JP2017155864A - Transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve transmission efficiency by effectively lubricating a contact portion of rolling elements and transmission grooves with a simple structure, in a transmission device which has a first transmission member rotating around a first axis, a second transmission member revolving around the first axis while rotating around a second axis eccentric from the first axis, and a transmission mechanism disposed between the first and second transmission members, and in which the transmission mechanism has a waveform annular first transmission groove existing on a face opposed to the second transmission member, of the first transmission member, a waveform annular second transmission groove existing on a face opposed to the first transmission member, of the second transmission member, and a plurality of rolling elements disposed on a plurality of intersecting portions of the transmission grooves for transmitting speed change between both transmission members.SOLUTION: At least one of first transmission members 5, 9 and a second transmission member 8 have the annular shape, at least one of the annular transmission members 5, 9, 8 is provided with a lubricant passage 50 having an oil inlet 51 at an inner peripheral portion of the transmission member and an oil outlet 52 at transmission grooves 21, 24, 25 of the transmission member.SELECTED DRAWING: Figure 1

Description

本発明は、伝動装置、特に第１軸線回りに回転する第１の伝動部材と、その第１の伝動部材に対向配置されて、第１軸線から偏心した第２軸線回りを自転しながら第１軸線回りに公転し得る第２の伝動部材と、前記第１の伝動部材及び前記第２の伝動部材の相互間に設けられて、その両伝動部材間で変速しつつトルク伝達可能な変速機構とを備える伝動装置に関する。   The present invention relates to a transmission device, in particular, a first transmission member that rotates about a first axis, and a first transmission member that is disposed opposite to the first transmission member and rotates about a second axis that is eccentric from the first axis. A second transmission member capable of revolving around an axis, and a transmission mechanism provided between the first transmission member and the second transmission member and capable of transmitting torque while shifting between the two transmission members. It is related with a transmission provided with.

上記伝動装置は、例えば特許文献１に示されるように従来公知であり、このものでは、第１変速機構が、第１の伝動部材の、第２の伝動部材との対向面に在り且つ第１軸線を中心とする波形環状の第１の伝動溝と、第２の伝動部材の、第１の伝動部材との対向面に在り且つ第２軸線を中心とする波形環状で波数が第１の伝動溝とは異なる第２の伝動溝と、第１の伝動溝及び第２の伝動溝の複数の交差部に介装される複数の転動体とを有しており、このものでは、例えば各伝動部材を板状に形成することで、伝動装置の軸方向小型化を図り得る利点がある。   The transmission device is conventionally known as disclosed in, for example, Patent Document 1. In this device, the first transmission mechanism is located on the surface of the first transmission member facing the second transmission member, and the first transmission mechanism is first. The first transmission groove having a wave shape centered on the second axis and located on the surface of the second transmission member facing the first transmission member and having the first transmission groove having a waveform shape centering on the axis. A second transmission groove different from the groove, and a plurality of rolling elements interposed at a plurality of intersections of the first transmission groove and the second transmission groove. By forming the member in a plate shape, there is an advantage that the transmission device can be reduced in the axial direction.

特開２００３−１７２４１９号公報JP 2003-172419 A

ところで上記伝動装置では、伝動中、各転動体がその両側の伝動溝を転動しながら両伝動部材間の変速伝動を行うことから、伝動効率を高めるためには、転動体及び伝動溝の接触部等に十分な潤滑を施す必要がある。   By the way, in the above transmission device, during transmission, each rolling element performs transmission transmission between both transmission members while rolling on the transmission grooves on both sides thereof. In order to increase transmission efficiency, contact between the rolling element and the transmission groove is required. It is necessary to provide sufficient lubrication to the parts.

そこで従来装置では、両伝動部材間の間隙を通して転動体及び伝動溝の接触部等に潤滑油を供給するようにしているが、その両伝動部材間の間隙は狭いため、潤滑油の供給量は十分ではなかった。   Therefore, in the conventional device, the lubricating oil is supplied to the contact portion of the rolling element and the transmission groove through the gap between the two transmission members, but since the gap between the two transmission members is narrow, the supply amount of the lubricating oil is It was not enough.

本発明は、かかる事情に鑑みてなされたものであって、転動体及び伝動溝の接触部等を効果的に潤滑し得る伝動装置を提供することを目的とする。   This invention is made | formed in view of this situation, Comprising: It aims at providing the transmission which can lubricate the contact part of a rolling element, a transmission groove, etc. effectively.

上記目的を達成するために、本発明は、第１軸線回りに回転する第１の伝動部材と、その第１の伝動部材に対向配置されて、第１軸線から偏心した第２軸線回りを自転しながら第１軸線回りに公転し得る第２の伝動部材と、前記第１の伝動部材及び前記第２の伝動部材の相互間に設けられて、その両伝動部材間で変速しつつトルク伝達可能な変速機構とを備え、前記変速機構が、前記第１の伝動部材の、前記第２の伝動部材との対向面に在り且つ第１軸線を中心とする波形環状の第１の伝動溝と、前記第２の伝動部材の、前記第１の伝動部材との対向面に在り且つ第２軸線を中心とする波形環状で波数が前記第１の伝動溝とは異なる第２の伝動溝と、前記第１の伝動溝及び前記第２の伝動溝の複数の交差部に介装され、その両伝動溝を転動しながら前記両伝動部材間の変速伝動を行う複数の転動体とを有する伝動装置であって、前記第１の伝動部材及び前記第２の伝動部材のうちの少なくとも一方が環状であり、前記少なくとも一方の環状の伝動部材には、その伝動部材の内周部に油入口が開口し且つその伝動部材の伝動溝に油出口が開口した潤滑油路が設けられることを第１の特徴とする。   In order to achieve the above object, the present invention provides a first transmission member that rotates about a first axis, and a second transmission line that is disposed opposite to the first transmission member and that is eccentric from the first axis. The second transmission member that can revolve around the first axis while being provided between the first transmission member and the second transmission member, and can transmit torque while shifting between the two transmission members. A first transmission groove having an annular shape centered on the first axis and located on a surface of the first transmission member facing the second transmission member; A second transmission groove on the surface of the second transmission member facing the first transmission member and having a wave shape centered on the second axis and having a wave number different from that of the first transmission groove; Interposed between a plurality of intersecting portions of the first transmission groove and the second transmission groove, rolling the both transmission grooves. A transmission device having a plurality of rolling elements that perform transmission transmission between the two transmission members, wherein at least one of the first transmission member and the second transmission member is annular, and the at least one The annular transmission member is provided with a lubricating oil passage having an oil inlet opened in the inner peripheral portion of the transmission member and an oil outlet opened in the transmission groove of the transmission member.

また本発明は、第１の特徴に加えて、前記転動体がボールで構成される一方、前記両伝動溝は、各伝動溝の、前記ボールとの接点が２点となるよう溝幅が溝底に向かうにつれて減少する断面形状を有しており、前記油出口は、前記接点の軌跡を避けるように前記少なくとも一方の環状の伝動部材の伝動溝の溝底に開口していることを第２の特徴とする。   According to the present invention, in addition to the first feature, the rolling element is formed of a ball, while the both transmission grooves have a groove width such that each of the transmission grooves has two points of contact with the ball. The oil outlet has a cross-sectional shape that decreases toward the bottom, and the oil outlet is open to the groove bottom of the transmission groove of the at least one annular transmission member so as to avoid the locus of the contact point. It is characterized by.

また本発明は、第１又は第２の特徴に加えて、前記少なくとも一方の環状の伝動部材には、その周方向に間隔をおいて複数の前記潤滑油路が設けられ、それら潤滑油路の前記油入口を相互に連通させる環状溝が、前記少なくとも一方の環状の伝動部材の内周面に凹設されることを第３の特徴とする。   Further, according to the present invention, in addition to the first or second feature, the at least one annular transmission member is provided with a plurality of the lubricating oil passages at intervals in the circumferential direction. A third feature is that an annular groove that allows the oil inlets to communicate with each other is recessed in an inner peripheral surface of the at least one annular transmission member.

