JP2018054053A - Vehicle drive device - Google Patents

Vehicle drive device Download PDF

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JP2018054053A
JP2018054053A JP2016192398A JP2016192398A JP2018054053A JP 2018054053 A JP2018054053 A JP 2018054053A JP 2016192398 A JP2016192398 A JP 2016192398A JP 2016192398 A JP2016192398 A JP 2016192398A JP 2018054053 A JP2018054053 A JP 2018054053A
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gear
coupling member
planetary
oil
shaft
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英範 柄澤
Hidenori Karasawa
英範 柄澤
功 平井
Isao Hirai
功 平井
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

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Abstract

PROBLEM TO BE SOLVED: To improve lubrication at a roller bearing 20a and attain its long life so as to support a gear device 30 for increasing a torque difference where planetary gear devices 39L, 39R are combined in a coaxial manner.SOLUTION: A first connecting member 31 is provided with a plurality of radial direction holes 82, 83 showing different phases in respect to an axial direction hole 81 becoming an oil passage for a shaft center oil supply; and a second connecting member 32 composed of a hollow shaft is provided with a plurality of radial direction holes 84 showing different phases. Lubricant oil flowing at a wall surface of a speed reducer housing 9 is collected at the wall surface of the speed reducer housing 9 oppositely facing against an end surface of the axial direction hole 81 arranged at the first connecting member 31; there is provided an oil guiding member 86 for supplying lubricant oil in the axial direction hole 81 of the first connecting member 31; and lubricant oil supplied from an oil guide member 86 into the axial direction hole 81 of the first connecting member 31 is supplied from the radial direction holes 82, 83 arranged at the first connecting member 31 to the inner peripheral surface of the outside second connecting member 32.SELECTED DRAWING: Figure 3

Description

この発明は、独立した二つの駆動源からの駆動トルクを、二つの出力部（左右の駆動輪、前後の駆動車軸など）にトルク差を増幅して伝達することができる車両用駆動装置に関するものである。   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 two output units (left and right drive wheels, front and rear drive axles, etc.). It is.

特許文献１及び特許文献２には、二つの駆動源と左右の駆動輪との間に、３要素２自由度の遊星歯車装置を同軸上に二つ組み合わせた歯車装置を備え、二つの駆動源から与えられるトルクの差を増大して左右の駆動輪に与えることができる車両用駆動装置が開示されている。   Patent Document 1 and Patent Document 2 each include a gear device in which two planetary gear devices 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 is disclosed that can increase the difference in torque applied from the left and right sides and apply the difference to left and right drive wheels.

本願の出願人は、特許文献１と特許文献２におけるトルク差を増大する歯車装置よりも小型、軽量化を図った車両用駆動装置を、既に特許出願を行っている（特願２０１６−０２３５２９号）。   The applicant of the present application has already filed a patent application for a vehicle drive device that is smaller and lighter than the gear device that increases the torque difference in Patent Document 1 and Patent Document 2 (Japanese Patent Application No. 2006-023529). ).

この本願の出願人が特許出願している車両用駆動装置（先願例１）は、図１２及び図１３に示す構成である。   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. 12 and 13.

先願例１の車両用駆動装置２００における歯車装置３００を構成する遊星歯車装置２１０Ｌ、２１０Ｒは、それぞれ内歯車ＲL、ＲRと、内歯車ＲL、ＲRと同軸上に設けられた遊星キャリヤＣL、ＣRと、内歯車ＲL、ＲRと同軸上に設けられた太陽歯車ＳL、ＳRと、公転歯車としての複数の遊星歯車ＰL、ＰRとを有する。 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.

歯車装置３００は、一方の遊星キャリヤＣLと他方の太陽歯車ＳRとを結合する第１結合部材２１１と、一方の太陽歯車ＳLと他方の遊星キャリヤＣRとを結合する第２結合部材２１２を有し、第1結合部材２１１と第２結合部材２１２が同軸上に配置されると共に、第1結合部材２１１および第２結合部材２１２のうち、第２結合部材２１２が中空軸、第1結合部材２１１が中空軸の第２結合部材２１２に挿通される軸を有し、２つの遊星歯車装置２１０Ｌ、２１０Ｒの間を通る軸が二重構造となる構成であって、遊星歯車装置２１０Ｌ、２１０Ｒの内歯車ＲL、ＲRと減速機の入力歯車２１３とを、内歯車ＲL、ＲRに設けた外歯車２１７に係合して連結する構造である。 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.

この先願例１の車両用駆動装置２００は、左右輪を駆動する駆動モータ１０１Ｌ、１０１Ｒのトルク差を増大して車輪に出力することができる。   The vehicle drive device 200 of the prior application example 1 can increase the torque difference between the drive motors 101L and 101R that drive the left and right wheels and output the increased torque difference to the wheels.

即ち、駆動モータ１０１Ｌ、１０１Ｒの駆動力は、３軸２段減速機の減速ギヤ列で伝達され、２軸目に位置する２個の遊星歯車装置２１０Ｌ、２１０Ｒを同軸で結合した歯車装置３００により、入力トルクの差が増大され左右輪に出力される。   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 increased and output to the left and right wheels.

そして、車輪の回転速度に差が無い場合には、歯車装置３００の２個の遊星歯車装置２１０Ｌ、２１０Ｒの内部（太陽歯車ＳL、ＳR、遊星歯車ＰL、ＰR）は相対回転せず、遊星歯車装置２１０Ｌ、２１０Ｒが一体となり回転する。車輪の回転速度に差が有る場合には、歯車装置３００の２個の遊星歯車装置２１０Ｌ、２１０Ｒの内部が回転し、太陽歯車ＳL、ＳR、内歯車ＲL、ＲRは相対回転し、遊星歯車ＰL、ＰRが自転・公転する。 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.

特開２０１５−２１５９４号公報JP 2015-21594 A 特許第４９０７３９０号公報Japanese Patent No. 4907390

ところで、歯車装置３００は、減速機ハウジング１０２に対して、内歯車ＲL、ＲRと同軸上に設けられた遊星キャリヤＣL、ＣRの両端部で、転がり軸受１０４、１０５によって支持されている。 Incidentally, the gear device 300 is supported by the rolling bearings 104 and 105 at both ends of the planetary carriers C L and C R provided coaxially with the internal gears R L and R R with respect to the reduction gear housing 102. Yes.

即ち、遊星キャリヤＣL、ＣRの両端部は、減速機ハウジング１０２の側面壁１０２ａと中央壁１０２ｂに設けた軸受穴１０３ａ、１０３ｂに転がり軸受１０４、１０５を介して支持されている。 That is, both end portions of the planetary carriers C L and C R are supported via the rolling bearings 104 and 105 in the bearing holes 103 a and 103 b provided in the side wall 102 a and the center wall 102 b of the reduction gear housing 102.

そして、先願例１の車両用駆動装置２００に使用される遊星歯車装置２１０Ｌ、２１０Ｒにおいては、歯車歯面や転がり軸受１０４、１０５の潤滑のために、遊星歯車装置２１０Ｌ、２１０Ｒの歯車の一部や遊星キャリヤＣL、ＣRの両端を支持する転がり軸受１０４、１０５の軌道面の一部が減速機ハウジング１０２の下部に溜められた潤滑油に浸かるよう油面高さが設定され、油浴潤滑や歯車の回転による跳ね掛け潤滑が行われている。 In the planetary gear devices 210L and 210R used in the vehicle drive device 200 according to the first application example, the gears of the planetary gear devices 210L and 210R are used to lubricate the gear tooth surfaces and the rolling bearings 104 and 105. The oil surface height is set so that part of the raceway surfaces of the rolling bearings 104 and 105 that support both ends of the rotor and planetary carriers C L and C R is immersed in the lubricating oil stored in the lower part of the reducer housing 102. Splash lubrication by bath lubrication or gear rotation is performed.

ところが、先願例１の車両用駆動装置２００のように、２個の遊星歯車装置２１０Ｌ、２１０Ｒを同軸で結合した歯車装置３００においては、車両の停止時に遊星キャリヤＣL、ＣRの両端を支持する転がり軸受１０４、１０５の一部が潤滑油に浸かるように油面高さを設定していても、歯車装置３００の内歯車ＲL、ＲRも中間歯車軸の大歯車として回転するため、回転する内歯車ＲL、ＲRが減速機ハウジング１０２の下部に溜められた潤滑油を掻き分けてしまい、特に、車両の高速走行時は遊星キャリヤＣL、ＣRの両端を支持する転がり軸受１０４、１０５が潤滑油に浸からない状態になる。 However, in the gear device 300 in which the two planetary gear devices 210L and 210R are coaxially coupled as in the vehicle drive device 200 of the prior application example 1, both ends of the planet carriers C L and C R are connected to each other when the vehicle is stopped. The internal gears R L and R R of the gear device 300 rotate as large gears of the intermediate gear shaft even if the oil level is set so that a part of the supporting rolling bearings 104 and 105 is immersed in the lubricating oil. The rotating internal gears R L , R R scrape the lubricating oil accumulated in the lower part of the speed reducer housing 102, and in particular, rolling bearings that support both ends of the planetary carriers C L , C R when the vehicle runs at high speed. 104 and 105 are not immersed in the lubricating oil.

さらに、図１２及び図１３に示す例では、歯車装置３００の軸方向寸法を小さくするために、遊星キャリヤＣL、ＣRのインボード側の側面に凹部１０６を設け、この凹部１０６内に、遊星キャリヤＣL、ＣRの両端を支持する転がり軸受１０４、１０５のうち、インボード側の転がり軸受１０４の一部が嵌るようにしている。このように、インボード側の転がり軸受１０４の一部を、遊星キャリヤＣL、ＣRのインボード側の側面の凹部１０６に嵌め入れると、油浴潤滑や歯車の回転による跳ね掛け潤滑では、インボード側の転がり軸受１０４に潤滑油が供給され難くなる。 Further, in the example shown in FIGS. 12 and 13, in order to reduce the axial dimension of the gear device 300, a concave portion 106 is provided on the side surface on the inboard side of the planetary carriers C L and C R , Of the rolling bearings 104 and 105 that support both ends of the planetary carriers C L and C R , a part of the rolling bearing 104 on the inboard side is fitted. As described above, when a part of the inboard side rolling bearing 104 is fitted into the recess 106 on the inboard side of the planetary carriers C L and C R , in oil bath lubrication and splash lubrication by gear rotation, Lubricating oil is unlikely to be supplied to the inboard rolling bearing 104.

また、内歯車ＲL、ＲRと遊星キャリヤＣL、ＣRが共に回転する遊星歯車装置２１０Ｌ、２１０Ｒの油浴潤滑や跳ね掛け潤滑では、遊星歯車ＰL、ＰRを支持する針状ころ軸受２２０の収容空間に潤滑油が供給され難く、潤滑不良により針状ころ軸受２２０が早期に破損する恐れもある。 Further, 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.

そこで、この発明は、遊星歯車装置を同軸上に二つ組み合わせたトルク差を増大する歯車装置を支持する転がり軸受について、その潤滑を改善し、長寿命化することを課題とするものである。   SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to improve lubrication and extend the life of a rolling bearing that supports a gear device that increases the torque difference by combining two planetary gear devices on the same axis.

