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

Planetary gear device and driving device for vehicle using the same Download PDF

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JP2018048685A
JP2018048685A JP2016183771A JP2016183771A JP2018048685A JP 2018048685 A JP2018048685 A JP 2018048685A JP 2016183771 A JP2016183771 A JP 2016183771A JP 2016183771 A JP2016183771 A JP 2016183771A JP 2018048685 A JP2018048685 A JP 2018048685A
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gear
planetary gear
needle roller
planetary
lubricating oil
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功 平井
Isao Hirai
功 平井
雪島　良
Makoto Yukishima
良 雪島
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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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

この発明は、車両用駆動装置の減速機に用いられる遊星歯車装置、特に、遊星歯車を支持する針状ころ軸受への潤滑油供給を改善し、針状ころ軸受を長寿命化した遊星歯車装置に関するものである。   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.

車両用等の各種の回転駆動装置の減速機等に使用されている遊星歯車装置として、例えば、特許文献１に開示されたものがある。   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.

特許文献１の遊星歯車装置は、図２３に示すように、内歯車Ｒと、内歯車Ｒと同軸上に設けられた太陽歯車Ｓと、内歯車Ｒと太陽歯車Ｓに噛み合う公転歯車としての遊星歯車Ｐと、内歯車Ｒと同軸上に設けられた遊星キャリヤＣとからなる。   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.

また、特許文献２及び特許文献３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幅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。   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.

本願の出願人は、特許文献２と特許文献３におけるトルク差を増幅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 amplifies the torque difference in Patent Document 2 and Patent Document 3 (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２４及び図２５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.

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。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。 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.

この先願例１の車両駆動装置２００は、左右輪を駆動する駆動モータ１０１Ｌ、１０１Ｒのトルク差を増幅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 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.

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幅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 amplified 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.

実用新案登録第２５０７５６１号公報Utility Model Registration No. 2507561 特開２０１５−２１５９４号公報JP 2015-21594 A 特許第４９０７３９０号公報Japanese Patent No. 4907390 特開２００８−８８９９３号公報JP 2008-88993 A 特開２０００−３３７４８４号公報JP 2000-337484 A

ところで、遊星歯車装置２１０Ｌ、２１０Ｒは、図２４及び図２５に示すように、遊星歯車ＰL、ＰRの中心に位置する歯車支持軸２１８に針状ころ軸受２２０を介して、遊星歯車ＰL、ＰRが回転自在に支持されている。歯車支持軸２１８の両端は、遊星キャリヤＣL、ＣRの一対のキャリヤフランジ２２１に挿通固定されている。 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.

一対のキャリヤフランジ２２１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、図２６及び図２７に示すような、歯車支持軸２１８が内部を通る形のスラスト板２２２を装着している。 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.

遊星歯車ＰL、ＰRを歯車支持軸２１８に対して回転自在に支持する針状ころ軸受２２０は、図２７に示すように、歯車支持軸２１８の外径面によって構成される内輪軌道面２２０ａと、遊星歯車ＰL、ＰRの内径面によって構成される外輪軌道面２２０ｂと、内輪軌道面２２０ａと外輪軌道面２２０ｂとの間に収容された複数本の針状ころ２２０ｃと、複数本の針状ころ２２０ｃを等間隔に保持する保持器２２０ｄとからなる。 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.

スラスト板２２２は、図２６及び図２７に示すように、中心に歯車支持軸２１８が通る貫通孔２２３を有するリング形状に形成され、スラスト板２２２の外径は、外輪軌道面２２０ｂを構成する遊星歯車ＰL、ＰRの内径面よりも大きく形成され、スラスト板２２２がキャリヤフランジ２２１の幅面と遊星歯車ＰL、ＰRの幅面との間で摺接している。 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.

図２７は、スラスト板２２２の一部を切り欠いて示しており、スラスト板２２２に隠れた針状ころ２２０ｃ、保持器２２０ｄ、外輪軌道面２２０ｂが見えるようにしている。   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.

ところで、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の潤滑のために、遊星歯車装置２１０Ｌ、２１０Ｒの歯車の一部や平行軸歯車減速機の歯車の一部が減速機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。   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.

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、車両の停止時に内部の遊星歯車ＰL、ＰRの歯車支持軸２１８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歯車ＰL、ＰRの歯車支持軸２１８が
潤滑油に浸からない状態になる。 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.