本発明の第１の特徴によれば、変速機構を相互間に設けた第１・第２の伝動部材のうちの少なくとも一方が環状であり、その少なくとも一方の環状の伝動部材には、その伝動部材の内周部に油入口が開口し且つその伝動部材の伝動溝に油出口が開口した潤滑油路が設けられるので、伝動装置の作動中、その機構内部を流動する潤滑油が環状の伝動部材の内周部に達すると、その油が伝動部材の回転による遠心力で、該内周部に開口する油入口から上記潤滑油路にスムーズに流入し、更にその潤滑油路を油出口側に向かって効率よく流動して伝動溝内に効率よく供給される。これにより、遠心力を利用した簡単な構造で転動体及び伝動溝の接触部等を効果的に潤滑可能となるから、変速機構、延いては伝動装置の伝動効率アップに寄与することができる。   According to the first aspect of the present invention, at least one of the first and second transmission members provided with the speed change mechanism between them is annular, and the at least one annular transmission member includes the transmission. Since a lubricating oil passage having an oil inlet opening in the inner peripheral portion of the member and an oil outlet opening in the transmission groove of the transmission member is provided, the lubricating oil flowing inside the mechanism during the transmission operation is an annular transmission. When the oil reaches the inner periphery of the member, the oil smoothly flows into the lubricating oil passage from the oil inlet that opens to the inner peripheral portion by centrifugal force due to the rotation of the transmission member, and the lubricating oil passage further enters the oil outlet side. And efficiently flows toward the power transmission groove. As a result, it is possible to effectively lubricate the contact portions of the rolling elements and the transmission grooves with a simple structure using centrifugal force, which can contribute to an increase in transmission efficiency of the speed change mechanism and the transmission device.

また第２の特徴によれば、両伝動溝は、各伝動溝の、ボール状転動体との接点が２点となるよう溝幅が溝底に向かうにつれて減少する断面形状を有し、上記潤滑油路の油出口は、接点軌跡を避けるように伝動溝の溝底に開口するので、油出口の形成に起因した伝動溝のボール軌道部とその周辺部の損傷を効果的に回避して、伝動溝におけるボールのスムーズな転動を確保可能となる。しかも潤滑油が伝動溝の特に溝底に供給されることで、その溝底の両側に存するボール軌道部を効果的に潤滑可能となる。   Further, according to the second feature, each of the transmission grooves has a cross-sectional shape in which the groove width decreases toward the groove bottom so that the contact point of each transmission groove with the ball-shaped rolling element becomes two points. Since the oil outlet of the oil passage opens at the groove bottom of the transmission groove so as to avoid the contact locus, effectively avoiding damage to the ball raceway portion of the transmission groove and its peripheral part due to the formation of the oil outlet, Smooth rolling of the ball in the transmission groove can be ensured. In addition, since the lubricating oil is supplied to the transmission groove, particularly to the groove bottom, the ball raceways existing on both sides of the groove bottom can be effectively lubricated.

また第３の特徴によれば、環状の伝動部材には、その周方向に間隔をおいて複数の潤滑油路が設けられ、それら潤滑油路の油入口を相互に連通させる環状溝が、環状の伝動部材の内周面に凹設されるので、環状の伝動部材の内周面に達した潤滑油を環状溝で効率よく捕捉して複数の潤滑油路に満遍なく分配することができ、これにより、伝動溝を広範囲に亘り偏りなく効果的に潤滑可能となる。   Further, according to the third feature, the annular transmission member is provided with a plurality of lubricating oil passages at intervals in the circumferential direction, and the annular groove for communicating the oil inlets of the lubricating oil passages with each other is provided in an annular shape. Since the lubricating oil that has reached the inner peripheral surface of the annular transmission member is efficiently captured by the annular groove, it can be evenly distributed to the plurality of lubricating oil paths. As a result, the transmission groove can be effectively lubricated without deviation over a wide range.

本発明の第１実施形態に係る伝動装置（差動装置）の縦断正面図1 is a longitudinal front view of a transmission device (differential device) according to a first embodiment of the present invention. 図１の２−２線断面図2-2 sectional view of FIG. 図１の３−３線断面図3-3 sectional view of FIG. 図１の４−４線断面図Sectional view taken along line 4-4 in FIG. 潤滑油路の中心軸線を通る断面で見た第２伝動部材（第２半体）の拡大断面図（図３の５−５線拡大断面図）Enlarged sectional view of the second transmission member (second half body) as seen in a section passing through the central axis of the lubricating oil passage (enlarged sectional view taken along line 5-5 in FIG. 3) 本発明の第２実施形態を示す図５対応断面図FIG. 5 is a sectional view corresponding to FIG. 5 showing a second embodiment of the present invention. 本発明の第３実施形態を示す図５対応断面図FIG. 5 is a sectional view corresponding to FIG. 5 showing a third embodiment of the present invention.

本発明の実施形態を添付図面に基づいて以下に説明する。   Embodiments of the present invention will be described below with reference to the accompanying drawings.

先ず、図１〜図５に示す本発明の第１実施形態を説明する。図１において、自動車のミッションケース１内には、伝動装置としての差動装置Ｄが変速装置と共に収容される。   First, a first embodiment of the present invention shown in FIGS. 1 to 5 will be described. In FIG. 1, a differential device D as a transmission device is housed in a transmission case 1 of an automobile together with a transmission.

この差動装置Ｄは、前記変速装置の出力側に連動回転するリングギヤＣｇの回転を、差動装置Ｄの中心軸線即ち第１軸線Ｘ１上に相対回転可能に並ぶ左右の駆動車軸Ｓ１，Ｓ２（即ち第１，第２ドライブ軸）に対して、両駆動車軸Ｓ１，Ｓ２相互の差動回転を許容しつつ分配する。尚、各々の駆動車軸Ｓ１，Ｓ２とミッションケース１との間は、シール部材４，４′でシールされる。   In the differential device D, the left and right drive axles S1, S2 (in which the rotation of the ring gear Cg that rotates in conjunction with the output side of the transmission device is arranged on the central axis of the differential device D, that is, the first axis X1, are relatively rotatable. That is, the first and second drive shafts) are distributed while allowing differential rotation between the drive axles S1 and S2. The drive axles S1, S2 and the transmission case 1 are sealed with seal members 4, 4 '.

ミッションケース１の底部は、潤滑油を所定量貯溜し得るオイルパン（図示せず）に構成される。そのオイルパン内の貯溜潤滑油は、ミッションケース１内の回転部分、例えば後述するデフケースＣが回転することで勢いよく掻き回されてケース１内空間に広範囲に飛散し、この飛散潤滑油によりケース１内の各部、即ち被潤滑部を潤滑可能である。尚、上記した潤滑構造に加えて（或いは代えて）、オイルポンプ等のポンプ手段で圧送された潤滑油をミッションケース１内の各部に強制的に圧送供給するようにしてもよい。   The bottom of the mission case 1 is configured as an oil pan (not shown) that can store a predetermined amount of lubricating oil. The stored lubricating oil in the oil pan is vigorously stirred by rotating a rotating portion in the mission case 1, for example, a differential case C described later, and scattered widely in the internal space of the case 1, and the scattered lubricating oil makes the case Each part in 1, that is, a lubricated part can be lubricated. In addition to (or instead of) the above-described lubrication structure, the lubricating oil pumped by pump means such as an oil pump may be forcibly fed to each part in the mission case 1.