前記の課題を解決するために、この発明は、車両に搭載され車輪を駆動する独立して制御可能な二つの電動モータと、二つの電動モータと二つの出力部との間に設けられ、二つの電動モータからのトルクを二つの出力部に分配する歯車装置と、二つの電動モータのトルクを二つの出力部に伝達する減速機とを備える車両用駆動装置において、減速機は、電動モータに連結し、入力歯車を有する入力歯車軸と、出力部に連結し、出力歯車を有する出力歯車軸と、歯車の噛合いにより入力歯車軸から出力歯車軸の間のトルク伝達を行う中間歯車軸が少なくとも1つ以上備え、歯車装置は、同軸に設けられた左右の1対の中間歯車軸と同軸上に二つ組み合わせた３要素２自由度の遊星歯車装置からなり、この遊星歯車装置は、内歯車と、内歯車と同軸上に設けられた遊星キャリヤと、内歯車と同軸上に設けられた太陽歯車と、公転歯車としての複数の遊星歯車とを備え、二つの遊星歯車装置の一方の遊星キャリヤと他方の太陽歯車とを結合する第１結合部材と、一方の太陽歯車と他方の遊星キャリヤとを結合する第２結合部材とを有し、第２結合部材は中空軸であり、第１結合部材は第２結合部材に内包され、第１結合部材と第２結合部材で二重軸となり、歯車装置の二つの遊星歯車機構の遊星キャリヤは、それぞれが両端を転がり軸受を介して減速機ハウジングに支持され、減速機の潤滑機構が、減速機ハウジング下部に溜まった潤滑油を歯車の回転により飛散させて潤滑する跳ね掛け潤滑であり、第１結合部材に軸心給油の油路となる軸方向穴と位相違いの複数の径方向穴を設け、中空軸からなる第２結合部材に位相違いの複数の径方向穴を設け、第１結合部材に設けられた軸方向穴の端面に対面する減速機ハウジングの壁面に、減速機ハウジングの壁面を流れる潤滑油を集油し、第１結合部材の軸方向穴内に潤滑油を供給する導油部材を設け、導油部材から第１結合部材の軸方向穴内に供給された潤滑油を、第１結合部材に設けた径方向穴から外側の第２結合部材の内周面に給油し、第２結合部材の内周面に給油された潤滑油を、二つの遊星歯車装置の遊星キャリヤの両端を支持する転がり軸受のうちのインボード側の転がり軸受に対し第２結合部材に設けた径方向穴から給油するようにしたものである。   In order to solve the above problems, the present invention is provided between two independently controllable electric motors mounted on a vehicle and driving wheels, two electric motors, and two output units. In a vehicle drive device including a gear device that distributes torque from one electric motor to two output units and a speed reducer that transmits torque of the two electric motors to two output units, the speed reducer is connected to the electric motor. An input gear shaft having an input gear connected thereto, an output gear shaft having an output gear connected to an output portion, and an intermediate gear shaft for transmitting torque between the input gear shaft and the output gear shaft by meshing of the gears. The gear device comprises at least one, and a gear device is composed of a planetary gear device having three elements and two degrees of freedom coaxially combined with a pair of left and right intermediate gear shafts provided coaxially. Coaxial with gear and internal gear A planetary carrier provided on the inner gear, a sun gear provided coaxially with the internal gear, and a plurality of planetary gears as revolution gears, and one planetary carrier and the other sun gear of the two planetary gear units. A first coupling member for coupling, a second coupling member for coupling one sun gear and the other planet carrier, the second coupling member is a hollow shaft, and the first coupling member is connected to the second coupling member. The planetary carrier of the two planetary gear mechanisms of the gear unit is supported by the reduction gear housing via rolling bearings at both ends, and is included in the double shaft of the first coupling member and the second coupling member. The lubrication mechanism is splash lubrication in which the lubricating oil accumulated in the lower part of the speed reducer housing is scattered and lubricated by the rotation of the gears, and the first coupling member has a plurality of phases that are out of phase with the axial hole serving as the oil passage for the axial center oil supply. A radial shaft with a hollow shaft A plurality of radial holes of different phases are provided in the second coupling member, and the lubricating oil flows through the wall surface of the reduction gear housing on the wall surface of the reduction gear housing facing the end surface of the axial hole provided in the first coupling member. An oil guide member that collects oil and supplies lubricating oil into the axial hole of the first coupling member is provided, and the lubricating oil supplied from the oil guiding member into the axial hole of the first coupling member is supplied to the first coupling member. Rolls that supply oil from the provided radial holes to the inner circumferential surface of the second coupling member on the outer side and lubricate the inner circumferential surface of the second coupling member to support both ends of the planetary carriers of the two planetary gear units. Oil is supplied from a radial hole provided in the second coupling member to the in-board side rolling bearing of the bearing.

第２結合部材に設ける径方向穴の軸方向位置は、歯車装置を構成する二つの遊星歯車装置のインボード側の遊星キャリヤを減速機ハウジングに対して支持する二つの転がり軸受の転動体間の中心位置に設けることが望ましい。   The axial position of the radial hole provided in the second coupling member is determined between the rolling elements of the two rolling bearings that support the planetary carrier on the inboard side of the two planetary gear devices constituting the gear device with respect to the reduction gear housing. It is desirable to provide it at the center position.

また、第２結合部材に設ける径方向穴の軸方向位置は、歯車装置を構成する二つの遊星歯車装置のインボード側の遊星キャリヤを減速機ハウジングに対して支持する二つの転がり軸受のインボード側の端面間に位置するようにしてもよい。   In addition, the axial position of the radial hole provided in the second coupling member is the inboard of the two rolling bearings that support the planetary carrier on the inboard side of the two planetary gear units constituting the gear unit with respect to the reduction gear housing. It may be located between the end faces on the side.

また、第２結合部材に設けた径方向穴の開口部の少なくとも一部が、歯車装置を構成する二つの遊星歯車装置のインボード側の遊星キャリヤの端面間に位置することが望ましい。   In addition, it is desirable that at least a part of the opening portion of the radial hole provided in the second coupling member is located between the end faces of the planet carrier on the inboard side of the two planetary gear devices constituting the gear device.

さらに、第２結合部材の内周面に、前記径方向穴を含むように周方向溝を設けることにより、第１結合部材の径方向穴から飛散した潤滑油を周方向溝に集めて、第２結合部材の径方向穴へ効率よく流すことが可能となる。   Further, by providing a circumferential groove on the inner peripheral surface of the second coupling member so as to include the radial hole, the lubricating oil scattered from the radial hole of the first coupling member is collected in the circumferential groove, It becomes possible to efficiently flow into the radial holes of the two coupling members.

以上のように、この発明によれば、減速機ハウジングの壁面を流れる潤滑油が、減速機ハウジングの壁面に設けた導油部材によって第１結合部材の軸心に設けた軸方向穴に供給され、第１結合部材の軸方向穴に供給された潤滑油が径方向穴から第２結合部材の内周面に飛散し、第２結合部材の内周面に飛散した潤滑油が、さらに第２結合部材の径方向穴から飛散し、二つの遊星歯車装置のインボード側の遊星キャリヤを支持する転がり軸受に供給されるので、遊星キャリヤを支持する転がり軸受が潤滑不良によって早期に破損したり、異音が生じたりするということを防止することができる。   As described above, according to the present invention, the lubricating oil flowing on the wall surface of the reduction gear housing is supplied to the axial hole provided in the shaft center of the first coupling member by the oil guide member provided on the wall surface of the reduction gear housing. The lubricating oil supplied to the axial hole of the first coupling member scatters from the radial hole to the inner circumferential surface of the second coupling member, and the lubricating oil splattered to the inner circumferential surface of the second coupling member is further second. Because it is scattered from the radial hole of the coupling member and supplied to the rolling bearing that supports the planet carrier on the inboard side of the two planetary gear units, the rolling bearing that supports the planet carrier is damaged early due to poor lubrication, It is possible to prevent abnormal noise from occurring.

また、減速機ハウジングの壁面を流れる潤滑油を、減速機ハウジングの壁面に設けた導油部材から第１結合部材の軸心に設けた軸方向穴に供給するので、軸心給油を実現するためのオイルポンプが不要で、油路の構成が簡易となり、減速機ハウジングの加工も容易となる。   Further, since the lubricating oil flowing on the wall surface of the reduction gear housing is supplied from the oil guide member provided on the wall surface of the reduction gear housing to the axial hole provided in the axial center of the first coupling member, the axial oil supply is realized. No oil pump is required, the oil passage is simplified, and the reduction gear housing is easily processed.

この発明の車両用駆動装置の実施形態を示す横断平面図である。It is a cross-sectional top view which shows embodiment of the vehicle drive device of this invention. 図１の実施形態の歯車装置部分の拡大図である。It is an enlarged view of the gear apparatus part of embodiment of FIG. 図１の実施形態の歯車装置の左側部分の給油状態を示す部分拡大図である。It is the elements on larger scale which show the oil supply state of the left side part of the gear apparatus of embodiment of FIG. 図１の実施形態の歯車装置の右側部分の給油状態を示す部分拡大図である。It is the elements on larger scale which show the oil supply state of the right side part of the gear apparatus of embodiment of FIG. 図１の実施形態の減速機ハウジング内の潤滑油の油面高さを示す断面図である。It is sectional drawing which shows the oil level height of the lubricating oil in the reduction gear housing of embodiment of FIG. 図１の実施形態の歯車装置における第１結合部材に設ける径方向穴と第２結合部材に設ける径方向穴の位置関係を示す部分拡大図である。It is the elements on larger scale which show the positional relationship of the radial hole provided in the 1st coupling member in the gear apparatus of embodiment of FIG. 1, and the radial hole provided in a 2nd coupling member. 図２のＢ−Ｂ線の方向の拡大断面図である。It is an expanded sectional view of the direction of the BB line of FIG. 図１の実施形態において遊星歯車装置に使用する導油部材を左側に取付けた場合の斜視図である。It is a perspective view at the time of attaching the oil guide member used for the planetary gear apparatus in the embodiment of FIG. 1 on the left side. 図１の実施形態において遊星歯車装置に使用する導油部材を右側に取付けた場合の斜視図である。It is a perspective view at the time of attaching the oil guide member used for the planetary gear apparatus in the embodiment of FIG. 1 on the right side. 図１の実施形態に係る車両用駆動装置の歯車構成をスケルトン図で示した電気自動車の説明図である。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. 図１の実施形態に係る車両用駆動装置に組み込まれた歯車装置によるトルク差増幅率を説明するための速度線図である。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. 先願例１に係る車両用駆動装置を示す横断平面図である。It is a cross-sectional top view which shows the vehicle drive device which concerns on the example 1 of prior application. 図１２の車両用駆動装置の歯車装置部分の拡大図である。It is an enlarged view of the gear apparatus part of the vehicle drive device of FIG.

以下、この発明の実施の形態を添付図面に基づいて説明する。   Embodiments of the present invention will be described below with reference to the accompanying drawings.

図１０に示す電気自動車ＡＭは、後輪駆動方式であり、シャーシ６０と、後輪としての駆動輪６１Ｌ、６１Ｒと、前輪６２Ｌ、６２Ｒと、この発明に係る２モータ式の車両用駆動装置１、バッテリ６３、インバータ６４等を備える。図１０では、車両用駆動装置１の歯車構成をスケルトン図で示している。   The electric vehicle AM shown in FIG. 10 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 type vehicle drive device 1 according to the present invention. , A battery 63, an inverter 64, and the like. In FIG. 10, the gear structure of the vehicle drive device 1 is shown in a skeleton diagram.

