetary gears P _L, the P _R gear support shaft 33 Will not be immersed in the lubricating oil.

The lubricating oil that has been scraped and scattered from the oil reservoir 75 in the lower part of the reducer housing 9 by the rotation of the gears adheres to the inner wall of the reducer housing 9 and flows down along ribs (not shown) provided on the inner wall. as shown by the thick arrows 6 and 7, through a rolling bearing 20b for supporting the planetary gear unit 39L, the planet carrier C _L of 39R, the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the C _R, hollow Lubricating oil flows into the shaft portion 35.

The lubricating oil that has flowed into the inside of the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _L of the left side of the planetary gear unit 39L, as shown by the thick arrow in FIG. 6, the left side of the first coupling member 31 through the toothless portion 73b of the spline portion 73 between the hollow shaft portion 35 of the end portion and the planet carrier C _L on the outboard side of the carrier flange 34a (FIG. 5), and the left end portion of the second coupling member 32 It is supplied to the inserted outer periphery of the thrust plate 38 between the inlet gap 72 carrier flange 34a and the planetary gear P _L provided between the end face on the inboard side of the carrier flange 34a of the planetary carrier C _L.

On the other hand, the lubricating oil that has flowed into the inside of the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C _R of the right planetary gear device 39R, as shown by the thick arrow in FIG. 7, a hollow carrier flange 34a respect to the shaft portion 35 through the interior of the rolling bearing 49 supporting the right end portion of the first coupling member 31, is supplied to the inserted outer periphery of the thrust plate 38 between the carrier flange 34a and the planetary gear P _R.

A pair of carrier flanges 34a, 34b and the planetary gears P _L, between P _R, as shown in FIG. 2, the planetary gear P _L, in order to facilitate the rotation of the P _R, gear support shaft 33 is an internal A thrust plate 38 having a passing shape is attached.

As shown in FIG. 9, the needle roller bearing 37 that rotatably supports the planetary gears P _L and P _R with respect to the gear support shaft 33 is an inner ring raceway surface 37 a constituted by the outer diameter surface of the gear support shaft 33. When the planetary gears P _L, and the outer ring raceway surface 37b formed by the radially inner surface of the P _R, and a plurality of needle rollers 37c which is accommodated between the inner ring raceway surface 37a and the outer ring raceway surface 37b, a plurality of It comprises a cage 37d that holds the needle rollers 37c at equal intervals.

In the present invention, as the thrust plate 38, for example, plates having the shapes shown in FIGS. 10 and 11, 12, 13 and 14 and 15 are used.
The thrust plate 38 shown in FIGS. 10 and 11 has a through hole 38a through which the gear support shaft 33 passes at the center, and the outer peripheral shape thereof is substantially a quadrangle. Thrust plate 38 of this quadrangle, the length of a diagonal direction, the needle roller planetary gear P _L which constitutes the outer ring raceway surface 37b of the bearing 37, is formed longer than the inside diameter surface of the P _R, 4 square corners planetary gears P _L of the thrust plate 38, so that sliding contact with the width surface of the P _R. The length of each side of the square of the thrust plate 38, needle roller planetary gear P _L which constitutes the outer ring raceway surface 37b of the bearing 37 is formed shorter than the inner diameter surface of the P _R, quadrangular A communication portion 38 b that communicates with the accommodation space of the needle roller bearing 37 is formed at the center of each side of the outer periphery of the thrust plate 38.

Circumscribed circle diameter of the outer peripheral surface of the square of the thrust plate 38, the planetary gears P _L, greater than the diameter of the outer ring raceway surface 37b formed by the radially inner surface of the P _R. The inscribed circle diameter of the outer peripheral surface of the square thrust plate 38 is smaller than the outer peripheral dimension of the cage 37d of the needle roller bearing 37, and the P. C. D. The communication portion 38b having a sufficiently large size is formed so as to be small to the vicinity.

  The thrust plate 38 shown in FIGS. 12 and 13 is similar to the thrust plate 38 shown in FIGS. 10 and 11 in that the outer peripheral shape is approximately a quadrangle, and the central portion of each side is curved inward, so that FIGS. 11, the inscribed circle diameter of the outer peripheral surface of the rectangular thrust plate 38 is further smaller than the thrust plate 38 shown in FIG. 11, and the communication portion 38 b communicating with the accommodation space of the needle roller bearing 37 is widened. Lubricating oil easily enters the housing space of the needle roller bearing 37 from the outer periphery of the thrust plate 38 as long as the communication portion 38b is wide.