差動装置Ｄは、ミッションケース１に第１軸線Ｘ１回りに回転可能に支持される伝動ケースとしてのデフケースＣと、そのデフケースＣ内に収容される後述の差動機構３とで構成される。デフケースＣは、短円筒状のギヤ本体の外周に斜歯Ｃｇａを設けたヘリカルギヤよりなるリングギヤＣｇと、そのリングギヤＣｇの軸方向両端部に外周端部がそれぞれ接合される左右一対の第１，第２側壁部Ｃａ，Ｃｂとを備える。少なくとも一方の側壁部Ｃａ，Ｃｂには、その外周端近傍において、デフケースＣ内の余剰の潤滑油を遠心力等で適度に排出可能なドレン孔（図示せず）が設けられる。   The differential device D includes a differential case C as a transmission case that is rotatably supported by the transmission case 1 around the first axis X1, and a differential mechanism 3 described later that is housed in the differential case C. The differential case C includes a ring gear Cg made of a helical gear having oblique teeth Cga provided on the outer periphery of a short cylindrical gear body, and a pair of left and right first and first pairs whose outer peripheral ends are joined to both axial ends of the ring gear Cg. 2 side wall parts Ca and Cb. At least one of the side wall portions Ca and Cb is provided with a drain hole (not shown) capable of appropriately discharging excess lubricating oil in the differential case C by centrifugal force or the like in the vicinity of the outer peripheral end thereof.

また第１，第２側壁部Ｃａ，Ｃｂは、各々の内周端部において第１軸線Ｘ１上に並ぶ円筒状の第１，第２ハブＨＢ１，ＨＢ２をそれぞれ一体に有しており、それらハブＨＢ１，ＨＢ２の外周部は、ミッションケース１に軸受２，２′を介して回転自在に支持される。また第１，第２ハブＨＢ１，ＨＢ２の内周部には第１，第２駆動車軸Ｓ１，Ｓ２が第１軸線Ｘ１回りにそれぞれ回転自在に嵌合、支持される。その嵌合面の少なくとも一方（図示例ではハブＨＢ１，ＨＢ２の内周面）には、自動車の少なくとも前進時（即ち駆動車軸Ｓ１，Ｓ２の正転時）にハブＨＢ１，ＨＢ２と駆動車軸Ｓ１，Ｓ２との相対回転に伴いミッションケース１内の飛散潤滑油をデフケースＣ内に引き込むための第１，第２螺旋溝１８，１９が形成される。その各螺旋溝１８，１９の外端はミッションケース１内に、またその内端はデフケースＣ内にそれぞれ開口する。またハブＨＢ１，ＨＢ２の外端面には、ミッションケース１内から各螺旋溝１８，１９の外端開口（即ち入口）への潤滑油の流入を効率よく誘導案内し得るガイド部ＨＢ１ａ，ＨＢ２ａが突設される。   The first and second side wall portions Ca and Cb integrally have cylindrical first and second hubs HB1 and HB2 arranged on the first axis X1 at their inner peripheral end portions, respectively. The outer peripheral portions of HB1 and HB2 are rotatably supported by the mission case 1 via bearings 2 and 2 '. The first and second drive axles S1 and S2 are fitted and supported on the inner peripheral portions of the first and second hubs HB1 and HB2 so as to be rotatable about the first axis X1, respectively. At least one of the fitting surfaces (in the illustrated example, the inner peripheral surfaces of the hubs HB1 and HB2) includes at least the hubs HB1 and HB2 and the drive axle S1, when the automobile is moving forward (ie, when the drive axles S1 and S2 are rotating forward). Along with the relative rotation with S2, first and second spiral grooves 18 and 19 for drawing the scattered lubricating oil in the mission case 1 into the differential case C are formed. The outer ends of the spiral grooves 18 and 19 are opened in the mission case 1 and the inner ends thereof are opened in the differential case C, respectively. On the outer end surfaces of the hubs HB1 and HB2, guide portions HB1a and HB2a that can efficiently guide and guide the inflow of lubricating oil from the inside of the transmission case 1 to the outer end openings (that is, the inlets) of the spiral grooves 18 and 19 protrude. Established.

尚、本実施形態では、ミッションケース１内の潤滑油をデフケースＣ内に供給するための潤滑油供給手段として上記螺旋溝１８，１９が例示されたが、このような螺旋溝１８，１９に加えて（又は代えて）、別の潤滑油供給手段として、例えばオイルポンプ等のポンプ手段で圧送された潤滑油を、駆動車軸Ｓ１，Ｓ２及び／又はデフケースＣに設けた油路（図示せず）を介してデフケースＣ内に供給するようにしてもよい。或いはまた、さらに別の潤滑油供給手段として、デフケースＣの少なくとも一方の側壁部Ｃａ，Ｃｂに、その内外を直接連通させる貫通孔を形成してもよい。尚また、螺旋溝１８，１９は、駆動車軸Ｓ１，Ｓ２の外周面に形成してもよい。   In the present embodiment, the spiral grooves 18 and 19 are exemplified as the lubricating oil supply means for supplying the lubricating oil in the mission case 1 into the differential case C. In addition to the spiral grooves 18 and 19, (Or instead), as another lubricating oil supply means, for example, an oil passage (not shown) provided with lubricating oil pumped by pump means such as an oil pump in the drive axles S1, S2 and / or the differential case C It may be supplied into the differential case C via Alternatively, as yet another lubricating oil supply means, a through hole that directly communicates the inside and the outside may be formed in at least one of the side wall portions Ca and Cb of the differential case C. The spiral grooves 18 and 19 may be formed on the outer peripheral surfaces of the drive axles S1 and S2.

次にデフケースＣ内の差動機構３の構造を説明する。差動機構３は、第１側壁部Ｃａに一体的に設けられて第１軸線Ｘ１回りに回転可能な第１伝動部材５と、第１駆動車軸Ｓ１にスプライン嵌合１６されて第１軸線Ｘ１回りに回転可能な円筒状の第１スプラインボスＳＢ１（即ち第１出力ボス）を一体に含む中空の主軸部６ｊ、および第１軸線Ｘ１から所定の偏心量ｅだけ偏心した第２軸線Ｘ２を中心軸線とする偏心軸部６ｅが結合一体化された偏心回転部材６と、第１伝動部材５に一側部が対向配置され且つ偏心軸部６ｅにボール軸受よりなる軸受７を介して回転自在に支持される円環状の第２伝動部材８と、第２伝動部材８の他側部に対向配置されると共に第２駆動車軸Ｓ２にスプライン嵌合１７されて第１軸線Ｘ１回りに回転可能な円環状の第３伝動部材９と、第１及び第２伝動部材５，８間で変速しつつトルク伝達可能な第１変速機構Ｔ１と、第２及び第３伝動部材８，９間で変速しつつトルク伝達可能な第２変速機構Ｔ２とを備える。   Next, the structure of the differential mechanism 3 in the differential case C will be described. The differential mechanism 3 is provided integrally with the first side wall portion Ca and can be rotated around the first axis X1 and is spline-fitted 16 to the first drive axle S1 to be coupled to the first axis X1. A hollow main shaft portion 6j that integrally includes a cylindrical first spline boss SB1 (that is, a first output boss) that can rotate around, and a second axis X2 that is eccentric from the first axis X1 by a predetermined eccentricity e. An eccentric rotating member 6 in which an eccentric shaft portion 6e serving as an axis is coupled and integrated, and one side portion is disposed opposite to the first transmission member 5, and the eccentric shaft portion 6e is rotatable via a bearing 7 formed of a ball bearing. An annular second transmission member 8 to be supported and a circle that is disposed opposite to the other side of the second transmission member 8 and is spline-fitted 17 to the second drive axle S2 so as to be rotatable about the first axis X1. An annular third transmission member 9 and first and second transmission members 5, A first transmission mechanism T1 which transmit the torque while shifting between, and a second transmission mechanism T2 which transmit the torque while shifting between the second and third transmission members 8,9.