図１に示す車両用駆動装置１は、車両に搭載され独立して制御可能な二つの駆動源としての電動モータ２Ｌ、２Ｒと、左右の駆動輪６１Ｌ、６１Ｒと二つの電動モータ２Ｌ、２Ｒとの間に設けられる左右２基の減速機３Ｌ、３Ｒとを備える。   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, left and right drive wheels 61L and 61R, and two electric motors 2L and 2R. 2 left and right speed reducers 3L and 3R.

２モータ式の車両用駆動装置１の駆動トルクは、等速ジョイント６５ａ、６５ｂと中間シャフト６５ｃからなるドライブシャフトを介して左右の駆動輪６１Ｌ、６１Ｒに伝達される。   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.

なお、２モータ式の車両用駆動装置１の搭載形態としては、図１０に示す後輪駆動方式の他、前輪駆動方式、四輪駆動方式でもよい。   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.

２モータ式の車両用駆動装置１における左右の電動モータ２Ｌ、２Ｒは、同一の最大出力を有する同一規格の電動モータが用いられ、図１に示すように、モータハウジング４Ｌ、４Ｒ内に収容されている。   The left and right electric motors 2L and 2R in the two-motor type vehicle drive device 1 use the same standard electric motors having the same maximum output, and are housed in the motor housings 4L and 4R as shown in FIG. ing.

モータハウジング４Ｌ、４Ｒは、円筒形のモータハウジング本体４ａＬ、４ａＲと、このモータハウジング本体４ａＬ、４ａＲの外側面を閉塞する外側壁４ｂＬ、４ｂＲと、モータハウジング本体４ａＬ、４ａＲの内側面に減速機３Ｌ、３Ｒと隔てる内側壁４ｃＬ、４ｃＲとからなる。モータハウジング本体４ａＬ、４ａＲの内側壁４ｃＬ、４ｃＲには、モータ軸５ａを引き出す開口部が設けられている。   The motor housings 4L and 4R include cylindrical motor housing bodies 4aL and 4aR, outer walls 4bL and 4bR that close the outer surfaces of the motor housing bodies 4aL and 4aR, and reduction gears on the inner surfaces of the motor housing bodies 4aL and 4aR. It consists of inner walls 4cL and 4cR separated from 3L and 3R. The inner walls 4cL and 4cR of the motor housing bodies 4aL and 4aR are provided with openings through which the motor shaft 5a is drawn.

電動モータ２Ｌ、２Ｒは、図１に示すように、モータハウジング本体４ａＬ、４ａＲの内周面にステータ６を設け、このステータ６の内周に間隔をおいてロータ５を設けたラジアルギャップタイプのものを使用している。なお、電動モータ２Ｌ、２Ｒは、アキシャルギャップタイプのものを使用してもよい。   As shown in FIG. 1, the electric motors 2 </ b> L and 2 </ b> R are of a radial gap type in which a stator 6 is provided on the inner peripheral surface of the motor housing body 4 aL and 4 aR, and a rotor 5 is provided on the inner periphery of the stator 6. I am using something. The electric motors 2L and 2R may be axial gap types.

ロータ５は、モータ軸５ａを中心部に有し、そのモータ軸５ａはモータハウジング本体４ａＬ、４ａＲの内側壁４ｃＬ、４ｃＲの開口部からそれぞれ減速機３Ｌ、３Ｒ側に引き出されている。モータハウジング本体４ａＬ、４ａＲの内側壁４ｃＬ、４ｃＲの開口部とモータ軸５ａとの間にはシール部材７が設けられている。   The rotor 5 has a motor shaft 5a in the center, and the motor shaft 5a is drawn from the openings of the inner walls 4cL and 4cR of the motor housing main bodies 4aL and 4aR to the speed reducers 3L and 3R, respectively. A seal member 7 is provided between the openings of the inner side walls 4cL and 4cR of the motor housing bodies 4aL and 4aR and the motor shaft 5a.

モータ軸５ａは、モータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲと外側壁４ｂＬ、４ｂＲとに転がり軸受８ａ、８ｂによって回転自在に支持されている（図１）。   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).

左右並列に設けられた２基の減速機３Ｌ、３Ｒを収容する減速機ハウジング９は、アウトボード側（車体外側）の端面が、電動モータ２Ｌ、２Ｒのモータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲに複数のボルト（図示省略）によって固定されている（図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).

減速機ハウジング９には、図１に示すように、中央に仕切り壁１１が設けられている。減速機ハウジング９は、この仕切り壁１１によって左右に２分割され、２基の減速機３Ｌ、３Ｒを収容する左右の収容室が並列に設けられている。   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.

減速機３Ｌ、３Ｒは、図１に示すように、概ね左右対称形に設けられ、モータ軸５ａから駆動力が伝達され入力歯車１２ａを有する入力歯車軸１２Ｌ、１２Ｒと、この入力歯車１２ａに噛み合う入力側大径歯車１３ａと出力歯車１４ａに噛み合う出力側小径歯車１３ｂを有する中間歯車軸１３Ｌ、１３Ｒと、出力歯車１４ａを有し、等速ジョイント６５ａ、６５ｂ（図１０）、中間シャフト６５ｃ（図１０）を介して駆動輪６１Ｌ、６１Ｒ（図１０）にトルクを伝達する出力歯車軸１４Ｌ、１４Ｒとを備える平行軸歯車減速機である。左右２基の減速機３Ｌ、３Ｒの各入力歯車軸１２Ｌ、１２Ｒ、中間歯車軸１３Ｌ、１３Ｒ、出力歯車軸１４Ｌ、１４Ｒは、それぞれ同軸上に配置されている。   As shown in FIG. 1, the speed reducers 3L and 3R are provided substantially symmetrically, and are engaged with the input gear shafts 12L and 12R having the input gear 12a to which the driving force is transmitted from the motor shaft 5a. Intermediate gear shafts 13L and 13R having output side small diameter gears 13b meshing with input side large diameter gear 13a and output gear 14a, and output gear 14a, constant velocity joints 65a and 65b (FIG. 10), intermediate shaft 65c (FIG. 10) is a parallel shaft gear reducer provided with output gear shafts 14L and 14R for transmitting torque to drive wheels 61L and 61R (FIG. 10). 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.

減速機３Ｌ、３Ｒの入力歯車軸１２Ｌ、１２Ｒの両端は、減速機ハウジング９の仕切り壁１１の左右両面に形成した軸受嵌合穴１６ａとモータハウジング本体４ａＬ、４ａＲの内側壁４ｃＬ、４ｃＲに形成した軸受嵌合穴１６ｂに転がり軸受１７ａ、１７ｂを介して回転自在に支持されている。図１では、転がり軸受１７ａ、１７ｂは同一のものとしているが、異なるサイズのものを組み合わせてもよい。   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.

入力歯車軸１２Ｌ、１２Ｒは中空構造であり、この中空の入力歯車軸１２Ｌ、１２Ｒに、モータ軸５ａの端部が挿入されている。入力歯車軸１２Ｌ、１２Ｒとモータ軸５ａとは、スプライン（セレーションも含む、以下同じ）結合されている。   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).

中間歯車軸１３Ｌ、１３Ｒは、少なくとも一組以上配置されており、図１に示す実施形態では、一対の中間歯車軸１３Ｌ、１３Ｒを有する。   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.

中間歯車軸１３Ｌ、１３Ｒは、外周面に入力歯車１２ａに噛み合う入力側大径歯車１３ａと出力歯車１４ａに噛み合う出力側小径歯車１３ｂを有する段付きの歯車軸を構成している。この中間歯車軸１３Ｌ、１３Ｒの両端は、減速機ハウジング９の仕切り壁１１の両面に形成した軸受嵌合穴１９ａとモータハウジング本体４ａＬ、４ａＲの内側壁４ｃＬ、４ｃＲの軸受嵌合穴１９ｂとに転がり軸受２０ａ、２０ｂを介して支持されている。図１では、転がり軸受２０ａ、２０ｂは同一サイズのものとしているが、異なるサイズのものを組み合わせてもよい。   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 the same size, but may have different sizes.

同軸上に配置された中間歯車軸１３Ｌ、１３Ｒには、この中間歯車軸１３Ｌ、１３Ｒと同軸上に、二つの電動モータ２Ｌ、２Ｒから与えられるトルクの差を左右の駆動輪６１Ｌ、６１Ｒに増幅して分配する歯車装置３０が組み込まれている。   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.

歯車装置３０は、同軸に配された左右1対の中間歯車軸１３Ｌ、１３Ｒと同軸上に二つ組み合わせた３要素２自由度の遊星歯車装置３９Ｌ、３９Ｒからなる。   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.

車両用駆動装置１における歯車装置３０を構成する遊星歯車装置３９Ｌ、３９Ｒは、それぞれ内歯車ＲL、ＲRと、内歯車ＲL、ＲRと同軸上に設けられた遊星キャリヤＣL、ＣRと、内歯車ＲL、ＲRと同軸上に設けられた太陽歯車ＳL、ＳRと、公転歯車としての複数の遊星歯車ＰL、ＰRとを有する。 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.

歯車装置３０は、一方の遊星キャリヤＣLと他方の太陽歯車ＳRとを結合する第１結合部材３１と、一方の太陽歯車ＳLと他方の遊星キャリヤＣRとを結合する第２結合部材３２を有し、第１結合部材３１と第２結合部材３２が同軸上に配置されると共に、第１結合部材３１および第２結合部材３２のうち、第２結合部材３２が中空軸、第１結合部材３１が中空軸に挿通される軸を有し、２つの遊星歯車装置３９Ｌ、３９Ｒの間を通る軸が二重構造となる構成であって、遊星歯車装置３９Ｌ、３９Ｒの内歯車ＲL、ＲRと減速機３Ｌ、３Ｒの入力歯車１２ａとを、内歯車ＲL、ＲRに連結した入力側大径歯車１３ａに係合して連結する構造である。 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.

この車両用駆動装置１は、左右輪を駆動する電動モータ２Ｌ、２Ｒのトルク差を増大して車輪に出力することができる。   The vehicle drive device 1 can increase the torque difference between the electric motors 2L and 2R that drive the left and right wheels and output the increased difference to the wheels.

即ち、電動モータ２Ｌ、２Ｒの駆動力は、３軸２段減速機の減速ギヤ列で伝達され、２軸目に位置する２個の遊星歯車装置３９Ｌ、３９Ｒを同軸で結合した歯車装置３０により、入力トルクの差が増大され左右輪に出力される。   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 increased and output to the left and right wheels.

そして、車輪の回転速度に差が無い場合には、歯車装置３０の２個の遊星歯車装置３９Ｌ、３９Ｒの内部（太陽歯車ＳL、ＳR、遊星歯車ＰL、ＰR）は相対回転せず、遊星歯車装置３９Ｌ、３９Ｒが一体となり回転する。車輪の回転速度に差が有る場合には、歯車装置３０の２個の遊星歯車装置３９Ｌ、３９Ｒの内部が回転し、太陽歯車ＳL、ＳR、内歯車ＲL、ＲRは相対回転し、遊星歯車ＰL、ＰRが自転・公転する。 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.

図１及び図２に示す実施形態の２モータ式の車両用駆動装置１の歯車構成は、図１０に示すスケルトン図の通りである。   The gear configuration of the two-motor vehicle drive device 1 of the embodiment shown in FIGS. 1 and 2 is as shown in the skeleton diagram of FIG.