また、遊星歯車ＰL、ＰRとキャリヤフランジ２２１の間に位置するスラスト板２２２は、遊星歯車ＰL、ＰRを所定の軸方向範囲に保持するため、遊星歯車ＰL、ＰRとキャリヤフランジ２２１とのクリアランスが小さい。 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.

さらに、遊星歯車ＰL、ＰRを均一に保持するように、図２６及び図２７に示すように、スラスト板２２２は円形となっており、スラスト板２２２の外径は、外輪軌道面２２０ｂを構成する遊星歯車ＰL、ＰRの内径面よりも大きく形成され、スラスト板２２２によって針状ころ軸受２２０における外輪軌道面２２０ｂと内輪軌道面２２０ａとの間の針状ころ２２０ｃの収容空間が塞がれている。 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.

したがって、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があった。 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.

従来、遊星歯車装置において、遊星歯車の幅面に配置されるスラスト板に溝を設け、潤滑油をスラスト板の溝によって潤滑油を供給しようとする技術が特許文献４に開示されている。   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.

特許文献４のようにスラスト板に溝を設けたとしても、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のような場合には、前記のように、特に、車両の高速走行時は回転する内歯車ＲL、ＲRが減速機ハウジングの下部に溜められた潤滑油を掻き分けてしまうので、スラスト板が潤滑油に浸からず、スラスト板に溝があっても、遊星歯車ＰL、ＰRを支持する針状ころ軸受２２０内に潤滑油が入っていかず、潤滑効果が得られない。また、薄いスラスト板に溝加工を行うことは、そもそも加工の難易度が高いという課題もある。 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.

また、特許文献５には、スラスト板に油溜め穴を設け、遊星歯車の内周部の針状ころ軸受側からスラスト板に向けて流れてきた潤滑油をスラスト板の油留め穴に保持して、スラスト板と遊星歯車または遊星キャリヤとの摺動面の潤滑を向上させようとする技術が開示されている。   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.

しかしながら、この特許文献５の技術では、スラスト板の外周面から飛散してきた潤滑油を針状ころ軸受の外輪軌道面と内輪軌道面との間の針状ころの収容空間に導くことはできない。特に、内歯車と遊星キャリヤが共に回転する車両用駆動装置の遊星歯車装置では、減速機ハウジングの下部の油溜まりから歯車の回転で掻き上げられて飛散した潤滑油は、減速機ハウジングの内壁に付着し、減速機ハウジングの内壁に設けたリブに沿って流れるため、この潤滑油がスラスト板の外周面に到達しても、特許文献５の技術では、潤滑油を針状ころ軸受の外輪軌道面と内輪軌道面との間の針状ころの収容空間に導くことはできない。   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.

そこで、この発明は、減速機ハウジングの下部の油溜まりから歯車の回転で掻き上げられて飛散した潤滑油が、減速機ハウジングの内壁に付着し、減速機ハウジングの内壁に設けたリブに沿って流れた際に、この潤滑油を針状ころ軸受の外輪軌道面と内輪軌道面との間の針状ころの収容空間に導くことができるようにすることにより、遊星歯車を支持する針状ころ軸受への潤滑油供給を改善し、針状ころ軸受を長寿命化しようとするものである。   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.

前記の課題を解決するために、この発明は、内歯車と、内歯車と同軸上に設けられた太陽歯車と、内歯車と太陽歯車に噛み合う公転歯車としての複数の遊星歯車と、遊星歯車を針状ころ軸受を介して回転自在に支持する歯車支持軸と、遊星歯車の両側を挟み、歯車支持軸の両端が挿通固定されるキャリヤフランジを有する遊星キャリヤとを備え、遊星歯車の幅面とキャリヤフランジの幅面との間にスラスト板を設けた遊星歯車装置において、スラスト板の外周形状を、歯車支持軸に設けられた針状ころ軸受の外径軌道面よりも外径側に位置し、遊星歯車の幅面とキャリヤフランジの幅面との間を摺接する大径部と、歯車支持軸に設けられた針状ころ軸受の外径軌道面よりも内径側に位置する小径部との組み合わせ形状にし、針状ころ軸受の外径軌道面よりも内径側に位置するスラスト板の小径部と針状ころ軸受の外径軌道面との間に、針状ころ軸受の収容空間に連通する連通部を形成したことを特徴とする。   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.