而して、第１軸線Ｘ１回りに回転する偏心回転部材６の偏心軸部６ｅに第２伝動部材８が第２軸線Ｘ２回りに回転自在に嵌合支持されることで、第２伝動部材８は、偏心回転部材６の第１軸線Ｘ１回りの回転に伴い、それの偏心軸部６ｅに対し第２軸線Ｘ２回りに自転しつつ、主軸部６ｊに対し第１軸線Ｘ１回りに公転可能である。   Thus, the second transmission member 8 is rotatably supported around the second axis X2 by the second transmission member 8 being rotatably supported on the eccentric shaft portion 6e of the eccentric rotation member 6 that rotates about the first axis X1. Can revolve around the first axis X1 relative to the main axis 6j while rotating around the second axis X2 relative to the eccentric axis 6e of the eccentric rotating member 6 around the first axis X1. .

また第２伝動部材８は、偏心回転部材６の偏心軸部６ｅに軸受７を介して回転自在に支持されるリング板状の第１半体８ａと、その第１半体８ａに間隔をおいて対向するリング板状の第２半体８ｂと、その両半体８ａ，８ｂ間を一体的に連結する基本的に円筒状の連結部材８ｃとを備える。特に本実施形態では、連結部材８ｃの一端部及び他端部の内周面に、第１半体８ａ及び第２半体８ｂをそれぞれインロー嵌合されており、その嵌合部が溶接、カシメ等の適当な固着手段により固着される。そして、第１半体８ａと第１伝動部材５との相対向面間に前記第１変速機構Ｔ１が、また第２半体８ｂと第３伝動部材９との相対向面間に前記第２変速機構Ｔ２がそれぞれ設けられる。   Further, the second transmission member 8 has a ring plate-like first half 8a that is rotatably supported by the eccentric shaft portion 6e of the eccentric rotating member 6 via a bearing 7, and an interval between the first half 8a. And a ring-plate-shaped second half body 8b facing each other and a basically cylindrical connecting member 8c for integrally connecting the two half bodies 8a and 8b. In particular, in the present embodiment, the first half 8a and the second half 8b are respectively fitted in the inner peripheral surfaces of the one end and the other end of the connecting member 8c, and the fitting portions are welded and caulked. It is fixed by suitable fixing means such as. The first transmission mechanism T1 is disposed between the opposing surfaces of the first half 8a and the first transmission member 5, and the second transmission mechanism T1 is disposed between the opposing surfaces of the second half 8b and the third transmission member 9. A transmission mechanism T2 is provided.

連結部材８ｃには、デフケースＣの内部空間ＩＣと第２伝動部材８の中空部ＳＰとの間を連通させる複数の第１油流通孔１１が周方向に等間隔おきに設けられ、デフケースＣの内部空間ＩＣに飛散する潤滑油を第１油流通孔１１を通して上記中空部ＳＰに導入可能となっている。また第２半体８ｂには、上記中空部ＳＰを第２変速機構Ｔ２の内周側に連通させる第２油流通孔１２が、第２軸線Ｘ２を中心とする円形状に形成される。   The connecting member 8c is provided with a plurality of first oil circulation holes 11 that communicate between the internal space IC of the differential case C and the hollow portion SP of the second transmission member 8 at equal intervals in the circumferential direction. Lubricating oil scattered in the internal space IC can be introduced into the hollow portion SP through the first oil circulation hole 11. Further, the second half body 8b is formed with a second oil circulation hole 12 that communicates the hollow portion SP with the inner peripheral side of the second transmission mechanism T2 in a circular shape with the second axis X2 as the center.

また、第３伝動部材９は、第２駆動車軸Ｓ２にスプライン嵌合１７されて第１軸線Ｘ１回りに回転可能な円筒状の第２スプラインボスＳＢ２（即ち第２出力ボス）を一体に含む主軸部９ｊと、その主軸部９ｊの内端部に同軸状に連設されて第２半体８ｂに対向する円形のリング板部９ｃとが結合一体化されて構成される。尚、上記スプライン嵌合１７部位には、周方向の一部に欠歯部が設けられ、その欠歯部は、第２螺旋溝１９の引き込み作用でミッションケース１内からデフケースＣ内に引き込まれた潤滑油を第２保持部材Ｈ２の内周側や第２伝動部材８の中空部ＳＰに効率よく誘導可能である。   The third transmission member 9 is a main shaft that integrally includes a cylindrical second spline boss SB2 (that is, a second output boss) that is spline-fitted 17 to the second drive axle S2 and is rotatable about the first axis X1. A portion 9j and a circular ring plate portion 9c concentrically connected to the inner end portion of the main shaft portion 9j and facing the second half 8b are coupled and integrated. The spline fitting 17 part is provided with a partial tooth portion in the circumferential direction, and the partial tooth portion is pulled from the transmission case 1 into the differential case C by the pulling action of the second spiral groove 19. The lubricant oil can be efficiently guided to the inner peripheral side of the second holding member H2 and the hollow portion SP of the second transmission member 8.

デフケースＣの第１側壁部Ｃａの内側面と偏心回転部材６との相対向面間には、その相互間の相対回転を許容する第１スラストワッシャＴＨ１が介装されると共に、第１螺旋溝１８の内端開口（即ち出口）を第１スラストワッシャＴＨ１の背面を経由して第１変速機構Ｔ１の内周側に連通させる油路４１が形成される。この油路４１には、第１螺旋溝１８の引き込み作用でミッションケース１内からデフケースＣ内に引き込まれた潤滑油が流入するものである。   A first thrust washer TH1 that allows relative rotation between the inner side surface of the first side wall portion Ca of the differential case C and the eccentric rotating member 6 is interposed between the inner surface and the first spiral groove. An oil passage 41 is formed to communicate the inner end opening (i.e., outlet) of 18 with the inner peripheral side of the first transmission mechanism T1 via the back surface of the first thrust washer TH1. Lubricating oil drawn into the differential case C from the transmission case 1 by the drawing action of the first spiral groove 18 flows into the oil passage 41.

而して、本実施形態の上記油路４１は、第１螺旋溝１８の出口が臨む環状の内周側油路部分４２と、第１側壁部Ｃａの内側面に設けた複数の凹溝４０と第１スラストワッシャＴＨ１の背面との間に画成される中間油路部分４３と、第１変速機構Ｔ１の内周側に直接連通する環状の外周側油路部分４４とで構成される。その外周側油路部分４４には第１変速機構Ｔ１の内周側のみならず前記軸受７も臨んでおり、従って、油路４１を流れる潤滑油は、外周側油路部分４４から第１変速機構Ｔ１及び軸受７の両方に供給可能である。   Thus, the oil passage 41 according to the present embodiment includes an annular inner peripheral oil passage portion 42 facing the outlet of the first spiral groove 18 and a plurality of concave grooves 40 provided on the inner side surface of the first side wall portion Ca. And an intermediate oil passage portion 43 defined between the first thrust washer TH1 and the back surface of the first thrust washer TH1, and an annular outer oil passage portion 44 that communicates directly with the inner periphery of the first transmission mechanism T1. Not only the inner peripheral side of the first speed change mechanism T1 but also the bearing 7 faces the outer peripheral side oil passage portion 44. Therefore, the lubricating oil flowing through the oil passage 41 is shifted from the outer peripheral side oil passage portion 44 to the first speed change. Both the mechanism T1 and the bearing 7 can be supplied.

またデフケースＣの第２側壁部Ｃｂの内側面と第３伝動部材９の外側面との相対向面間には、その相互間の相対回転を許容する第２スラストワッシャＴＨ２が介装される。この第２スラストワッシャＴＨ２には、第２螺旋溝１９の引き込み作用でミッションケース１内からデフケースＣ内に引き込まれた潤滑油が、第３伝動部材９と第２側壁部Ｃｂとの間の油路４５を通して供給される。   Further, a second thrust washer TH2 that allows relative rotation between the inner surface of the second side wall portion Cb of the differential case C and the outer surface of the third transmission member 9 is interposed. In the second thrust washer TH2, the lubricating oil drawn into the differential case C from the transmission case 1 by the drawing action of the second spiral groove 19 is oil between the third transmission member 9 and the second side wall Cb. Supplied through line 45.