図１０に示すように、左右の電動モータ２Ｌ及び電動モータ２Ｒは、車両に搭載されたバッテリ６３からインバータ６４を介して与えられた電力により動作する。そして、電動モータ２Ｌ、２Ｒは、電子制御装置（図示省略）により個別に制御され、異なるトルクを発生させて出力することができる。   As shown in FIG. 10, 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.

電動モータ２Ｌ、２Ｒのモータ軸５ａのトルクは、減速機３Ｌ、３Ｒの入力歯車軸１２Ｌ、１２Ｒの入力歯車１２ａと中間歯車軸１３Ｌ、１３Ｒの入力側大径歯車１３ａとの歯数比で増大されて歯車装置３０の内歯車ＲL、ＲRに伝達される。 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.

そして、歯車装置３０を介して中間歯車軸１３Ｌ、１３Ｒの出力側小径歯車１３ｂが出力歯車軸１４Ｌ、１４Ｒの大径の出力歯車１４ａに噛み合って出力側小径歯車１３ｂと出力歯車１４ａとの歯数比で電動モータ２Ｌ、２Ｒのモータ軸５ａのトルクがさらに増大されて、駆動輪６１Ｌ、６１Ｒに出力される。   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.

歯車装置３０は、３要素２自由度の同一の遊星歯車装置３９Ｌ、３９Ｒが同軸上の中間歯車軸１３Ｌ、１３Ｒに二つ組み合わされて構成され、遊星歯車装置３９Ｌ、３９Ｒとして、シングルピニオン遊星歯車装置を採用している。   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.

遊星歯車装置３９Ｌ、３９Ｒは、同軸上に設けられた太陽歯車ＳL、ＳR及び内歯車ＲL、ＲRと、これら太陽歯車ＳL、ＳRと内歯車ＲL、ＲRとの間に位置する複数の遊星歯車ＰL、ＰRと、遊星歯車ＰL、ＰRを回転可能に支持し太陽歯車ＳL、ＳR及び内歯車ＲL、ＲRと同軸上に設けられた遊星キャリヤＣL、ＣRとから構成される。ここで、太陽歯車ＳL、ＳRと遊星歯車ＰL、ＰRは外周にギヤ歯を有する外歯歯車であり、内歯車ＲL、ＲRは内周にギヤ歯を有する内歯歯車である。遊星歯車ＰL、ＰRは太陽歯車ＳL、ＳRと内歯車ＲL、ＲRとに噛み合っている。 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.

遊星歯車装置３９Ｌ、３９Ｒでは、遊星キャリヤＣL、ＣRを固定した場合に太陽歯車ＳL、ＳRと内歯車ＲL、ＲRとが逆方向に回転するため、図１１に示す速度線図に表すと内歯車ＲL、ＲR及び太陽歯車ＳL、ＳRが遊星キャリヤＣL、ＣRに対して反対側に配置される。 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.

この歯車装置３０は、前記のように、太陽歯車ＳL、遊星キャリヤＣL、遊星歯車ＰL及び内歯車ＲLを有する第１の遊星歯車装置３９Ｌと、同じく太陽歯車ＳR、遊星キャリヤＣR、遊星歯車ＰR及び内歯車ＲRを有する第２の遊星歯車装置３９Ｒとが同軸上に組み合わされて構成されている。 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.

そして、第１の遊星歯車装置３９Ｌの遊星キャリヤＣLと第２の遊星歯車装置３９Ｒの太陽歯車ＳRとが結合されて第１結合部材３１を形成し、第１の遊星歯車装置の太陽歯車ＳLと第２の遊星歯車装置の遊星キャリヤＣRとが結合されて第２結合部材３２を形成している。 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.

第１の遊星歯車装置３９Ｌの内歯車ＲLに電動モータ２Ｌで発生したトルクＴＭ１は、入力歯車軸１２Ｌの入力歯車１２ａと入力側大径歯車１３ａとが噛み合って中間歯車軸１３Ｌに伝達され、中間歯車軸１３Ｌに伝達されたトルクが、第１の遊星歯車機構を介して中間歯車軸１３Ｌの出力側小径歯車１３ｂに伝達され、中間歯車軸１３Ｌの出力側小径歯車１３ｂと出力歯車軸１４Ｌの出力歯車１４ａとが噛み合って出力歯車軸１４Ｌから駆動輪６１Ｌに駆動トルクＴＬが出力される。 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.

第２の遊星歯車装置３９Ｒの内歯車ＲRに電動モータ２Ｒで発生したトルクＴＭ２は、入力歯車軸１２Ｒの入力歯車１２ａと入力側大径歯車１３ａとが噛み合って中間歯車軸１３Ｒに伝達され、中間歯車軸１３Ｒに伝達されたトルクが、第２の遊星歯車装置３９Ｒを介して中間歯車軸１３Ｒの出力側小径歯車１３ｂに伝達され、中間歯車軸１３Ｒの出力側小径歯車１３ｂと出力歯車軸１４Ｒの出力歯車１４ａとが噛み合って出力歯車軸１４Ｒから駆動輪６１Ｒに駆動トルクＴＲが出力される。 Torque TM2 generated by the electric motor 2R to the internal gear R R of the second planetary gear device 39R includes an input gear 12a of the input gear shaft 12R and the input-side large diameter gear 13a is transmitted to the intermediate gear shaft 13R meshing, The torque transmitted to the intermediate gear shaft 13R is transmitted to the output-side small diameter gear 13b of the intermediate gear shaft 13R via the second planetary gear device 39R, and the output-side small diameter gear 13b and the output gear shaft 14R of the intermediate gear shaft 13R. The output gear 14a meshes with the output gear shaft 14R, and the drive torque TR is output from the output gear shaft 14R to the drive wheel 61R.

電動モータ２Ｌ、２Ｒからの出力は、二つの遊星歯車装置３９Ｌ、３９Ｒのそれぞれの内歯車ＲL、ＲRに与えられ、第１結合部材３１、第２結合部材３２からの出力が駆動輪６１Ｌ、６１Ｒに与えられる。 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.

第２結合部材３２は、中空軸で構成されており、その内部に第１結合部材３１が挿通され、第１結合部材３１と第２結合部材３２を構成する軸は二重構造になっている。   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. .

第１結合部材３１は、その一端（図中右端）が太陽歯車ＳRの回転軸であり、他端（図中左端）が太陽歯車ＳLを貫通して設けられ、遊星キャリヤＣLに接続されている。また、中空軸である第２結合部材３２は、一端（図中左端）が太陽歯車ＳLの回転軸となっており、他端（図中右端）は遊星キャリヤＣRと接続されている。この第１結合部材３１と第２結合部材３２によって、二つの遊星歯車装置３９Ｌ、３９Ｒが結合されている。 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 devices 39L and 39R are coupled by the first coupling member 31 and the second coupling member 32.

歯車装置３０は、二つの同一のシングルピニオン形式の遊星歯車装置３９Ｌ、３９Ｒを組み合わせて構成されるため、図１１に示すように二本の速度線図によって表すことができる。ここでは、分かりやすいように、二本の速度線図を上下にずらし、上側に左側の遊星歯車装置３９Ｌの速度線図を示し、下側に右側の遊星歯車装置３９Ｒの速度線図を示す。本来は、図１の実施形態では、各電動モータ２Ｌ、２Ｒから出力されたトルクＴＭ１及びＴＭ２は、各入力歯車軸１２Ｌ、１２Ｒの入力歯車１２ａと噛み合う入力側大径歯車１３ａを介して各内歯車ＲL、ＲRに入力されるため減速比が掛かり、また、歯車装置３０から取り出された駆動トルクＴＬ、ＴＲは、出力歯車１４ａと噛み合う出力側小径歯車１３ｂを介し左右の駆動輪６１Ｌ、６１Ｒへ伝達されるため減速比が掛かるが、以降、理解を容易にするため、図１１に示す速度線図及び各計算式の説明においては、減速比を省略し、各内歯車ＲL、ＲRに入力されるトルクをＴＭ１及びＴＭ２のまま、歯車装置３０から取り出された駆動トルクはＴＬ、ＴＲのままとする。 Since the gear device 30 is configured by combining two planetary gear devices 39L and 39R of the same single pinion type, 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. 11 are omitted in the description of the speed diagram 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.

歯車装置３０を構成する二つの遊星歯車装置３９Ｌ、３９Ｒは、同一の歯数の歯車要素を使用しているため、図１１に示す速度線図においては内歯車ＲLと遊星キャリヤＣLとの距離及び内歯車ＲRと遊星キャリヤＣRとの距離は等しく、これをａとする。また、太陽歯車ＳLと遊星キャリヤＣLとの距離及び太陽歯車ＳRと遊星キャリヤＣRとの距離も等しく、これをｂとする。遊星キャリヤＣL、ＣRから内歯車ＲL、ＲRまでの長さと遊星キャリヤＣL、ＣRから太陽歯車ＳL、ＳRまでの長さの比は、内歯車ＲL、ＲRの歯数Ｚｒの逆数（１／Ｚｒ）と太陽歯車ＳL、ＳRの歯数Ｚｓの逆数（１／Ｚｓ）との比と等しい。よって、ａ＝（１／Ｚｒ）、ｂ＝（１／Ｚｓ）と表すことができる。 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. 11, the internal 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).

ＲRの点を基準にしたモーメントＭの釣り合いから下記（１）式が算出される。なお、図１１において、矢印方向がモーメントＭの正方向である。
ａ・ＴＲ＋（ａ＋ｂ）・ＴＬ−（ｂ＋２ａ）・ＴＭ１＝０ …（１） The following equation (1) is calculated from the balance of moment M with reference to the point of R R. In FIG. 11, the arrow direction is the positive direction of the moment M.
a * TR + (a + b) * TL- (b + 2a) * TM1 = 0 (1)

ＲLの点を基準にしたモーメントＭの釣り合いから下記（２）式が算出される。
−ａ・ＴＬ−（ａ＋ｂ）・ＴＲ＋（ｂ＋２ａ）・ＴＭ２＝０ …（２） 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)

（１）式と（２）式の和より、下記（３）式が得られる。
−ｂ・（ＴＲ−ＴＬ）＋（２ａ＋ｂ）・（ＴＭ２−ＴＭ１）＝０
（ＴＲ−ＴＬ）＝（（２ａ＋ｂ）／ｂ）・（ＴＭ２−ＴＭ１） …（３） 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)

（３）式の（２ａ＋ｂ）／ｂがトルク差増幅率αとなる。ａ＝１／Ｚｒ、ｂ＝１／Ｚｓを代入すると、α＝（Ｚｒ＋２Ｚｓ）／Ｚｒとなり、下記のトルク差増幅率αが得られる。   (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   α = (Zr + 2Zs) / Zr

この発明では、電動モータ２Ｌ、２Ｒからの入力は、内歯車ＲL、ＲRとなり、駆動輪６１Ｌ、６１Ｒへの出力は太陽歯車ＳRと遊星キャリヤＣL、太陽歯車ＳLと遊星キャリヤＣRとなる。 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.