前記遊星歯車装置をハウジング内に収容し、遊星キャリヤの軸心に遊星キャリヤをハウジングに対して支持する中空軸部を設け、この中空軸部に、前記ハウジングの壁面を流れる潤滑油を前記スラスト板の外径部に供給する潤滑油通路を設けてもよい。   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.

前記中空軸部の内径部に転がり軸受を介して太陽歯車を支持し、スラスト板の外径部に供給する潤滑油通路が太陽歯車を支持する転がり軸受を通過するように設けてもよい。   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.

前記中空軸部と太陽歯車との間に、トルクを伝達するスプライン部を設け、このスプライン部に欠歯部を設け、この欠歯部がスラスト板の外径部に潤滑油を供給する潤滑油通路を構成するようにしてもよい。   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.

前記中空軸部が対面するハウジングの壁面に、ハウジングの壁面を流れる潤滑油を集油し、中空軸部内に潤滑油を供給する油受け部材を設けるようにしてもよい。   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.

前記中空軸部の内径面に段差部を設け、前記油受け部材に、段差部を超えて集油した潤滑油を軸方向の内部に導く導油管を設けるようにしてもよい。   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.

車両に搭載され独立して制御可能な二つの駆動源と左右の駆動輪との間に、この発明に係る遊星歯車装置を同軸上に二つ組み合わせ、一方の遊星歯車装置の特定の要素と、他方の遊星歯車装置の特定の要素とを、第１結合部材と第２結合部材により相互に連結して二つの駆動源からのトルクを左右の駆動輪にトルク差を増幅して伝達する歯車装置を設け、前記遊星歯車装置の内歯車に減速装置としての外歯車が連結されている車両用駆動装置を構成することができる。   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.

以上のように、この発明によれば、遊星歯車の幅面とキャリヤフランジの幅面との間に設けられたスラスト板の外径部に、遊星歯車を回転自在に支持する針状ころ軸受の収容空間に連通する連通部を形成したので、スラスト板の外径部に供給された潤滑油を連通部を介して針状ころ軸受の収容空間に導入できるので、遊星歯車を支持する針状ころ軸受への潤滑油供給が改善され、針状ころ軸受を長寿命化することができる。   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.

この発明の遊星歯車装置を組み込んだ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 drive device for vehicles incorporating the planetary gear apparatus 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. 図１の実施形態における遊星キャリヤの中空軸部の内面に形成したスプライン部の拡大図である。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. 図１の実施形態の左側の遊星歯車装置における遊星歯車を支持する針状ころ軸受への潤滑油の供給経路を示す部分拡大図である。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. 図１の実施形態の右側の遊星歯車装置における遊星歯車を支持する針状ころ軸受への潤滑油の供給経路を示す部分拡大図である。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. 図１の実施形態の歯車の配置を示す図１のＡ−Ａの断面図である。It is sectional drawing of AA of FIG. 1 which shows arrangement | positioning of the gearwheel of embodiment of FIG. 図１の実施形態の遊星歯車の拡大側面図である。It is an enlarged side view of the planetary gear of the embodiment of FIG. この発明で使用するスラスト板の一例を示す斜視図である。It is a perspective view which shows an example of the thrust board used by this invention. 図１０のスラスト板を遊星歯車の側面に装着した状態を示す拡大側面図である。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. この発明で使用するスラスト板の他の例を示す斜視図である。It is a perspective view which shows the other example of the thrust board used by this invention. 図１２のスラスト板を遊星歯車の側面に装着した状態を示す拡大側面図である。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. この発明で使用するスラスト板の他の例を示す斜視図である。It is a perspective view which shows the other example of the thrust board used by this invention. 図１４のスラスト板を遊星歯車の側面に装着した状態を示す拡大側面図である。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. 図１０のスラスト板を使用した遊星歯車装置の潤滑油の供給経路を示す図２のＢ−Ｂ線の断面図である。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. この発明の遊星歯車装置を組み込んだ車両用駆動装置の他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 other embodiment of the drive device for vehicles incorporating the planetary gear apparatus of this invention. 図１７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１７の実施形態の左側の遊星歯車装置における遊星歯車を支持する針状ころ軸受への潤滑油の供給経路を示す部分拡大図である。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. 図１７の実施形態の右側の遊星歯車装置における遊星歯車を支持する針状ころ軸受への潤滑油の供給経路を示す部分拡大図である。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. 図１７の実施形態において遊星歯車装置に使用する油受け部材を左側に取り付けた場合の斜視図である。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. 図１７の実施形態において遊星歯車装置に使用する油受け部材を右側に取り付けた場合の斜視図である。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. 従来の遊星歯車装置の断面図である。It is sectional drawing of the conventional planetary gear apparatus. 先願例１の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 of prior application example 1. 図２４に示す先願例１の車両用駆動装置の歯車装置部分の拡大図である。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. 先願例１の車両用駆動装置において使用するスラスト板の斜視部である。3 is a perspective view of a thrust plate used in the vehicle drive device of Prior Application Example 1. FIG. 図２６のスラスト板を遊星歯車の側面に装着した状態を示す拡大側面図である。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.