更に差動機構３は、第１軸線Ｘ１を挟んで偏心回転部材６の偏心軸部６ｅ及び第２伝動部材８の総合重心Ｇとは逆位相であり且つその総合重心Ｇの回転半径よりも大なる回転半径を有していて偏心回転部材６の主軸部６ｊに相対回転不能に取付けられるバランスウェイトＷを備えている。このバランスウェイトＷは、クリップ１０で主軸部６ｊに固定される環状基部Ｗｍと、その環状基部Ｗｍの周方向特定領域に固設される重錘部Ｗｗとから構成される。そして、第２伝動部材８の中空部ＳＰがバランスウェイトＷの収容空間として利用される。   Further, the differential mechanism 3 is opposite in phase to the eccentric shaft portion 6e of the eccentric rotating member 6 and the total center of gravity G of the second transmission member 8 across the first axis X1, and larger than the rotational radius of the total center of gravity G. And a balance weight W that is attached to the main shaft portion 6j of the eccentric rotating member 6 so as not to be relatively rotatable. This balance weight W is comprised from the cyclic | annular base part Wm fixed to the main axis | shaft part 6j with the clip 10, and the weight part Ww fixed to the circumferential direction specific area | region of the cyclic | annular base part Wm. The hollow portion SP of the second transmission member 8 is used as a storage space for the balance weight W.

図１，図２に示すように、第１伝動部材５の、第２伝動部材８の一側部（第１半体８ａ）に対向する内側面には、第１軸線Ｘ１を中心とした波形環状の第１伝動溝２１が形成され、この第１伝動溝２１は、図示例では第１軸線Ｘ１を中心とする仮想円を基礎円としたハイポトロコイド曲線に沿って周方向に延びている。一方、第２伝動部材８の、第１伝動部材５に対向する一側部（第１半体８ａ）には、第２軸線Ｘ２を中心とした波形環状の第２伝動溝２２が形成される。この第２伝動溝２２は、図示例では第２軸線Ｘ２を中心とする仮想円を基礎円としたエピトロコイド曲線に沿って周方向に延びており、上記第１伝動溝２１の波数よりも少ない波数を有して第１伝動溝２１と複数箇所で交差する。これら第１伝動溝２１及び第２伝動溝２２の交差部（即ち重なり部）には、第１転動体としての複数の第１転動ボール２３が介装されており、各々の第１転動ボール２３は、それら第１及び第２伝動溝２１，２２の内側面を転動自在である。   As shown in FIGS. 1 and 2, the first transmission member 5 has a waveform centered on the first axis X <b> 1 on the inner surface facing the one side portion (first half 8 a) of the second transmission member 8. An annular first transmission groove 21 is formed, and the first transmission groove 21 extends in the circumferential direction along a hypotrochoid curve having a virtual circle centered on the first axis X1 in the illustrated example. On the other hand, a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side portion (first half 8a) of the second transmission member 8 facing the first transmission member 5. . In the illustrated example, the second transmission groove 22 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the second axis X2 as a base circle, and is smaller than the wave number of the first transmission groove 21. It has a wave number and intersects the first transmission groove 21 at a plurality of locations. A plurality of first rolling balls 23 as first rolling elements are interposed at intersections (that is, overlapping portions) of the first transmission groove 21 and the second transmission groove 22, and each first rolling groove is provided. The ball 23 can roll on the inner surfaces of the first and second transmission grooves 21 and 22.

第１伝動部材５及び第２伝動部材８（第１半体８ａ）の相対向面間には、円環状の扁平な第１保持部材Ｈ１が介装される。この第１保持部材Ｈ１は、複数の第１転動ボール２３の、第１、第２伝動溝２１，２２相互の交差部での両伝動溝２１，２２への係合状態を維持し得るように、複数の第１転動ボール２３をそれらの相互間隔を一定に規制しつつ回転自在に保持する複数の円形の第１保持孔３１を周方向で等間隔置きに有している。   Between the opposing surfaces of the first transmission member 5 and the second transmission member 8 (first half 8a), an annular flat first holding member H1 is interposed. The first holding member H1 can maintain the engagement state of the plurality of first rolling balls 23 with both the transmission grooves 21 and 22 at the intersections of the first and second transmission grooves 21 and 22. In addition, a plurality of circular first holding holes 31 that hold the plurality of first rolling balls 23 in a freely rotating manner while keeping their mutual spacing constant are provided at equal intervals in the circumferential direction.

また、図１，２，４に示すように、第２伝動部材８の他側部（第２半体８ｂ）には、第２軸線Ｘ２を中心とした波形環状の第３伝動溝２４が形成され、この第３伝動溝２４は、図示例では第２軸線Ｘ２を中心とする仮想円を基礎円としたハイポトロコイド曲線に沿って周方向に延びている。一方、第３伝動部材９の、第２伝動部材８との対向面すなわちリング板部９ｃの内側面には、第１軸線Ｘ１を中心とした波形環状の第４伝動溝２５が形成される。この第４伝動溝２５は、図示例では第１軸線Ｘ１を中心とする仮想円を基礎円としたエピトロコイド曲線に沿って周方向に延びており、上記第３伝動溝２４の波数よりも少ない波数を有して第３伝動溝２４と複数箇所で交差する。これら第３伝動溝２４及び第４伝動溝２５の交差部（重なり部）には、第２転動体としての複数の第２転動ボール２６が介装されており、各々の第２転動ボール２６は、それら第３及び第４伝動溝２４，２５の内側面を転動自在である。また本実施形態では、第１及び第２伝動溝２１，２２のトロコイド係数と、第３及び第４伝動溝２４，２５のトロコイド係数とは互いに異なる値に設定される。   As shown in FIGS. 1, 2, and 4, a corrugated annular third transmission groove 24 centering on the second axis X <b> 2 is formed on the other side (second half 8 b) of the second transmission member 8. In the illustrated example, the third transmission groove 24 extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the second axis X2 as a base circle. On the other hand, on the surface of the third transmission member 9 facing the second transmission member 8, that is, on the inner surface of the ring plate portion 9c, a corrugated fourth transmission groove 25 centered on the first axis X1 is formed. In the illustrated example, the fourth transmission groove 25 extends in the circumferential direction along an epitrochoidal curve having a virtual circle centered on the first axis X1 as a base circle, and is smaller than the wave number of the third transmission groove 24. It has a wave number and intersects with the third transmission groove 24 at a plurality of locations. A plurality of second rolling balls 26 as second rolling elements are interposed at intersections (overlapping portions) of the third transmission groove 24 and the fourth transmission groove 25, and each second rolling ball is disposed. 26 can roll on the inner surfaces of the third and fourth transmission grooves 24 and 25. In the present embodiment, the trochoidal coefficients of the first and second transmission grooves 21 and 22 and the trochoidal coefficients of the third and fourth transmission grooves 24 and 25 are set to different values.

第３伝動部材９及び第２伝動部材８（第２半体８ｂ）の相対向面間には、円環状の扁平な第２保持部材Ｈ２が介装される。この第２保持部材Ｈ２は、複数の第２転動ボール２６の、第３、第４伝動溝２４，２５相互の交差部での両伝動溝２４，２５への係合状態を維持し得るように、複数の第２転動ボール２６をそれらの相互間隔を一定に規制しつつ回転自在に保持する複数の円形の第２保持孔３２を周方向で等間隔置きに有している。   Between the opposing surfaces of the third transmission member 9 and the second transmission member 8 (second half 8b), an annular flat second holding member H2 is interposed. The second holding member H2 can maintain the engaged state of the plurality of second rolling balls 26 in both the transmission grooves 24 and 25 at the intersections of the third and fourth transmission grooves 24 and 25. In addition, a plurality of circular second holding holes 32 for holding the plurality of second rolling balls 26 rotatably while restricting the mutual interval between them are provided at equal intervals in the circumferential direction.