そして、二つの電動モータ２Ｌ、２Ｒで異なるトルクＴＭ１、ＴＭ２を発生させて入力トルク差ΔＴＩＮ（＝（ＴＭ２−ＴＭ１））を与えると、歯車装置３０において入力トルク差ΔＴＩＮが増幅され、入力トルク差ΔＴＩＮよりも大きな駆動トルク差α・ΔＴＩＮを得ることができる。すなわち、入力トルク差ΔＴＩＮが小さくても、歯車装置３０において上記したトルク差増幅率α（＝（Ｚｒ＋２Ｚｓ）／Ｚｒ）で入力トルク差ΔＴＩＮを増幅することができ、左駆動輪６１Ｌと右駆動輪６１Ｒとに伝達される駆動トルクＴＬ、ＴＲに、入力トルク差ΔＴＩＮよりも大きな駆動トルク差ΔＴＯＵＴ（＝α・（ＴＭ２−ＴＭ１）＝ＴＲ−ＴＬ）を与えることができる。   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.

図１及び図２に示す実施形態では、内歯車ＲL、ＲRに連結する入力側大径歯車１３ａは、内歯車ＲL、ＲRと一体に形成しているが、別体に形成してもよい。 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.

出力歯車軸１４Ｌ、１４Ｒは、図１に示すように、中空構造であり、この中空の出力歯車軸１４Ｌ、１４Ｒのアウトボード側の端部内周面に、等速ジョイント６５ａの外輪部材の軸部が挿入され、等速ジョイント６５ａの外輪部材の軸部と中空の出力歯車軸１４Ｌ、１４Ｒのアウトボード側の端部内周面とがスプライン結合（セレーション結合を含む）されている。   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).

次に、出力歯車軸１４Ｌ、１４Ｒに結合された等速ジョイント６５ａは、中間シャフト６５ｃ、等速ジョイント６５ａを介して駆動輪６１Ｌ、６１Ｒに接続される（図１０参照）。   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. 10).

出力歯車軸１４Ｌ、１４Ｒのアウトボード側の端部とモータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲに形成した開口部との間には、シール部材５５を設け、減速機３Ｌ、３Ｒに封入された潤滑油の漏洩を防止するとともに、外部から減速機３Ｌ、３Ｒの内部への埃や泥水の侵入を防止している。   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.

出力歯車軸１４Ｌ、１４Ｒは、大径の出力歯車１４ａを有し、減速機ハウジング９の仕切り壁１１の両面に形成した軸受嵌合穴５３ａとモータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲに形成した軸受嵌合穴５３ｂに転がり軸受５４ａ、５４ｂによって支持されている。図１及び図２では、転がり軸受５４ａ、５４ｂは同一のものとしているが、異なるサイズのものを組み合わせて使用してもよい。   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. 1 and 2, the rolling bearings 54a and 54b are the same, but different sizes may be used in combination.

遊星歯車装置３９Ｌ、３９Ｒの遊星歯車ＰL、ＰRは、図２に示すように、針状ころ軸受３７を介して歯車支持軸３３に回転自在に支持されている。歯車支持軸３３の両端は、遊星キャリヤＣL、ＣRの一対のキャリヤフランジ３４ａ、３４ｂに挿通固定されている。 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.

歯車支持軸３３の外周面は、遊星歯車ＰL、ＰRを回転自在に支持する針状ころ軸受３７の内輪軌道面になるため、高炭素クロム軸受鋼（ＳＵＪ２）のずぶ焼入れ・焼戻し、または浸炭鋼（ＳＣＭ４２０）の浸炭焼入れ・焼戻し等の、鋼を熱処理し表面硬さを５８ＨＲＣ以上とし、表面を内輪軌道面に適した粗さに研削して仕上げている。 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.

次に、遊星キャリヤＣL、ＣRのアウトボード側のキャリヤフランジ３４ａは、アウトボード側（車両の外側）に延びる中空軸部３５を備えており、中空軸部３５のアウトボード側の端部が、モータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲに形成した軸受嵌合穴１９ｂに転がり軸受２０ｂを介して支持されている。 Then, the carrier flange 34a of the planetary carrier C L, C R on the outboard side is the outboard side is provided with a hollow shaft portion 35 extending (outside the vehicle), the outboard side of the hollow shaft portion 35 end Is supported by a bearing fitting hole 19b formed in the inner side walls 4cL and 4cR of the motor housings 4L and 4R via a rolling bearing 20b.

遊星キャリヤＣL、ＣRのインボード側（車両の内側）のキャリヤフランジ３４ｂは、インボード側に延びる中空軸部３６を有する。この中空軸部３６は、減速機ハウジング９の仕切り壁１１に形成した軸受嵌合穴１９ａに転がり軸受２０ａを介して支持されている。 The carrier flange 34b on the inboard side (the inside of the vehicle) of the planetary carriers C L and C R has a hollow shaft portion 36 extending toward the inboard side. The hollow shaft portion 36 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.

また、遊星キャリヤＣL、ＣRのうち、右側の遊星キャリヤＣRのインボード側のキャリヤフランジ３４ｂの中空軸部３６の内径面に、中空の第２結合部材３２の右側端部がスプライン部７４によって連結されている。右側の遊星キャリヤＣRと第２結合部材３２は別体であり、インロウ部７８により芯出しされ、スプライン部７４に嵌合している。右側の遊星キャリヤＣRと第２結合部材３２は、一体としてもよい。第２結合部材３２の左側端部は、遊星キャリヤＣLのインボード側の端面との間に、潤滑油の流入隙間７２を介して対面している。 Further, the planet carrier C L, of C R, the inner surface of the hollow shaft portion 36 of the carrier flange 34b on the inboard side of the right-hand planet carrier C R, the right end portion spline portion of the hollow second coupling member 32 74 are connected. Right planet carrier C R and a second coupling member 32 are separate members, are centered by the spigot portion 78 is fitted to the spline portion 74. Right planet carrier C R and a second coupling member 32 may be integrated. Left end portion of the second coupling member 32, between the end face on the inboard side of the planet carrier C L, it is opposed via the inlet gap 72 of the lubricating oil.

この中空の第２結合部材３２は、左側端部に大径部７７を有し、この大径部７７の外周面に、左側の遊星歯車装置３９Ｌの遊星歯車ＰLと噛み合う外歯車が形成され、この外歯車が左側の遊星歯車装置３９Ｌの太陽歯車ＳLを構成している。 The second coupling member 32 of the hollow has a large diameter portion 77 at the left end, the outer peripheral surface of the large diameter portion 77, the external gear meshing with the planetary gears P L of the left planetary gear device 39L is formed the external gear constitutes the sun gear S L of the left side of the planetary gear unit 39L.

図１及び図２に示す実施形態では、前記出力側小径歯車１３ｂが、アウトボード側のキャリヤフランジ３４ａの中空軸部３５の外周面に一体に形成されているが、それぞれ別部材としてスプライン結合（セレーション結合を含む）としてもよい。   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).

内歯車ＲL、ＲRは、遊星キャリヤＣL、ＣRに対して左右２個の転がり軸受３９ａ、３９ｂによって支持されている。 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.

車両用駆動装置１の歯車装置３０を構成する２つの遊星歯車装置３９Ｌ、３９Ｒを連結している第１結合部材３１および第２結合部材３２は、減速機ハウジング９の仕切り壁１１を貫通して組み込まれている。   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.

この第１結合部材３１と第２結合部材３２は、同軸上に配置されると共に、一方の結合部材（図１及び図２の実施形態では第２結合部材３２）が中空軸、他方の結合部材（図１及び図２の実施形態では第１結合部材３１）が中空軸に挿通される軸からなる二重構造になっている。   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.

第１結合部材３１は、左側端部が、遊星キャリヤＣLのアウトボード側のキャリヤフランジ３４ａの中空軸部３５にスプライン部７３により連結されている。 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.

中空軸で構成される第２結合部材３２に挿通される第１結合部材３１は、右側端部に大径部７９を有し、この大径部７９の外周面に、右側の遊星歯車装置３９Ｒの遊星歯車ＰRと噛み合う外歯車が形成され、この外歯車が右側の遊星歯車装置３９Ｒの太陽歯車ＳRを構成している。 The first coupling member 31 inserted through the second coupling member 32 constituted by a hollow shaft has a large-diameter portion 79 at the right end, and a right planetary gear device 39R on the outer peripheral surface of the large-diameter portion 79. external gear meshing with the planetary gears P R is formed, the outer gear constitutes the sun gear S R of the right planetary gear 39R.

上記のように、２つの遊星歯車装置３９Ｌ、３９Ｒの第１結合部材３１を、遊星キャリヤＣLに対しスプライン部７３によって連結することにより、２つの遊星歯車装置３９Ｌ、３９Ｒを左右に分割することが可能となり、２つの遊星歯車装置３９Ｌ、３９Ｒを減速機ハウジング９に他の減速歯車軸と一緒に左右から組込むことができる。 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.

２つの遊星歯車装置３９Ｌ、３９Ｒを連結する二重構造の軸の内径側の第１結合部材３１は、遊星歯車装置３９Ｌ側の端部が、遊星キャリヤＣLのアウトボード側のキャリヤフランジ３４ａの中空軸部３５にスプライン部７３によって結合され、遊星歯車装置３９Ｒ側の端部が、遊星キャリヤＣRのアウトボード側のキャリヤフランジ３４ａの中空軸部３５に転がり軸受４９によって支持されている。この転がり軸受４９は、開放型の深溝玉軸受によって構成することができる。 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 side, of the planet carrier C L on the outboard side of the carrier flange 34a the hollow shaft portion 35 are joined 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.

一対のキャリヤフランジ３４ａ、３４ｂと遊星歯車ＰL、ＰRの間には、遊星歯車ＰL、ＰRの回転を円滑化するために、歯車支持軸３３が内部を通る形のスラスト板３８を装着している。 A pair of carrier flanges 34a, 34b and the planetary gears P L, between P R, the planetary gear P L, in order to facilitate the rotation of the P R, the thrust plate 38 in the form of gear support shaft 33 passes through the interior Wearing.

転がり軸受４９として開放型の深溝玉軸受を使用することにより、図４に太線矢印で示すように、右側の遊星キャリヤＣRのアウトボード側のキャリヤフランジ３４ａの中空軸部３５内に流入した潤滑油が、転がり軸受４９を通って、キャリヤフランジ３４ａと遊星歯車ＰRの間に挿入したスラスト板３８の外周に供給される。 By using an open deep groove ball bearing as a rolling bearing 49, as shown by the thick arrow in FIG. 4, 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.

ところで、図１に示すように、入力歯車軸１２Ｌ、１２Ｒ、中間歯車軸１３Ｌ、１３Ｒ、出力歯車軸１４Ｌ、１４Ｒは、減速機ハウジング９に収容されいる。図５は、右側の入力歯車軸１２Ｒ、中間歯車軸１３Ｒ、出力歯車軸１４Ｒを示しているが、左側の入力歯車軸１２Ｌ、中間歯車軸１３Ｌ、出力歯車軸１４Ｌも配置は同じである。即ち、図５に示すように、歯車装置３０を組み込んだ中間歯車軸１３Ｌ、１３Ｒが最も低位置になるように配置され、減速機ハウジング９の下部に油溜まり８７が設けられている。減速機ハウジング９の下部の油溜まり８７の油面高さＨは、車両の停止時に中間歯車軸１３Ｌ、１３Ｒを減速機ハウジング９に対して支持する転がり軸受２０ａ、２０ｂの軌道面が潤滑油に浸かるように設定され、油浴潤滑や歯車の回転による跳ね掛け潤滑が行われるようになっている。   By the way, as shown in FIG. 1, 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. FIG. 5 shows the right input gear shaft 12R, intermediate gear shaft 13R, and output gear shaft 14R, but the left input gear shaft 12L, intermediate gear shaft 13L, and output gear shaft 14L are arranged in the same manner. That is, as shown in FIG. 5, the intermediate gear shafts 13 </ b> L and 13 </ b> R incorporating the gear device 30 are disposed at the lowest position, and an oil sump 87 is provided at the lower portion of the speed reducer housing 9. The oil level height H of the oil sump 87 at the lower part of the reduction gear housing 9 is such that the raceway surfaces of the rolling bearings 20a and 20b that support the intermediate gear shafts 13L and 13R with respect to the reduction gear housing 9 when the vehicle is stopped are lubricated. It is set so as to be soaked, and oil bath lubrication and splash lubrication by rotation of gears are performed.