以下、この発明の実施の形態を、独立した二つの駆動源からの駆動トルクを左右の駆動輪にトルク差を増幅して伝達することができるトルク差増幅機構として、車両駆動装置の平行軸歯車減速機に組み込まれる遊星歯車装置を例にして説明する。   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.

図３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、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３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. 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.

図１及び図３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。   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.

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３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。四輪駆動方式においては、車両用駆動装置１は前輪又は後輪の双方に搭載してもよく、又はそのいずれか一方に搭載して、もう一方は例えばエンジンにより駆動する歯車装置など他の駆動装置であってもよい。   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.

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出力特性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。   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.

モータハウジング４Ｌ、４Ｒは、図１に示すように、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の内側面に設けられた内側壁４ｃＬ、４ｃＲとからなる。モータハウジング４Ｌ、４Ｒ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。   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.

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の内周に隙間を隔ててロータ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 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.

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４Ｌ、４Ｒ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４Ｌ、４Ｒ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 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.

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からトルク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３）、中間シャフト６５ｃ（図３）を介して駆動輪６１Ｌ、６１Ｒ（図３）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 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.

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は異なるサイズのものとしているが、同一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 different sizes, but the same size may be combined.

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。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。 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.

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のトルク差を増幅して車輪に出力することができる。   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.

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幅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 amplified 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３に示すスケルトン図の通りである。   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.

図３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. 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.

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４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と入力側外歯車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 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.

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にスプライン結合（セレーション結合を含む）にて接続されている。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, 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.

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４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４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 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.

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４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. 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).

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４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. 4, 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３参照）。   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. 3).

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。そして、軸受嵌合穴５３ａ、５３ｂは、転がり軸受５４ａ、５４ｂの外輪が当接する段付き形状になっている。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. 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.

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 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.

遊星キャリヤＣL、ＣRのうち、左側の遊星キャリヤＣL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を有し、この中空軸部３６の外径面が、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。 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.

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（車両の内側）のキャリヤフランジ３４ｂには、インボード側に延びる中空の第２結合部材３２が一体に形成され、中空の第２結合部材３２のキャリヤフランジ３４ｂ側に大径部３２ａが形成され、この大径部３２ａが減速機ハウジング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。 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.

インボード側のキャリヤフランジ３４ｂと転がり軸受２０ａとの間には、カラー４０を配置している。   A collar 40 is disposed between the carrier flange 34b on the inboard side and the rolling bearing 20a.

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.

図１及び図２に示す実施形態では、中空軸で構成される第２結合部材３２は、右側端部が、遊星キャリヤＣRのインボード側のキャリヤフランジ３４ｂと一体に形成されている。第２結合部材３２の左側端部は、遊星キャリヤＣLのアウトボード側キャリヤフランジ３４ａ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。 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.

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.

この第１結合部材３１の左側端部と遊星キャリヤ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とを連結するスプライン部７３には、図５に示すようにスプライン歯７３ａの一部が除去された欠歯部７３ｂが設けられている。 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.

この欠歯部７３ｂは、図６に太線矢印で示すように、左側の遊星キャリヤ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内に流入した潤滑油の潤滑油通路を構成している。 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.

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、図２に示すように、右側端部に大径部７４を有し、この大径部７４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。 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.

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.

第２結合部材３２の遊星キャリヤＣL側の端部は、その外周面に、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の太陽歯車ＳLを構成している。 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.

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 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.

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７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. 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.

ところで、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に収容されており、図８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８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７５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７５の油面高さＨは、車両の停止時に中間歯車軸１３Ｌ、１３Ｒに組み込んだ遊星歯車ＰL、ＰRの歯車支持軸３３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。 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.