ところで、本実施形態において上記各伝動溝２１，２２，２４，２５は、溝幅が溝底に向かうにつれて徐々に減少する横断面形状、例えばＶ字状（図５参照）又はゴシックアーチ状に形成される。従って、その各伝動溝２１，２２，２４，２５の、転動ボール２３，２６との接点５３，５４は２点となり、転動ボール２３，２６が各伝動溝２１，２２，２４，２５を転動する際に、その両接点５３，５４の移動軌跡が伝動溝２１，２２，２４，２５の長手方向に沿う２条の曲線となる。   By the way, in the present embodiment, each of the transmission grooves 21, 22, 24, and 25 is formed in a cross-sectional shape that gradually decreases as the groove width approaches the groove bottom, for example, a V shape (see FIG. 5) or a Gothic arch shape. Is done. Accordingly, the contact points 53, 54 of the transmission grooves 21, 22, 24, 25 with the rolling balls 23, 26 are two points, and the rolling balls 23, 26 pass through the transmission grooves 21, 22, 24, 25. When rolling, the movement trajectory of both the contacts 53, 54 becomes two curves along the longitudinal direction of the transmission grooves 21, 22, 24, 25.

以上説明した本実施形態において、第１伝動溝２１の波数をＺ１、第２伝動溝２２の波数をＺ２、第３伝動溝２４の波数をＺ３、第４伝動溝２５の波数をＺ４としたとき、下記式が成立するように、第１〜第４伝動溝２１，２２，２４，２５は形成される。
（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
望ましくは、図示例のように、Ｚ１＝８、Ｚ２＝６、Ｚ３＝６、Ｚ４＝４とするか、又はＺ１＝６、Ｚ２＝４、Ｚ３＝８、Ｚ４＝６とするとよい。 In the present embodiment described above, the wave number of the first transmission groove 21 is Z1, the wave number of the second transmission groove 22 is Z2, the wave number of the third transmission groove 24 is Z3, and the wave number of the fourth transmission groove 25 is Z4. The first to fourth transmission grooves 21, 22, 24, and 25 are formed so that the following expression is established.
(Z1 / Z2) × (Z3 / Z4) = 2
Desirably, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, and Z4 = 6 as shown in the illustrated example.

尚、図示例では、８波の第１伝動溝２１と６波の第２伝動溝２２とが７箇所で交差し、この７箇所の交差部（重なり部）に７個の第１転動ボール２３が介装され、また６波の第３伝動溝２４と４波の第４伝動溝２５とが５箇所で交差し、この５箇所の交差部（重なり部）に５個の第２転動ボール２６が介装される。   In the illustrated example, the eight-wave first transmission groove 21 and the six-wave second transmission groove 22 intersect at seven locations, and seven first rolling balls are formed at the seven intersections (overlapping portions). 23, and the 6-wave third transmission groove 24 and the 4-wave fourth transmission groove 25 intersect at five locations, and five second rolling motions at the five intersections (overlapping portions). A ball 26 is interposed.

而して、第１伝動溝２１、第２伝動溝２２及び第１転動ボール２３は互いに協働して、第１伝動部材５及び第２伝動部材８間で変速しつつトルク伝達可能な第１変速機構Ｔ１を構成し、また第３伝動溝２４、第４伝動溝２５及び第２転動ボール２６は互いに協働して、第２伝動部材８及び第３伝動部材９間で変速しつつトルク伝達可能な第２変速機構Ｔ２を構成する。   Thus, the first transmission groove 21, the second transmission groove 22, and the first rolling ball 23 cooperate with each other and can transmit torque while shifting between the first transmission member 5 and the second transmission member 8. The first transmission mechanism T1 is configured, and the third transmission groove 24, the fourth transmission groove 25, and the second rolling ball 26 cooperate with each other while shifting between the second transmission member 8 and the third transmission member 9. A second transmission mechanism T2 capable of transmitting torque is configured.

ところで、図１，図３及び図５に示すように、少なくとも一方の変速機構（本実施形態では第２変速機構Ｔ２）の潤滑性を更に高めるために、各々環状をなす第１〜第３伝動部材５，８，９のうち少なくとも一つの伝動部材（本実施形態では第２伝動部材８）には、その伝動部材８（より具体的には第２半体８ｂ）の内周部に油入口５１が開口し且つその伝動部材８（第２半体８ｂ）の伝動溝２４に油出口５２が開口した潤滑油路５０が設けられる。   By the way, as shown in FIGS. 1, 3 and 5, in order to further improve the lubricity of at least one speed change mechanism (second speed change mechanism T2 in this embodiment), first to third transmissions each having an annular shape. At least one transmission member (second transmission member 8 in the present embodiment) among the members 5, 8, and 9 has an oil inlet at the inner peripheral portion of the transmission member 8 (more specifically, the second half 8b). A lubricating oil passage 50 having an oil outlet 52 opened is provided in the transmission groove 24 of the transmission member 8 (second half 8b).

この潤滑油路５０は、周方向に間隔をおいて複数配設される。そして、その一部の複数の潤滑油路５０の油出口５２は、図３に示すようにハイポトロコイド曲線に沿って延びる第３伝動溝２４の、径方向外側に凸の曲率急変部に開口し、またその残余の油出口５２は、第３伝動溝２４の、相隣なる曲率急変部の中間位置に開口している。しかもその各々の油出口５２は、本実施形態では、第３伝動溝２４と第２転動ボール２６との接点５３，５４の移動軌跡を避けるように第３伝動溝２４の溝底に開口している。   A plurality of the lubricating oil passages 50 are arranged at intervals in the circumferential direction. Then, the oil outlets 52 of some of the plurality of lubricating oil passages 50 open to a suddenly changing curvature portion that protrudes radially outward of the third transmission groove 24 extending along the hypotrochoid curve as shown in FIG. Further, the remaining oil outlet 52 opens at an intermediate position of the adjacent suddenly changing curvature portion of the third transmission groove 24. In addition, in the present embodiment, each of the oil outlets 52 opens to the groove bottom of the third transmission groove 24 so as to avoid the movement locus of the contacts 53 and 54 between the third transmission groove 24 and the second rolling ball 26. ing.

各々の潤滑油路５０は、第２伝動部材８における第２半体８ｂの内、外周面に両端が開口するよう放射状に延びる縦油路部分５０ａと、その縦油路部分５０ａの中間部を横切って該中間部に直接連通するように第１軸線Ｘ１と平行に延びる横油路部分５０ｂとで構成される。各々の縦油路部分５０ａの径方向内端は第２半体８ｂの内周面に開口して油入口５１となり、また縦油路部分５０ａの径方向外端は、第２伝動部材８の円筒状連結部材８ｃにより閉塞される。また縦油路部分５０ａ及び横油路部分５０ｂは、本実施形態では何れも直線孔であるため、ドリル加工により容易に形成可能である。   Each of the lubricating oil passages 50 includes a vertical oil passage portion 50a radially extending so that both ends are open on the outer peripheral surface of the second half 8b of the second transmission member 8, and an intermediate portion of the vertical oil passage portion 50a. It is comprised by the horizontal oil path part 50b extended in parallel with the 1st axis line X1 so that it may communicate directly with this intermediate part across. The radially inner end of each vertical oil passage portion 50a opens to the inner peripheral surface of the second half 8b to be an oil inlet 51, and the radially outer end of the vertical oil passage portion 50a is the second transmission member 8's. It is closed by a cylindrical connecting member 8c. In addition, since the vertical oil passage portion 50a and the horizontal oil passage portion 50b are both straight holes in this embodiment, they can be easily formed by drilling.