２個の遊星歯車装置３９Ｌ、３９Ｒを同軸で結合した歯車装置３０においては、図５に示すように、車両の停止時に転がり軸受２０ａ、２０ｂが潤滑油に浸かるように、減速機ハウジング９の下部の油溜まり８７の油面高さＨを設定していても、歯車装置３０の内歯車ＲL、ＲRも中間歯車軸１３Ｌ、１３Ｒの大歯車として回転するため、回転する内歯車ＲL、ＲRが減速機ハウジング９の下部に溜められた潤滑油を掻き分けてしまい、特に、車両の高速走行時は中間歯車軸１３Ｌ、１３Ｒを支持する転がり軸受２０ａ、２０ｂの軌道面が潤滑油に浸からない状態になる。 In the gear unit 30 in which the two planetary gear units 39L and 39R are coaxially coupled, as shown in FIG. 5, the lower part of the speed reducer housing 9 is arranged so that the rolling bearings 20a and 20b are immersed in the lubricating oil when the vehicle is stopped. even if you set the oil level height H of the oil sump 87, the internal gear R L of the gear device 30, to rotate also R R intermediate gear shaft 13L, as a large gear 13R, 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, the rolling bearing 20a at high speeds of the vehicle for supporting the intermediate gear shaft 13L, the 13R, raceways 20b is immersed in lubricating oil It becomes a state not to be.

減速機ハウジング９の下部の油溜まり８７から歯車の回転で掻き上げられ飛散した潤滑油は、減速機ハウジング９の内壁に付着し、内壁に設けられたリブ（図示省略）に沿って流れ落ち、図３及び図４に太線矢印で示すように、遊星歯車装置３９Ｌ、３９Ｒの遊星キャリヤＣL、ＣRのアウトボード側のキャリヤフランジ３４ａの中空軸部３５を支持する転がり軸受２０ｂを通って、中空軸部３５内に潤滑油が流入する。 Lubricating oil that has been scraped and scattered from the oil reservoir 87 at the lower part of the reducer housing 9 adheres to the inner wall of the reducer housing 9 and flows down along ribs (not shown) provided on the inner wall. 3 and as indicated by the thick arrow in FIG. 4, 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.

一方、右側の遊星歯車装置３９Ｒの遊星キャリヤＣRのアウトボード側のキャリヤフランジ３４ａの中空軸部３５の内部に流入した潤滑油は、図４の太線矢印で示すように、キャリヤフランジ３４ａの中空軸部３５に対して第１結合部材３１の右側端部を支持する転がり軸受４９の内部を通って、キャリヤフランジ３４ａと遊星歯車ＰRの間に挿入したスラスト板３８の外周に供給される。 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. 4, 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.

ところで、図１及び図２に示す実施形態では、歯車装置３０の軸方向寸法を小さくするために、遊星キャリヤＣL、ＣRのインボード側の側面に凹部８０を設け、この凹部８０内に、遊星キャリヤＣL、ＣRの両端を支持する転がり軸受２０ａ、２０ｂのうち、インボード側の転がり軸受２０ａの一部が嵌り、インボード側の転がり軸受２０ａと、内歯車ＲL、ＲRを遊星キャリヤＣL、ＣRに対して支持する転がり軸受３９ａ、３９ｂのインボード側の転がり軸受３９ｂとが軸方向で一部が重なるように配置されている。 In the meantime, in the embodiment shown in FIGS. 1 and 2, in order to reduce the axial dimension of the gear device 30, a concave portion 80 is provided on the inboard side surface of the planetary carriers C L and C R , and the concave portion 80 is provided in the concave portion 80. Among the rolling bearings 20a and 20b that support both ends of the planet carriers C L and C R , a part of the in-board side rolling bearing 20a is fitted, and the in-board side rolling bearing 20a and the internal gears R L and R R are fitted. The rolling bearings 39a and 39b that support the rotating bearings 39a and 39b with respect to the planetary carriers C L and C R are arranged so as to partially overlap in the axial direction.

このように、インボード側の転がり軸受２０ａの一部を、遊星キャリヤＣL、ＣRのインボード側の側面の凹部８０に嵌め入れると、油浴潤滑や歯車の回転による跳ね掛け潤滑では、インボード側の転がり軸受２０ａに潤滑油が供給され難くなる。 In this way, when a part of the inboard side rolling bearing 20a is fitted into the concave portion 80 on the inboard side of the planetary carriers C L and C R , in oil bath lubrication and splash lubrication by rotation of gears, Lubricating oil is difficult to be supplied to the inboard rolling bearing 20a.

このため、この発明では、歯車装置３０を支持する転がり軸受２０ａ、２０ｂのうち、油浴潤滑や歯車の回転による跳ね掛け潤滑によって潤滑油が供給され難いインボード側の転がり軸受２０ａに対し、潤滑油が供給されるように、潤滑油の供給経路を次のようにして確保している。   Therefore, according to the present invention, among the rolling bearings 20a and 20b that support the gear device 30, the inboard rolling bearing 20a that is difficult to be supplied with lubricating oil by oil bath lubrication or splash lubrication by rotation of the gear is lubricated. In order to supply the oil, the supply path of the lubricating oil is secured as follows.

まず、第１結合部材３１に、軸心給油の油路となる、軸方向穴８１と位相違いの複数の径方向穴８２、８３を設けている。   First, the first coupling member 31 is provided with a plurality of radial holes 82 and 83 that are out of phase with the axial hole 81 and serve as an oil passage for the axial center oil supply.

そして、中空軸で構成された第２結合部材３２にも位相違いの複数の径方向穴８４を設けている。   A plurality of radial holes 84 having different phases are also provided in the second coupling member 32 formed of a hollow shaft.

第１結合部材３１に設ける軸方向穴８１は、一端が遊星キャリヤＣL、ＣRのアウトボード側のキャリヤフランジ３４ａからアウトボード側（車両の外側）に延びる中空軸部３５に開口するように設けられている。図１及び図２の実施形態では、軸方向穴８１の一端が、遊星キャリヤＣLのアウトボード側のキャリヤフランジ３４ａの中空軸部３５に開口している。 Axial bore 81 provided in the first coupling member 31, so as to open into the hollow shaft 35 having one end extending from the planet carrier C L, C R on the outboard side of the carrier flange 34a on the outboard side (outside of the vehicle) Is provided. In the embodiment of FIGS. 1 and 2, one end of the axial bore 81 is open to the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the planet carrier C L.

第１結合部材３１に設けられた軸方向穴８１は、その他端が、遊星キャリヤＣLのインボード側のキャリヤフランジ３４ｂのインボード側に延びる中空軸部３６を越えるように設けられている。 Axial bore 81 provided in the first coupling member 31 has its other end is provided so as to exceed the hollow shaft portion 36 extending inboard side of the carrier flange 34b on the inboard side of the planet carrier C L.

第１結合部材３１に設けられる径方向穴８２、８３のうち、アウトボード側の径方向穴８２は、第２結合部材３２の左側端部と遊星キャリヤＣLのキャリヤフランジ３４ａのインボード側の端面との間に設けた流入隙間７２に開口するように設けられている。 Of radial holes 82, 83 provided on the first coupling member 31, the radial bore 82 of the outboard side, the inboard side of the carrier flange 34a of the left end portion and the planet carrier C L of the second coupling member 32 It is provided so that it may open to the inflow gap 72 provided between the end surfaces.

第１結合部材３１に設けられる他方の径方向穴８３は、左右の遊星キャリヤＣL、ＣRの中間位置に開口するように設けらている。 The other radial hole 83 provided in the first coupling member 31 is provided so as to open at an intermediate position between the left and right planetary carriers C L and C R.

第１結合部材３１に設けられる径方向穴８２、８３は、１８０°、１２０°、９０°等の等配位置に開けられいる。図１及び図２に示す実施形態では、第１結合部材３１に設けられる径方向穴８３は、図７に示すように、１８０°の対向位置に開けられている。   The radial holes 82 and 83 provided in the first coupling member 31 are opened at equal positions such as 180 °, 120 °, and 90 °. In the embodiment shown in FIGS. 1 and 2, the radial hole 83 provided in the first coupling member 31 is opened at an opposing position of 180 ° as shown in FIG. 7.

第１結合部材３１に設けられる径方向穴８３は、径方向穴８３から供給された潤滑油が第２結合部材３２の内周面へ飛散し、第２結合部材３２の径方向穴８４を経由して遊星キャリヤＣL、ＣRのインボード側の転がり軸受２０ａへ飛散しやすいように、第１結合部材３１の径方向穴８３の軸方向位置は、第２結合部材３２の径方向穴８４の近傍に設けられる。 In the radial hole 83 provided in the first coupling member 31, the lubricating oil supplied from the radial hole 83 scatters to the inner peripheral surface of the second coupling member 32 and passes through the radial hole 84 of the second coupling member 32. Thus, the axial position of the radial hole 83 of the first coupling member 31 is set to the radial hole 84 of the second coupling member 32 so that the planetary carriers C L and C R are easily scattered to the rolling bearing 20a on the inboard side. It is provided in the vicinity.

第２結合部材３２に設けられる径方向穴８４は、左右の遊星キャリヤＣL、ＣRのインボード側の中空軸部３６の間に位置するように設けられている。 The radial hole 84 provided in the second coupling member 32 is provided so as to be positioned between the hollow shaft portions 36 on the inboard side of the left and right planetary carriers C L and C R.

第２結合部材３２に設けられる径方向穴８４は、１８０°、１２０°、９０°等の等配位置に開けられている。図１及び図２に示す実施形態では、第２結合部材３２に設けられる径方向穴８４は、図７に示すように、１８０°の対向位置に開けられている。   The radial holes 84 provided in the second coupling member 32 are opened at equal positions such as 180 °, 120 °, and 90 °. In the embodiment shown in FIGS. 1 and 2, the radial hole 84 provided in the second coupling member 32 is opened at an opposing position of 180 ° as shown in FIG. 7.

この第２結合部材３２に設けられる径方向穴８４の軸方向位置は、インボード側の転がり軸受２０ａの内部に潤滑油が流入し易いよう、転がり軸受２０ａの近傍の位置とする。   The axial position of the radial hole 84 provided in the second coupling member 32 is a position in the vicinity of the rolling bearing 20a so that the lubricating oil can easily flow into the inboard-side rolling bearing 20a.

例えば、インボード側の転がり軸受２０ａの２個の転動体の中心間の位置、即ち図６のＡの範囲内に径方向穴８４を配置するのが良い。   For example, the radial hole 84 may be arranged at a position between the centers of the two rolling elements of the inboard side rolling bearing 20a, that is, within the range of A in FIG.