  The thrust plate 38 shown in FIGS. 14 and 15 has a petal-like shape in which the outer peripheral shape is provided with a convex portion 38 c and a concave portion 38 d in a corrugated shape, and the circumscribed circle of the convex portion 38 c is formed on the needle roller bearing 37. The outer ring raceway surface 37b is made larger, the inscribed circle of the recess 38d is made smaller than the outer ring raceway surface 37b of the needle roller bearing 37, and the bottom portion of the recess 38d communicates with the accommodation space of the needle roller bearing 37. This is an embodiment in which a portion 38b is formed.

FIG. 16 shows that in the right planetary gear unit 39R, the carrier flange 34a and the planetary gear are passed through the inside of a rolling bearing 49 that supports the right end portion of the first coupling member 31 with respect to the hollow shaft portion 35 of the carrier flange 34a. lubricating oil supplied to the outer periphery of the thrust plate 38 which is inserted between the P _R is shows how to enter the accommodation space of the needle roller bearing 37 from the communicating portion 38b of the outer periphery of the thrust plate 38 in the arrow.

  Lubricating oil that has entered the accommodation space of the needle roller bearing 37 from the communication portion 38b on the outer periphery of the thrust plate 38 lubricates the inside of the needle roller bearing 37 and then is connected to the communication portion 38b on the outer periphery of the thrust plate 38 by centrifugal force. To lubricate the external gear teeth.

Since the thrust plate 38 according to the present invention is provided with a communication portion 38b communicating with the accommodation space of the needle roller bearing 37 on the outer peripheral portion, the lubricating oil supplied to the outer periphery of the thrust plate 38 is passed through the communication portion 38b. Te can be guided into the accommodation space of the needle rollers 37c between the inner ring raceway surface 37a and the outer ring raceway surface 37b of the needle roller bearing 37, the planetary gears P _L, to needle roller bearings 37 for supporting the P _R Lubricating oil supply is improved and the life of the needle roller bearing 37 can be extended.

  The material of the thrust plate 38 is steel, and carburizing heat treatment is performed on the case-hardened steel to suppress wear, and the surface hardness is set to 650 to 800 Hv. Alternatively, the material of the thrust plate 38 may be a resin (polyimide) having self-lubricating properties, heat resistance, and oil resistance.

  In addition, it is desirable to reduce the edge stress by chamfering the corners of the outer peripheral surface of the thrust plate 38.

Next, the second embodiment of the present invention shown in FIGS. 17 to 20 receives more lubricating oil flowing along the inner wall and ribs of the speed reducer housing 9 and outputs the planetary carriers C _L and C _R out. The board can be supplied to the inner diameter portion of the hollow shaft portion 35 of the carrier flange 34a, and the following structure is further added to the first embodiment.

  In the second embodiment, a notch portion 19c is provided in the bearing fitting hole 19b of the inner side walls 4cL and 4cR of the motor housings 4L and 4R that support the end portions on the outboard side of the intermediate gear shafts 13L and 13R. As shown by thick arrows in FIGS. 19 and 20, the lubricating oil flowing along the inner wall and rib of the speed reducer housing 9 is passed through the notch portion 19c of the hollow shaft portion 35 on the outboard side of the intermediate gear shafts 13L and 13R. Easy to flow into the side.

  And the oil receiving member 76 which receives the lubricating oil which flowed along the inner side walls 4cL and 4cR is attached to the inner side walls 4cL and 4cR facing the openings of the hollow shaft portions 35 on the outboard side of the intermediate gear shafts 13L and 13R. Yes.

  As shown in FIGS. 21 and 22, the oil receiving member 76 is screwed to the inner side walls 4cL and 4cR and communicates with a receiving plate 76b having a funnel-shaped receiving portion 76a on the upper surface and a bottom portion of the receiving portion 76a. The oil collecting pipe 76c guides the lubricating oil collected by flowing into the receiving portion 76a to the inside of the hollow shaft portion 35 of the intermediate gear shafts 13L and 13R.