また各々の横油路部分５０ｂは、その一端が第３伝動溝２４の溝底に開口して油出口５２となり、また横油路部分５０ｂの他端は、そこに圧入した栓体５５で閉塞される。尚、栓体５５は、本実施形態ではボール状栓体を用いたが、ボール以外の種々の形態（例えばピン状）の栓体であってもよい。   In addition, each side oil passage portion 50b has one end opened to the groove bottom of the third transmission groove 24 to be an oil outlet 52, and the other end of the side oil passage portion 50b is blocked by a plug 55 press-fitted therein. Is done. In addition, although the ball-shaped plug body was used for the plug body 55 in this embodiment, plug bodies of various forms (for example, pin shape) other than the ball may be used.

次に、前記第１実施形態の作用について説明する。   Next, the operation of the first embodiment will be described.

いま、例えば右方の第１駆動車軸Ｓ１を固定することで偏心回転部材６（従って偏心軸部６ｅ）を固定した状態において、エンジンからの動力でリングギヤＣｇが駆動され、デフケースＣ、従って第１伝動部材５を第１軸線Ｘ１回りに回転させると、第１伝動部材５の８波の第１伝動溝２１が第２伝動部材８の６波の第２伝動溝２２を第１転動ボール２３を介して駆動するので、第１伝動部材５が８／６の増速比を以て第２伝動部材８を駆動することになる。そして、この第２伝動部材８の回転によれば、第２伝動部材８の６波の第３伝動溝２４が第３伝動部材９のリング板部９ｃの４波の第４伝動溝２５を第２転動ボール２６を介して駆動するので、第２伝動部材８が６／４の増速比を以て第３伝動部材９を駆動することになる。   Now, for example, in a state where the eccentric rotary member 6 (and hence the eccentric shaft portion 6e) is fixed by fixing the right first drive axle S1, the ring gear Cg is driven by the power from the engine, and the differential case C and therefore the first When the transmission member 5 is rotated about the first axis X 1, the eight-wave first transmission groove 21 of the first transmission member 5 passes through the six-wave second transmission groove 22 of the second transmission member 8 to the first rolling ball 23. Therefore, the first transmission member 5 drives the second transmission member 8 with a speed increasing ratio of 8/6. According to the rotation of the second transmission member 8, the six-wave third transmission groove 24 of the second transmission member 8 replaces the four-wave fourth transmission groove 25 of the ring plate portion 9 c of the third transmission member 9. Since it is driven via the two rolling balls 26, the second transmission member 8 drives the third transmission member 9 with a speed increasing ratio of 6/4.

結局、第１伝動部材５は、
（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝（８／６）×（６／４）＝２
の増速比を以て第３伝動部材９を駆動することになる。 After all, the first transmission member 5 is
(Z1 / Z2) × (Z3 / Z4) = (8/6) × (6/4) = 2
The third transmission member 9 is driven with the speed increasing ratio.

一方、左方の第２駆動車軸Ｓ２を固定することで第３伝動部材９を固定した状態において、デフケース（従って第１伝動部材５）を回転させると、第１伝動部材５の回転駆動力と、第２伝動部材８の、不動の第３伝動部材９に対する駆動反力とにより、第２伝動部材８は、偏心回転部材６の偏心軸部６ｅ（第２軸線Ｘ２）に対し自転しながら第１軸線Ｘ１回りに公転して、偏心軸部６ｅを第１軸線Ｘ１回りに駆動する。その結果、第１伝動部材５は、２倍の増速比を以て偏心回転部材６を駆動することになる。   On the other hand, when the differential case (and hence the first transmission member 5) is rotated in the state where the third transmission member 9 is fixed by fixing the left second driving axle S2, the rotational driving force of the first transmission member 5 Due to the driving reaction force of the second transmission member 8 against the stationary third transmission member 9, the second transmission member 8 rotates while rotating about the eccentric shaft portion 6 e (second axis X 2) of the eccentric rotation member 6. Revolving around one axis line X1 drives the eccentric shaft portion 6e around the first axis line X1. As a result, the first transmission member 5 drives the eccentric rotating member 6 with a double speed increasing ratio.

而して、偏心回転部材６及び第３伝動部材９の負荷が相互にバランスしたり、相互に変化したりすると、第２伝動部材８の自転量及び公転量が無段階に変化し、偏心回転部材６及び第３伝動部材９の回転数の平均値が第１伝動部材５の回転数と等しくなる。こうして、第１伝動部材５の回転は、偏心回転部材６及び第３伝動部材９に分配され、したがってリングギヤＣｇからデフケースＣに伝達された回転力を左右の駆動車軸Ｓ１，Ｓ２に分配することができる。   Thus, when the loads of the eccentric rotating member 6 and the third transmission member 9 are balanced with each other or change with each other, the amount of rotation and the amount of revolution of the second transmission member 8 change steplessly, and the eccentric rotation The average value of the rotational speeds of the member 6 and the third transmission member 9 is equal to the rotational speed of the first transmission member 5. Thus, the rotation of the first transmission member 5 is distributed to the eccentric rotation member 6 and the third transmission member 9, so that the rotational force transmitted from the ring gear Cg to the differential case C can be distributed to the left and right drive axles S1, S2. it can.

その際、Ｚ１＝８、Ｚ２＝６、Ｚ３＝６、Ｚ４＝４とするか、又はＺ１＝６、Ｚ２＝４、Ｚ３＝８、Ｚ４＝６とすることにより、差動機能を確保しつゝ構造の簡素化を図ることができる。   At that time, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, Z4 = 6 to ensure the differential function. Simplification of the eaves structure can be achieved.

ところで、この差動装置Ｄにおいて、第１伝動部材５の回転トルクは、第１伝動溝２１、複数の第１転動ボール２３及び第２伝動溝２２を介して第２伝動部材８に、また第２伝動部材８の回転トルクは、第３伝動溝２４、複数の第２転動ボール２６及び第４伝動溝２５を介して第３伝動部材９にそれぞれ伝達されるので、第１伝動部材５と第２伝動部材８、第２伝動部材８と第３伝動部材９の各間では、トルク伝達が第１及び第２転動ボール２３，２６が存在する複数箇所に分散して行われることになり、第１〜第３伝動部材５，８，９及び第１、第２転動ボール２３，２６等の各伝動要素の強度増及び軽量化を図ることができる。   By the way, in this differential device D, the rotational torque of the first transmission member 5 is applied to the second transmission member 8 via the first transmission groove 21, the plurality of first rolling balls 23 and the second transmission groove 22, and The rotational torque of the second transmission member 8 is transmitted to the third transmission member 9 via the third transmission groove 24, the plurality of second rolling balls 26 and the fourth transmission groove 25, respectively. Torque transmission between the second transmission member 8 and the second transmission member 8 and the third transmission member 9 is performed at a plurality of locations where the first and second rolling balls 23 and 26 exist. Thus, the strength and weight of each transmission element such as the first to third transmission members 5, 8, 9 and the first and second rolling balls 23, 26 can be increased.

しかもこの差動装置Ｄは、第１〜第３伝動部材５，８，９を各々、軸方向に極力扁平化することが可能であり、また第１、第２伝動部材５，８の相対向面間の第１変速機構Ｔ１と、第２、第３伝動部材８，９の相対向面間の第２変速機構Ｔ２とが、偏心回転部材６を固定したときに第１伝動部材５から第３伝動部材９を２倍の増速比を以て駆動するように構成される。従って、軸方向に容易に扁平小型化し得る差動装置Ｄが得られる。   In addition, the differential device D can flatten the first to third transmission members 5, 8, 9 in the axial direction as much as possible, and is opposed to the first and second transmission members 5, 8. The first transmission mechanism T1 between the surfaces and the second transmission mechanism T2 between the opposing surfaces of the second and third transmission members 8 and 9 are connected to the first transmission member 5 when the eccentric rotation member 6 is fixed. 3 The transmission member 9 is configured to be driven with a double speed increasing ratio. Therefore, the differential device D that can be easily flattened in the axial direction can be obtained.