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８に示すように、車両の停止時に内部の遊星歯車ＰL、ＰRの歯車支持軸３３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７５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の大径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遊星歯車ＰL、ＰRの歯車支持軸３３が潤滑油に浸からない状態になる。 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.

減速機ハウジング９の下部の油溜まり７５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６及び図７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。 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.

左側の遊星歯車装置３９Ｌの遊星キャリヤ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の内部に流入した潤滑油は、図６の太線矢印で示すように、第１結合部材３１の左側端部と遊星キャリヤ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との間のスプライン部７３の欠歯部７３ｂ（図５）を通って、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からキャリヤフランジ３４ａと遊星歯車ＰLの間に挿入したスラスト板３８の外周に供給される。 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.

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７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. 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.

一対のキャリヤフランジ３４ａ、３４ｂと遊星歯車ＰL、ＰRの間には、図２に示すように、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, 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.

遊星歯車ＰL、ＰRを歯車支持軸３３に対して回転自在に支持する針状ころ軸受３７は、図９に示すように、歯車支持軸３３の外径面によって構成される内輪軌道面３７ａと、遊星歯車ＰL、ＰRの内径面によって構成される外輪軌道面３７ｂと、内輪軌道面３７ａと外輪軌道面３７ｂとの間に収容された複数本の針状ころ３７ｃと、複数本の針状ころ３７ｃを等間隔に保持する保持器３７ｄとからなる。 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.

この発明では、スラスト板３８として、例えば、図１０及び図１１、図１２及び図１３、図１４及び図１５にそれぞれ示す形状のものを使用している。
図１０及び図１１に示すスラスト板３８は、中心に歯車支持軸３３が通る貫通孔３８ａを有し、その外周形状が概ね４角形をしている。この４角形のスラスト板３８は、対角線方向の長さが、針状ころ軸受３７の外輪軌道面３７ｂを構成する遊星歯車ＰL、ＰRの内径面よりも長く形成されており、４角形のスラスト板３８の角部が遊星歯車ＰL、ＰRの幅面に摺接するようにしている。そして、４角形のスラスト板３８の各辺の長さは、針状ころ軸受３７の外輪軌道面３７ｂを構成する遊星歯車ＰL、ＰRの内径面よりも短く形成されており、４角形のスラスト板３８の外周の各辺の中央部に、針状ころ軸受３７の収容空間に連通する連通部３８ｂが形成されている。 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.

この４角形のスラスト板３８の外周面の外接円径は、遊星歯車ＰL、ＰRの内径面によって構成される外輪軌道面３７ｂの径よりも大きい。４角形のスラスト板３８の外周面の内接円径は、針状ころ軸受３７の保持器３７ｄの外周寸法より小さく、針状ころ３７ｃのＰ．Ｃ．Ｄ．近傍まで小さくし、十分な大きさの連通部３８ｂが形成されるようにしている。 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.

図１２及び図１３に示すスラスト板３８は、図１０及び図１１に示すスラスト板３８と同様に、外周形状を概ね４角形とし、各辺の中央部を内側に湾曲させて、図１０及び図１１に示すスラスト板３８よりも４角形のスラスト板３８の外周面の内接円径をさらに小さくして、針状ころ軸受３７の収容空間に連通する連通部３８ｂを広くした実施形態であり、連通部３８ｂが広いだけ針状ころ軸受３７の収容空間にスラスト板３８の外周から潤滑油が侵入しやすくなる。   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.

図１４及び図１５に示すスラスト板３８は、外周形状が凸部３８ｃと凹部３８ｄを波形形状に設けた花弁のような形状をしており、凸部３８ｃの外接円を針状ころ軸受３７の外輪軌道面３７ｂよりも大きくし、凹部３８ｄの内接円を針状ころ軸受３７の外輪軌道面３７ｂよりも小さくして、凹部３８ｄの底部分に針状ころ軸受３７の収容空間に連通する連通部３８ｂを形成した実施形態である。   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.

図１６は、右側の遊星歯車装置３９Ｒにおいて、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の外周に供給された潤滑油が、スラスト板３８の外周の連通部３８ｂから針状ころ軸受３７の収容空間に入る様子を矢印で示している。 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.

スラスト板３８の外周の連通部３８ｂから針状ころ軸受３７の収容空間に入った潤滑油は、針状ころ軸受３７の軸受内を潤滑した後、遠心力によってスラスト板３８の外周の連通部３８ｂから流出し、外部の歯車の歯面を潤滑する。   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.