さらに、インボード側の転がり軸受２０ａの内部に潤滑油がより流入し易いよう、第２結合部材３２の径方向穴８４の軸方向位置を、インボード側の転がり軸受２０ａのインボード側の端面間、即ち、図６のＢの範囲内に配置するのが良い。   Further, the axial position of the radial hole 84 of the second coupling member 32 is set to the end face on the inboard side of the inboard side rolling bearing 20a so that the lubricating oil more easily flows into the inboard side rolling bearing 20a. It is good to arrange between them, that is, within the range of B in FIG.

また、インボード側の転がり軸受２０ａの内部にさらに飛散しやすいよう、第２結合部材３２の径方向穴８４の開口部の少なくとも一部が、遊星キャリヤＣL、ＣRのインボード側端部間、即ち、図６のＣの範囲に位置することが望ましい。 Also, to further easily scattered inside the inboard side of the rolling bearing 20a, at least a part of the opening of the radial holes 84 of the second coupling member 32, planet carrier C L, inboard-side end portion of the C R It is desirable to be in the middle, that is, in the range of C in FIG.

第２結合部材３２の内周面に、径方向穴８４を含むように周方向溝８５を設けてもよい。第１結合部材３１の径方向穴８３から飛散した潤滑油を周方向溝８５に集めることができるので、第２結合部材３２の径方向穴８４へ効率よく流すことが可能となる。   A circumferential groove 85 may be provided on the inner peripheral surface of the second coupling member 32 so as to include the radial hole 84. Since the lubricating oil splashed from the radial hole 83 of the first coupling member 31 can be collected in the circumferential groove 85, it can be efficiently flowed to the radial hole 84 of the second coupling member 32.

次に、減速機ハウジング９の内壁、リブ（図示省略）に沿って流れる潤滑油を、より多く受け止めて、遊星キャリヤＣL、ＣRのアウトボード側のキャリヤフランジ３４ａの中空軸部３５内に供給できるように、中間歯車軸１３Ｌ、１３Ｒのアウトボード側の端部を支持する、モータハウジング４Ｌ、４Ｒの内側壁４ｃＬ、４ｃＲの軸受嵌合穴１９ｂに切欠き部１９ｃを設け、図３及び図４に太線矢印で示すように、減速機ハウジング９の内壁、リブに沿って流れる潤滑油を、切欠き部１９ｃから中間歯車軸１３Ｌ、１３Ｒのアウトボード側の中空軸部３５の側面に流れ込み易くしている。 Then, the inner wall of the reducer housing 9, the lubricating oil flowing along the ribs (not shown), more and receiving, planet carrier C L, the hollow shaft portion 35 of the carrier flange 34a on the outboard side of the C R A notch portion 19c is provided in the bearing fitting hole 19b of the inner wall 4cL, 4cR of the motor housing 4L, 4R that supports the end portion on the outboard side of the intermediate gear shafts 13L, 13R so that it can be supplied. As shown by the thick arrow in FIG. 4, the lubricating oil flowing along the inner wall and rib of the reducer housing 9 flows into the side surface of the hollow shaft portion 35 on the outboard side of the intermediate gear shafts 13L and 13R from the notch portion 19c. It is easy.

さらに、中間歯車軸１３Ｌ、１３Ｒのアウトボード側の中空軸部３５の開口が対向する内側壁４ｃＬ、４ｃＲに、内側壁４ｃＬ、４ｃＲに沿って流れ込んだ潤滑油を受け、中空軸部３５の内部に潤滑油を導く導油部材８６を取付けている。   Further, the inner wall 4cL, 4cR facing the opening of the hollow shaft portion 35 on the outboard side of the intermediate gear shafts 13L, 13R receives the lubricating oil flowing along the inner wall 4cL, 4cR, and the inside of the hollow shaft portion 35 An oil guide member 86 that guides the lubricating oil is attached.

導油部材８６は、図８及び図９に示すように、内側壁４ｃＬ、４ｃＲにねじ固定され、上面に漏斗形状の受け部８６ａを有する受け板８６ｂと、受け部８６ａの底部に連通し、受け部８６ａに流れ込んで集油された潤滑油を、中間歯車軸１３Ｌ、１３Ｒの中空軸部３５の軸方向の内部に導く導油管８６ｃとからなる。   As shown in FIGS. 8 and 9, the oil guide member 86 is screwed to the inner side walls 4cL and 4cR and communicates with a receiving plate 86b having a funnel-shaped receiving portion 86a on the upper surface and a bottom portion of the receiving portion 86a. The oil guide pipe 86c guides the lubricating oil collected by flowing into the receiving portion 86a to the inside of the hollow shaft portion 35 of the intermediate gear shafts 13L and 13R.

左側の導油部材８６の導油管８６ｃは、右側の端部が第１結合部材３１に設けられた軸方向穴８１内に挿入され、導油部材８６によって集油した潤滑油を導油管８６ｃによって第１結合部材３１の軸方向穴８１内に供給している。   The oil guide pipe 86c of the left oil guide member 86 has a right end inserted into an axial hole 81 provided in the first coupling member 31, and the lubricating oil collected by the oil guide member 86 is collected by the oil guide pipe 86c. This is supplied into the axial hole 81 of the first coupling member 31.

左側の遊星歯車装置３９Ｌでは、図３に太線矢印で示すように、減速機ハウジング９の内壁、リブに沿って流れる潤滑油は、軸受嵌合穴１９ｂに設けた切欠き部１９ｃからモータハウジング４Ｌの内側壁４ｃＬに取付けた導油部材８６の受け部８６ａに流入する。導油部材８６の受け部８６ａに流入して集油された潤滑油は、導油管８６ｃを通って、第１結合部材３１の軸方向穴８１の内部に導かれる。第１結合部材３１の軸方向穴８１の内部に供給された潤滑油は、その後、第１結合部材３１の左側の径方向穴８２から第２結合部材３２の左側端部と遊星キャリヤＣLのキャリヤフランジ３４ａのインボード側の端面との間に設けた流入隙間７２から遊星歯車ＰLに供給され、遊星歯車ＰLの内部と外部の歯車の歯面を潤滑する。さらに、第１結合部材３１の軸方向穴８１の内部に供給された潤滑油は、インボード側の径方向穴８３から第２結合部材３２の内周面に飛散し、第２結合部材３２の内周面に飛散した潤滑油が、さらに第２結合部材３２の径方向穴８４から飛散し、二つの遊星歯車装置３９Ｌ、３９Ｒのインボード側の遊星キャリヤ３４ｂを支持する転がり軸受２０ａに供給される。これにより、遊星キャリヤ３４ｂを支持する転がり軸受２０ａが潤滑不良によって早期に破損したり、異音が生じたりするということを防止することができる。 In the planetary gear device 39L on the left side, as shown by a thick arrow in FIG. 3, the lubricating oil flowing along the inner wall and rib of the speed reducer housing 9 flows from the notch 19c provided in the bearing fitting hole 19b to the motor housing 4L. Flows into the receiving portion 86a of the oil guide member 86 attached to the inner wall 4cL. The lubricating oil collected by flowing into the receiving portion 86a of the oil guide member 86 is guided into the axial hole 81 of the first coupling member 31 through the oil guide pipe 86c. Inside supplied lubricating oil axial hole 81 of the first coupling member 31 is then in the radial direction hole 82 of the left side of the first coupling member 31 of the left end portion and the planet carrier C L of the second coupling member 32 is supplied from the inlet gap 72 provided between the inboard side end face of the carrier flange 34a on the planetary gear P L, for lubricating the inner and tooth surfaces of the external gear of the planetary gear P L. Further, the lubricating oil supplied to the inside of the axial hole 81 of the first coupling member 31 scatters from the radial hole 83 on the inboard side to the inner peripheral surface of the second coupling member 32, and The lubricating oil scattered on the inner peripheral surface is further scattered from the radial hole 84 of the second coupling member 32, and is supplied to the rolling bearing 20a that supports the planet carrier 34b on the inboard side of the two planetary gear devices 39L and 39R. The As a result, it is possible to prevent the rolling bearing 20a supporting the planet carrier 34b from being damaged early due to poor lubrication or abnormal noise.

他方の右側の遊星歯車装置３９Ｒでは、図４に太線矢印で示すように、減速機ハウジング９の内壁、リブに沿って流れる潤滑油は、軸受嵌合穴１９ｂに設けた切欠き部１９ｃから内側壁４ｃＲに取付けた導油部材８６の受け部８６ａに流入する。導油部材８６の受け部８６ａに流入した潤滑油は、導油管８６ｃを通って、キャリヤフランジ３４ａの中空軸部３５の内部に導かれ、その後、第１結合部材３１の右側端部を支持する転がり軸受４９内を通り、キャリヤフランジ３４ａと遊星歯車ＰRの間に挿入したスラスト板３８の外周に供給され、遊星歯車ＰRの内部と外部の歯車の歯面を潤滑する。 In the other planetary gear unit 39R on the right side, as indicated by a thick arrow in FIG. 4, the lubricating oil flowing along the inner wall and rib of the reducer housing 9 flows from the notch 19c provided in the bearing fitting hole 19b. It flows into the receiving portion 86a of the oil guide member 86 attached to the wall 4cR. The lubricating oil flowing into the receiving portion 86a of the oil guiding member 86 is guided to the inside of the hollow shaft portion 35 of the carrier flange 34a through the oil guiding tube 86c, and then supports the right end of the first coupling member 31. through the rolling bearing 49, it is supplied to the inserted outer periphery of the thrust plate 38 between the carrier flange 34a and the planetary gear P R, to lubricate the inside and the tooth surface of the external gear of the planetary gear P R.

以上の実施形態では、二つの駆動源として電動モータ２Ｌ、２Ｒを用い、同一の最大出力を有する同一出力特性の電動モータである場合を例示したが、二つの駆動源はこれに限られない。   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.

また、以上の実施形態では、トルク差増幅機構を構成する歯車装置３０は平行軸歯車減速機の中間歯車軸１３Ｌ、１３Ｒに位置するが、中間歯車軸１３Ｌ、１３Ｒ（大歯車を構成する大径の入力側大径歯車１３ａと小歯車を構成する出力側小径歯車１３ｂが同軸にある軸）は複数あってもよく、そのうちの１軸にトルク差増幅機構である歯車装置３０を組み込むことができる。   Further, 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 large diameter constituting the large gear). The input side large-diameter gear 13a and the output-side small-diameter gear 13b constituting the small gear may have a plurality of axes), and a gear device 30 that is a torque difference amplifying mechanism can be incorporated in one of them. .

なお、車両用駆動装置１が搭載される車両は、電気自動車やハイブリッド電気自動車に限られず、例えば、第１の電動モータ２Ｌ及び第２の電動モータ２Ｒを駆動源とした燃料電池自動車であってもよい。   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.