In the second embodiment shown in FIGS. 17 and 18, the intermediate gear shaft 13L, 13R on the outboard side of flowing into the hollow shaft portion 35 lubricating oil inside the planetary gears P _L, to flow easily to the P _R side In addition, since the step portion is provided in the hollow shaft portion 35 so that the diameter on the back side is increased, the length of the oil guiding pipe 76c is set to the step portion so that the lubricating oil is supplied beyond the step portion. The length is set to exceed.

  In the hollow shaft portion 35 of the left intermediate gear shaft 13L, a stepped portion is formed by fitting a collar 77 on the inner diameter portion.

Lubricating oil is supplied to the needle roller bearings 37 that support the planetary gears P _L and P _R in the second embodiment as shown in FIGS. 19 and 20.

First, in the planetary gear device 39L on the left side, as shown by a thick arrow in FIG. 19, the lubricating oil flowing along the inner wall and rib of the speed reducer housing 9 flows from the notch portion 19c provided in the bearing fitting hole 19b. It flows into the receiving portion 76a of the oil receiving member 76 attached to the inner wall 4cL of the housing 4L. The lubricating oil collected and collected into the receiving portion 76a of the oil receiving member 76 is guided to the inside of the hollow shaft portion 35 of the carrier flange 34a through the oil guide tube 76c, and then left of the first coupling member 31. through the toothless portion 73b of the spline portion 73 between the hollow shaft portion 35 of the end portion and the planet carrier C _L on the outboard side of the carrier flange 34a (FIG. 5), and the left end portion of the second coupling member 32 The planetary carrier C _L is supplied to the outer periphery of the thrust plate 38 inserted between the carrier flange 34a and the planetary gear P _L from the inflow gap 72 provided between the carrier flange 34a and the end face on the inboard side. It is supplied to the accommodation space of the needle roller bearing 37 through the outer communication portion 38b (FIG. 16). Lubricating oil that has entered the accommodation space of the needle roller bearing 37 from the communication portion 38b on the outer periphery of the thrust plate 38 lubricates the inside of the needle roller bearing 37 and then is connected to the communication portion 38b on the outer periphery of the thrust plate 38 by centrifugal force. To lubricate the external gear teeth.

In the other planetary gear device 39R on the right side, as indicated by a thick line arrow in FIG. 20, the lubricating oil flowing along the inner wall and rib of the reduction gear housing 9 flows from the notch 19c provided in the bearing fitting hole 19b. It flows into the receiving portion 76a of the oil receiving member 76 attached to the wall 4cR. The lubricating oil that has flowed into the receiving portion 76a of the oil receiving member 76 is guided to the inside of the hollow shaft portion 35 of the carrier flange 34a through the oil guide tube 76c, and then supports the right end portion 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, through the outer periphery of the communicating portion 38b of the thrust plate 38 (FIG. 16), needle roller bearing It is supplied to 37 accommodation spaces. Lubricating oil that has entered the accommodation space of the needle roller bearing 37 from the communication portion 38b on the outer periphery of the thrust plate 38 lubricates the inside of the needle roller bearing 37 and then is connected to the communication portion 38b on the outer periphery of the thrust plate 38 by centrifugal force. To lubricate the external gear teeth.

  In the above embodiment, 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 thereto.

  In the above embodiment, the gear device 30 constituting the torque difference amplifying mechanism is located on the intermediate gear shafts 13L and 13R of the parallel shaft gear reducer, but the intermediate gear shafts 13L and 13R (the input side constituting the large gear). There may be a plurality of shafts on which the large-diameter gear 13a and the output-side small-diameter gear 13b constituting the small gear are coaxial, and a gear device 30 that is a torque difference amplifying mechanism can be incorporated in one of them.