この発明に係るスラスト板３８は、外周部に針状ころ軸受３７の収容空間に連通する連通部３８ｂを設けているので、スラスト板３８の外周に供給された潤滑油を、連通部３８ｂを介して針状ころ軸受３７の内輪軌道面３７ａと外輪軌道面３７ｂとの間の針状ころ３７ｃの収容空間に導くことができ、遊星歯車ＰL、ＰRを支持する針状ころ軸受３７への潤滑油供給が改善され、針状ころ軸受３７の長寿命化が図れる。 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.

スラスト板３８の材質は鋼製であり、摩耗を抑制するため肌焼鋼に浸炭熱処理が施され、表面硬さを６５０〜８００Ｈｖとしている。あるいは、スラスト板３８の材質を、自己潤滑性と耐熱性、耐油性のある樹脂（ポリイミド、）とすることも可能である。   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.

また、スラスト板３８の外周面の角部は、面取りなどを施してエッジ応力を下げておくことが望ましい。   In addition, it is desirable to reduce the edge stress by chamfering the corners of the outer peripheral surface of the thrust plate 38.

次に、図１７〜図２０に示すこの発明の第２の実施形態は、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、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の内径部に供給できるようにしたものであり、前述の第１の実施形態にさらに次のような構造を付加している。 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.

この第２の実施形態では、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１９及び図２０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。   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.

そして、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る油受け部材７６を取付けている。   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.

油受け部材７６は、図２１及び図２２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７６ａを有する受け板７６ｂと、受け部７６ａの底部に連通し、受け部７６ａ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７６ｃとからなる。   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.

図１７及び図１８に示す第２の実施形態では、中間歯車軸１３Ｌ、１３Ｒのアウトボード側の中空軸部３５に流れ込んだ潤滑油を内部の遊星歯車ＰL、ＰR側に流れ易くするために、中空軸部３５の内部に奥側の径が大きくなるように段差部を設けているので、この段差部を超えて潤滑油が供給されるように、導油管７６ｃの長さが段差部を超える長さに設定している。 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.

なお、左側の中間歯車軸１３Ｌの中空軸部３５においては、内径部にカラー７７を嵌めることによって段差部を形成している。   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.

第２の実施形態における遊星歯車ＰL、ＰRを支持する針状ころ軸受３７への潤滑油供給は、図１９及び図２０に示すように行われる。 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.

まず、左側の遊星歯車装置３９Ｌでは、図１９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に取付けた油受け部材７６の受け部７６ａに流入する。油受け部材７６の受け部７６ａに流入して集油された潤滑油は、導油管７６ｃ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の左側端部と遊星キャリヤ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との間のスプライン部７３の欠歯部７３ｂ（図５）を通って、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からキャリヤフランジ３４ａと遊星歯車ＰLの間に挿入したスラスト板３８の外周に供給され、スラスト板３８の外周の連通部３８ｂ（図１６）を通って、針状ころ軸受３７の収容空間に供給される。スラスト板３８の外周の連通部３８ｂから針状ころ軸受３７の収容空間に入った潤滑油は、針状ころ軸受３７の軸受内を潤滑した後、遠心力によってスラスト板３８の外周の連通部３８ｂから流出し、外部の歯車の歯面を潤滑する。 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.

他方の右側の遊星歯車装置３９Ｒでは、図２０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に取付けた油受け部材７６の受け部７６ａに流入する。油受け部材７６の受け部７６ａに流入した潤滑油は、導油管７６ｃ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、スラスト板３８の外周の連通部３８ｂ（図１６）を通って、針状ころ軸受３７の収容空間に供給される。スラスト板３８の外周の連通部３８ｂから針状ころ軸受３７の収容空間に入った潤滑油は、針状ころ軸受３７の軸受内を潤滑した後、遠心力によってスラスト板３８の外周の連通部３８ｂから流出し、外部の歯車の歯面を潤滑する。 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.

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。   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.