この発明は前述した実施形態に何ら限定されるものではなく、この発明の要旨を逸脱しない範囲において、さらに種々の形態で実施し得る。   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 ：車両用駆動装置
２Ｌ、２Ｒ ：電動モータ
３Ｌ、３Ｒ ：減速機
４Ｌ、４Ｒ ：モータハウジング
４ａＬ、４ａＲ ：モータハウジング本体
４ｂＬ、４ｂＲ ：外側壁
４ｃＬ、４ｃＲ ：内側壁
５ ：ロータ
５ａ ：モータ軸
６ ：ステータ
７ ：シール部材
８ａ、８ｂ ：転がり軸受
９ ：減速機ハウジング
１１ ：仕切り壁
１２Ｌ、１２Ｒ ：入力歯車軸
１２ａ ：入力歯車
１３Ｌ、１３Ｒ ：中間歯車軸
１３ａ ：入力側大径歯車
１３ｂ ：出力側小径歯車
１４Ｌ、１４Ｒ ：出力歯車軸
１４ａ ：出力歯車
１６ａ、１６ｂ ：軸受嵌合穴
１７ａ、１７ｂ ：転がり軸受
１９ａ、１９ｂ ：軸受嵌合穴
１９ｃ ：切欠き部
２０ａ、２０ｂ ：転がり軸受
３０ ：歯車装置
３１ ：第１結合部材
３２ ：第２結合部材
３３ ：歯車支持軸
３４ａ、３４ｂ ：キャリヤフランジ
３５、３６ ：中空軸部
３７ ：軸受
３８ ：スラスト板
３９Ｌ、３９Ｒ ：遊星歯車装置
３９ａ、３９ｂ、４９ ：転がり軸受
５３ａ、５３ｂ ：軸受嵌合穴
５４ａ、５４ｂ ：転がり軸受
５５ ：シール部材
６０ ：シャーシ
６１Ｌ、６１Ｒ ：駆動輪
６２Ｌ、６２Ｒ ：前輪
６３ ：バッテリ
６４ ：インバータ
６５ａ、６５ｂ ：等速ジョイント
６５ｃ ：中間シャフト
７２ ：流入隙間
７３、７４ ：スプライン部
７７ ：大径部
７８ ：インロウ部
７９ ：大径部
８０ ：凹部
８１ ：軸方向穴
８２、８３、８４ ：径方向穴
８５ ：周方向溝
８６ ：導油部材
８６ａ ：受け部
８６ｂ ：受け板
８６ｃ ：導油管
８７ ：油溜まり
ＡＭ ：電気自動車
ＣＬ、ＣＲ ：遊星キャリヤ
ＰＬ、ＰＲ ：遊星歯車
ＲＬ、ＲＲ ：内歯車
ＳＬ、ＳＲ ：太陽歯車 1: Vehicle drive device 2L, 2R: 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 33: Gear support shafts 34a, 34b: Carrier flange 3 5, 36: Hollow shaft portion 37: Bearing 38: Thrust plates 39L, 39R: Planetary gear devices 39a, 39b, 49: Rolling bearings 53a, 53b: Bearing fitting holes 54a, 54b: Rolling bearing 55: Seal member 60: Chassis 61L, 61R: Drive wheel 62L, 62R: Front wheel 63: Battery 64: Inverter 65a, 65b: Constant velocity joint 65c: Intermediate shaft 72: Inflow gap 73, 74: Spline portion 77: Large diameter portion 78: In-row portion 79: Large Diameter portion 80: Recessed portion 81: Axial holes 82, 83, 84: Radial direction hole 85: Circumferential groove 86: Oil guide member 86a: Receiving portion 86b: Receiving plate 86c: Oil guide pipe 87: Oil reservoir AM: Electric vehicle CL , CR: planetary carrier PL, PR: planetary gear RL, RR: internal gear SL, SR: sun gear

Claims (5)

車両に搭載され車輪を駆動する独立して制御可能な二つの電動モータと、二つの電動モータと二つの出力部との間に設けられ、二つの電動モータからのトルクを二つの出力部に分配する歯車装置と、二つの電動モータのトルクを二つの出力部に伝達する減速機とを備える車両用駆動装置において、減速機は、電動モータに連結し、入力歯車を有する入力歯車軸と、出力部に連結し、出力歯車を有する出力歯車軸と、歯車の噛合いにより入力歯車軸から出力歯車軸の間のトルク伝達を行う中間歯車軸が少なくとも1つ以上備え、歯車装置は、同軸に設けられた左右の1対の中間歯車軸と同軸上に二つ組み合わせた３要素２自由度の遊星歯車装置からなり、この遊星歯車装置は、内歯車と、内歯車と同軸上に設けられた遊星キャリヤと、内歯車と同軸上に設けられた太陽歯車と、公転歯車としての複数の遊星歯車とを備え、二つの遊星歯車装置の一方の遊星キャリヤと他方の太陽歯車とを結合する第１結合部材と、一方の太陽歯車と他方の遊星キャリヤとを結合する第２結合部材とを有し、第２結合部材は中空軸であり、第１結合部材は第２結合部材に内包され、第１結合部材と第２結合部材で二重軸となり、歯車装置の二つの遊星歯車機構の遊星キャリヤは、それぞれが両端を転がり軸受を介して減速機ハウジングに支持され、減速機の潤滑機構が、減速機ハウジング下部に溜まった潤滑油を歯車の回転により飛散させて潤滑する跳ね掛け潤滑であり、第１結合部材に軸心給油の油路となる軸方向穴と位相違いの複数の径方向穴を設け、中空軸からなる第２結合部材に位相違いの複数の径方向穴を設け、第１結合部材に設けられた軸方向穴の端面に対面する減速機ハウジングの壁面に、減速機ハウジングの壁面を流れる潤滑油を集油し、第１結合部材の軸方向穴内に潤滑油を供給する導油部材を設け、導油部材から第１結合部材の軸方向穴内に供給された潤滑油を、第１結合部材に設けた径方向穴から外側の第２結合部材の内周面に給油し、第２結合部材の内周面に給油された潤滑油を、二つの遊星歯車装置の遊星キャリヤの両端を支持する転がり軸受のうちのインボード側の転がり軸受に対し第２結合部材に設けた径方向穴から給油するようにしたことを特徴とする車両用駆動装置。   Installed between two independently controllable electric motors mounted on the vehicle to drive the wheels and between the two electric motors and the two output units, the torque from the two electric motors is distributed to the two output units And a reduction gear that transmits the torque of two electric motors to two output portions. The reduction gear is connected to the electric motor, has an input gear shaft having an input gear, and an output. And an output gear shaft having an output gear and at least one intermediate gear shaft for transmitting torque between the input gear shaft and the output gear shaft by meshing of the gear, and the gear device is provided coaxially It consists of a three-element two-degree-of-freedom planetary gear device that is coaxially combined with a pair of left and right intermediate gear shafts, and this planetary gear device is composed of an inner gear and a planetary gear that is provided coaxially with the inner gear. Same as carrier and internal gear A first coupling member that includes a sun gear provided on the top and a plurality of planetary gears as revolution gears, and that couples one planetary carrier of the two planetary gear devices and the other sun gear, and one sun gear And a second coupling member for coupling the other planet carrier, the second coupling member is a hollow shaft, the first coupling member is contained in the second coupling member, and the first coupling member and the second coupling member The planetary carrier of the two planetary gear mechanisms of the gear unit is supported by the reducer housing via rolling bearings at both ends, and the lubrication mechanism of the reducer accumulates in the lower part of the reducer housing. Splash lubrication in which oil is scattered by rotation of gears and lubricated, and the first coupling member is provided with a plurality of radial holes that are out of phase with an axial hole that serves as an oil passage for axially-centered oil supply, and is a hollow shaft. Multiple diameters with different phases in 2 coupling members In the axial hole of the first coupling member, the lubricating oil flowing through the wall surface of the reduction gear housing is collected on the wall surface of the reduction gear housing facing the end surface of the axial hole provided in the first coupling member. An oil guide member for supplying lubricating oil is provided, and the lubricant oil supplied from the oil guide member into the axial hole of the first connecting member is supplied to the outer side of the second connecting member from the radial hole provided in the first connecting member. Lubricating oil supplied to the inner peripheral surface and supplied to the inner peripheral surface of the second coupling member is compared with the rolling bearing on the inboard side of the rolling bearings that support both ends of the planetary carriers of the two planetary gear devices. 2. A vehicle drive device characterized in that oil is supplied from a radial hole provided in a coupling member. 第２結合部材に設けた径方向穴の軸方向位置が、歯車装置を構成する二つの遊星歯車機構のインボード側の遊星キャリヤを減速機ハウジングに対して支持する二つの転がり軸受の転動体間の中心位置にあることを特徴とする請求項１記載の車両用駆動装置。   The axial position of the radial hole provided in the second coupling member is between the rolling elements of the two rolling bearings that support the planetary carrier on the inboard side of the two planetary gear mechanisms constituting the gear device with respect to the reduction gear housing. The vehicle drive device according to claim 1, wherein the vehicle drive device is located at the center position of the vehicle. 第２結合部材に設けた径方向穴の軸方向位置が、歯車装置を構成する二つの遊星歯車機構のインボード側の遊星キャリヤを減速機ハウジングに対して支持する二つの転がり軸受のインボード側の端面間に位置することを特徴とする請求項１記載の車両用駆動装置。   The axial position of the radial hole provided in the second coupling member is the inboard side of the two rolling bearings that support the planetary carrier on the inboard side of the two planetary gear mechanisms constituting the gear device with respect to the reduction gear housing. The vehicle drive device according to claim 1, wherein the vehicle drive device is located between the end faces of the vehicle. 第２結合部材に設けた径方向穴の開口部の少なくとも一部が、歯車装置を構成する二つの遊星歯車機構のインボード側の遊星キャリヤの端面間に位置することを特徴とする請求項１記載の車両用駆動装置。   The at least part of the opening of the radial hole provided in the second coupling member is located between the end faces of the planet carrier on the inboard side of the two planetary gear mechanisms constituting the gear device. The vehicle drive device as described. 第二結合部材の内周面に、前記径方向穴を含むように周方向溝を設けたことを特徴とする請求項１〜４のいずれかに記載の車両用駆動装置。   The vehicle drive device according to claim 1, wherein a circumferential groove is provided on an inner circumferential surface of the second coupling member so as to include the radial hole.
JP2016192398A 2016-09-30 2016-09-30 Vehicle drive device Pending JP2018054053A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111577880A (en) * 2020-06-01 2020-08-25 江苏行星重载齿轮箱有限公司 Lubricating system of planetary gear box
WO2020179203A1 (en) * 2019-03-06 2020-09-10 三菱自動車工業株式会社 Left-right wheel drive device
WO2020194950A1 (en) * 2019-03-28 2020-10-01 三菱自動車工業株式会社 Left-right wheel drive device
CN112145658A (en) * 2020-08-26 2020-12-29 东风汽车集团有限公司 Gearbox jackshaft structure
CN113757347A (en) * 2021-08-18 2021-12-07 浙江夏厦精密制造股份有限公司 Speed reducer for electric automobile

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020179203A1 (en) * 2019-03-06 2020-09-10 三菱自動車工業株式会社 Left-right wheel drive device
JPWO2020179203A1 (en) * 2019-03-06 2021-12-02 三菱自動車工業株式会社 Left and right wheel drive
WO2020194950A1 (en) * 2019-03-28 2020-10-01 三菱自動車工業株式会社 Left-right wheel drive device
JPWO2020194950A1 (en) * 2019-03-28 2021-11-25 三菱自動車工業株式会社 Left and right wheel drive
CN111577880A (en) * 2020-06-01 2020-08-25 江苏行星重载齿轮箱有限公司 Lubricating system of planetary gear box
CN112145658A (en) * 2020-08-26 2020-12-29 东风汽车集团有限公司 Gearbox jackshaft structure
CN113757347A (en) * 2021-08-18 2021-12-07 浙江夏厦精密制造股份有限公司 Speed reducer for electric automobile

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