  The vehicle on which the vehicle drive device 1 is mounted is not limited to an electric vehicle or a hybrid electric vehicle, and is, for example, a fuel cell vehicle using the first electric motor 2L and the second electric motor 2R as driving sources. Also 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, 2L: Electric motor 3L, 3R: Reducer 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, 8b: Rolling bearing 9: Reduction gear housing 11: Partition walls 12L, 12R: Input gear shaft 12a: Input gear 13L, 13R: Intermediate gear shaft 13a: Input-side large gear 13b: Output Side small diameter gears 14L, 14R: Output gear shaft 14a: Output gears 16a, 16b: Bearing fitting holes 17a, 17b: Rolling bearings 19a, 19b: Bearing fitting holes 19c: Notches 20a, 20b: Rolling bearings 30: Gears Device 31: First coupling member 32: Second coupling member 32a: Large diameter portion 33: Gear support shafts 34a, 34b: Key Rear flange 35, 36: Hollow shaft portion 37: Needle roller bearing 37a: Inner ring raceway surface 37b: Outer ring raceway surface 37d: Cage 38: Thrust plate 38a: Through hole 38b: Communication portion 38c: Convex portion 38d: Concave portion 39L, 39R: planetary gear devices 39a, 39b: rolling bearing 40: collar 49: rolling bearings 53a, 53b: bearing fitting holes 54a, 54b: rolling bearing 55: seal member 60: chassis 61L, 61R: driving wheels 62L, 62R: front wheels 63: battery 64: inverters 65a, 65b: constant velocity joint 65c: intermediate shaft 72: inflow gap 73: spline portion 73a: spline teeth 73b: missing tooth portion 74: large diameter portion 75: oil reservoir 76: oil receiving member 76a: receiving unit 76 b: receiving plates 76c: oil guiding pipe 77: color AM: electric vehicle C _L, C _R : Planetary carrier H: Oil level height M: Moment P _L , P _R : Planetary gears R _L , R _R : Internal gears S _L , S _R : Sun gears

Claims (7)

  An internal gear, a sun gear provided coaxially with the internal gear, a plurality of planetary gears as revolution gears meshing with the internal gear and the sun gear, and a gear that rotatably supports the planetary gear via a needle roller bearing A planet having a support shaft and a planet carrier having a carrier flange sandwiching and fixing both sides of the planet gear and having both ends of the gear support shaft inserted and fixed, and having a thrust plate provided between the width surface of the planet gear and the width surface of the carrier flange In the gear device, the outer peripheral shape of the thrust plate is positioned on the outer diameter side of the outer diameter raceway surface of the needle roller bearing provided on the gear support shaft, and slides between the width surface of the planetary gear and the width surface of the carrier flange. Combined with the large diameter portion in contact with the small diameter portion located on the inner diameter side of the outer diameter raceway surface of the needle roller bearing provided on the gear support shaft, the inner diameter side of the outer diameter raceway surface of the needle roller bearing Thrust plate located at Between the small-diameter portion and the needle roller outer 径軌 road surface of the bearing, the planetary gear unit, characterized in that the formation of the communicating portion communicating with the accommodating space of the needle roller bearings.   The planetary gear device is accommodated in a housing, and a hollow shaft portion for supporting the planet carrier with respect to the housing is provided at an axis center of the planet carrier, and the lubricating oil flowing on the wall surface of the housing is supplied to the thrust plate on the hollow shaft portion. The planetary gear device according to claim 1, wherein a lubricating oil passage is provided to be supplied to an outer diameter portion of the planetary gear unit.   A sunshade is supported on an inner diameter portion of the hollow shaft portion via a rolling bearing, and a lubricating oil passage supplied to the outer diameter portion of the thrust plate is provided so as to pass through the rolling bearing supporting the sun gear. 2. The planetary gear device according to 2.   A lubricating oil is provided between the hollow shaft portion and the sun gear, and a spline portion for transmitting torque is provided. The spline portion is provided with a missing tooth portion, and the missing tooth portion supplies lubricating oil to the outer diameter portion of the thrust plate. The planetary gear device according to claim 2 constituting a passage.   The oil receiving member for collecting the lubricating oil flowing on the wall surface of the housing and supplying the lubricating oil into the hollow shaft portion is provided on the wall surface of the housing facing the hollow shaft portion. The planetary gear device according to any one of the above.   6. The step according to claim 5, wherein a step portion is provided on an inner diameter surface of the hollow shaft portion, and an oil guide pipe is provided on the oil receiving member to guide the lubricating oil collected beyond the step portion to the inside in the axial direction. The planetary gear device described.   Two planetary gear devices according to any one of claims 1 to 6 are coaxially combined between two drive sources mounted on a vehicle and independently controllable and left and right drive wheels, and one planetary gear is combined. A specific element of the device and a specific element of the other planetary gear device are connected to each other by the first connecting member and the second connecting member, so that the power from the two driving sources is torque difference between the left and right driving wheels. A vehicle drive device comprising a gear device for amplifying and transmitting, wherein an external gear as a speed reducer is connected to an internal gear of the planetary gear device.

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