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、２Ｌ ：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
３２ａ ：大径部
３３ ：歯車支持軸
３４ａ、３４ｂ ：キャリヤフランジ
３５、３６ ：中空軸部
３７ ：針状ころ軸受
３７ａ ：内輪軌道面
３７ｂ ：外輪軌道面
３７ｄ ：保持器
３８ ：スラスト板
３８ａ ：貫通孔
３８ｂ ：連通部
３８ｃ ：凸部
３８ｄ ：凹部
３９Ｌ、３９Ｒ ：遊星歯車装置
３９ａ、３９ｂ ：転がり軸受
４０ ：カラー
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 ：スプライン部
７３ａ ：スプライン歯
７３ｂ ：欠歯部
７４ ：大径部
７５ ：油溜まり
７６ ：油受け部材
７６ａ ：受け部
７６ｂ ：受け板
７６ｃ ：導油管
７７ ：カラー
ＡＭ ：電気自動車
ＣL、ＣR ：遊星キャリヤ
Ｈ ：油面高さ
Ｍ ：モーメント
ＰL、ＰR ：遊星歯車
ＲL、ＲR ：内歯車
ＳL、ＳR ：太陽歯車 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)

内歯車と、内歯車と同軸上に設けられた太陽歯車と、内歯車と太陽歯車に噛み合う公転歯車としての複数の遊星歯車と、遊星歯車を針状ころ軸受を介して回転自在に支持する歯車支持軸と、遊星歯車の両側を挟み、歯車支持軸の両端が挿通固定されるキャリヤフランジを有する遊星キャリヤとを備え、遊星歯車の幅面とキャリヤフランジの幅面との間にスラスト板を設けた遊星歯車装置において、スラスト板の外周形状を、歯車支持軸に設けられた針状ころ軸受の外径軌道面よりも外径側に位置し、遊星歯車の幅面とキャリヤフランジの幅面との間を摺接する大径部と、歯車支持軸に設けられた針状ころ軸受の外径軌道面よりも内径側に位置する小径部との組み合わせ形状にし、針状ころ軸受の外径軌道面よりも内径側に位置するスラスト板の小径部と針状ころ軸受の外径軌道面との間に、針状ころ軸受の収容空間に連通する連通部を形成したことを特徴とする遊星歯車装置。   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. 前記遊星歯車装置をハウジング内に収容し、遊星キャリヤの軸心に遊星キャリヤをハウジングに対して支持する中空軸部を設け、この中空軸部に、前記ハウジングの壁面を流れる潤滑油を前記スラスト板の外径部に供給する潤滑油通路を設けたことを特徴とする請求項１記載の遊星歯車装置。   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. 前記中空軸部の内径部に転がり軸受を介して太陽歯車を支持し、スラスト板の外径部に供給する潤滑油通路が太陽歯車を支持する転がり軸受を通過するように設けられている請求項２記載の遊星歯車装置。   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. 前記中空軸部と太陽歯車との間に、トルクを伝達するスプライン部を設け、このスプライン部に欠歯部を設け、この欠歯部がスラスト板の外径部に潤滑油を供給する潤滑油通路を構成する請求項２記載の遊星歯車装置。   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. 前記中空軸部が対面するハウジングの壁面に、ハウジングの壁面を流れる潤滑油を集油し、中空軸部内に潤滑油を供給する油受け部材を設けたことを特徴とする請求項２〜４のいずれかに記載の遊星歯車装置。   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. 前記中空軸部の内径面に段差部を設け、前記油受け部材に、段差部を超えて集油した潤滑油を軸方向の内部に導く導油管を設けたことを特徴とする請求項５に記載の遊星歯車装置。   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. 車両に搭載され独立して制御可能な二つの駆動源と左右の駆動輪との間に、請求項１〜６のいずれかに記載の遊星歯車装置を同軸上に二つ組み合わせ、一方の遊星歯車装置の特定の要素と、他方の遊星歯車装置の特定の要素とを、第１結合部材と第２結合部材により相互に連結して二つの駆動源からの動力を左右の駆動輪にトルク差を増幅して伝達する歯車装置を設け、前記遊星歯車装置の内歯車に減速装置としての外歯車が連結されていることを特徴とする車両用駆動装置。   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.
JP2016183771A 2016-09-21 2016-09-21 Planetary gear device and driving device for vehicle using the same Pending JP2018048685A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022071091A1 (en) 2020-09-29 2022-04-07 株式会社アイシン Vehicle drive device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022071091A1 (en) 2020-09-29 2022-04-07 株式会社アイシン Vehicle drive device
EP4224684A4 (en) * 2020-09-29 2024-03-20 Aisin Corporation Vehicle drive device
JP7495991B2 (en) 2020-09-29 2024-06-05 株式会社アイシン Vehicle drive device

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