また、この差動装置Ｄの作動中は、前述のようにミッションケース１底部の貯溜潤滑油がデフケースＣ等に掻き回されてミッションケース１内に広範囲に飛散し、その飛散潤滑油の一部は、デフケースＣのハブＨＢ１，ＨＢ２と駆動車軸Ｓ１，Ｓ２との相対回転に伴う第１及び第２螺旋溝１８，１９の引き込み作用により、デフケースＣ内にその両側から積極的に供給される。   During the operation of the differential device D, as described above, the stored lubricating oil at the bottom of the transmission case 1 is stirred by the differential case C or the like and scattered widely within the transmission case 1, and a part of the scattered lubricating oil. Is actively supplied into the differential case C from both sides by the pulling action of the first and second spiral grooves 18 and 19 associated with the relative rotation between the hubs HB1 and HB2 of the differential case C and the drive axles S1 and S2.

このとき、特に第１螺旋溝１８の出口に達した潤滑油は、その一部が遠心力の作用で油路４１を経由して第１変速機構Ｔ１の内周側及び偏心軸部６ｅ上の軸受７に流動し、第１スラストワッシャＴＨ１や第１変速機構Ｔ１及び軸受７を潤滑する。   At this time, in particular, a part of the lubricating oil that has reached the outlet of the first spiral groove 18 passes through the oil passage 41 by the action of centrifugal force, and on the inner peripheral side of the first transmission mechanism T1 and on the eccentric shaft portion 6e. It flows to the bearing 7 and lubricates the first thrust washer TH1, the first transmission mechanism T1, and the bearing 7.

一方、第２螺旋溝１９の出口に達した潤滑油は、その一部が遠心力の作用で油路４５を経て第２スラストワッシャＴＨ２に向かい同ワッシャを潤滑する。またその潤滑油の残部は、スプライン嵌合部１７（主としスプライン欠歯部）を通して第３伝動部材９の内方空間に導入され、その導入潤滑油の一部は、遠心力で径方向外方に流動して第２変速機構Ｔ２の内周側（即ち第２保持部材Ｈ２の内周側、並びに第２伝動部材８の第２半体８ｂの各内周側）に向かって流動し、それらを潤滑する。   On the other hand, a part of the lubricating oil that has reached the outlet of the second spiral groove 19 lubricates the washer toward the second thrust washer TH2 through the oil passage 45 by the action of centrifugal force. Further, the remaining portion of the lubricating oil is introduced into the inner space of the third transmission member 9 through the spline fitting portion 17 (mainly the spline missing tooth portion), and a part of the introduced lubricating oil is radially outside by centrifugal force. Flow toward the inner peripheral side of the second transmission mechanism T2 (that is, the inner peripheral side of the second holding member H2 and the inner peripheral side of the second half 8b of the second transmission member 8), Lubricate them.

ところで本実施形態の第２伝動部材８、特に第２半体８ｂには、それの内周部に油入口５１が開口し且つそれの第３伝動溝２４に油出口５２が開口した複数の潤滑油路５０が周方向に間隔をおいて配設されている。このため、差動装置Ｄの作動中、ミッションケース１内からデフケースＣ内に引き込まれた潤滑油の一部が上述のようにして第２半体８ｂの内周部に達すると、その油が第２伝動部材８の回転による遠心力で、該内周部に開口する油入口５１から潤滑油路５０にスムーズに流入し、更にその潤滑油路５０を油出口５２側に向かって効率よく流動して第３伝動溝２４内、延いては第２変速機構Ｔ２全域に効率よく供給される。   By the way, the second transmission member 8 of the present embodiment, particularly the second half 8b, has a plurality of lubrications in which an oil inlet 51 is opened in the inner peripheral portion thereof and an oil outlet 52 is opened in the third transmission groove 24 thereof. Oil passages 50 are arranged at intervals in the circumferential direction. For this reason, when a part of the lubricating oil drawn into the differential case C from the transmission case 1 reaches the inner peripheral portion of the second half 8b as described above during the operation of the differential gear D, the oil is The centrifugal force generated by the rotation of the second transmission member 8 smoothly flows into the lubricating oil passage 50 from the oil inlet 51 that opens to the inner peripheral portion, and further flows efficiently through the lubricating oil passage 50 toward the oil outlet 52 side. Then, the air is efficiently supplied in the third transmission groove 24, and in other words, throughout the second transmission mechanism T2.

かくして、遠心力を利用した簡単な構造で第２転動ボール２６と第３，第４伝動溝２４，２５との接触部等を効果的に潤滑可能となるから、第２変速機構Ｔ２、延いては差動装置Ｄの伝動効率アップが図られる。特に、本実施形態では、第２保持部材Ｈ２が第３，第４伝動溝２４，２５の間に介在しているため、第３，第４伝動溝２４，２５内への溝開口側からの潤滑油供給が妨げられる可能性があるが、本実施形態によれば、潤滑油路５０を経由して各溝２４，２５内に溝底側から潤滑油を供給できる。   Thus, the contact portion between the second rolling ball 26 and the third and fourth transmission grooves 24 and 25 can be effectively lubricated with a simple structure using centrifugal force. Thus, the transmission efficiency of the differential device D can be increased. In particular, in the present embodiment, since the second holding member H2 is interposed between the third and fourth transmission grooves 24 and 25, the groove from the groove opening side into the third and fourth transmission grooves 24 and 25 is provided. Although there is a possibility that the supply of the lubricating oil may be hindered, according to the present embodiment, the lubricating oil can be supplied into the grooves 24 and 25 from the groove bottom side via the lubricating oil passage 50.

また、本実施形態の第３，第４伝動溝２４，２５は、それの、転動ボール２３，２６との接点５３，５４が２点となるよう溝幅が溝底に向かうにつれて減少する断面形状を有している上、各潤滑油路５０の油出口５２は、接点軌跡を避けるように第３伝動溝２４の溝底に開口している。これにより、油出口５２の形成に起因した、第３伝動溝２４のボール軌道部とその周辺部の損傷が効果的に回避可能となるから、第３伝動溝２４における第２転動ボール２６のスムーズな転動が確保可能となる。しかも潤滑油が第３伝動溝２４の特に溝底に供給されることで、その溝底の両側に存するボール軌道部を効果的に潤滑可能となる。   Further, the third and fourth transmission grooves 24 and 25 of the present embodiment have a cross section in which the groove width decreases toward the groove bottom so that the contact points 53 and 54 with the rolling balls 23 and 26 become two points. In addition to having a shape, the oil outlet 52 of each lubricating oil passage 50 opens at the groove bottom of the third transmission groove 24 so as to avoid the contact locus. Thereby, damage to the ball raceway portion of the third transmission groove 24 and its peripheral portion due to the formation of the oil outlet 52 can be effectively avoided, so that the second rolling ball 26 in the third transmission groove 24 can be avoided. Smooth rolling can be ensured. In addition, since the lubricating oil is supplied to the third transmission groove 24, particularly to the groove bottom, the ball raceways existing on both sides of the groove bottom can be effectively lubricated.

また図６に本発明の第２実施形態が示される。この第２実施形態では、少なくとも１つの伝動部材（本実施形態では第２伝動部材８の第２半体８ｂ）に周方向に間隔をおいて配設される複数の潤滑油路５０の配置、特に油出口５２の開口位置のみが第１実施形態と異なる。即ち、第２実施形態の油出口５２は、第３伝動溝２４と第２転動ボール２６との接点５３，５４の移動軌跡を避けるように、第３伝動溝２４の、溝開口縁の近傍（即ち溝開口縁と一方の接点５４の移動軌跡との間）の内面に開口している。   FIG. 6 shows a second embodiment of the present invention. In the second embodiment, an arrangement of a plurality of lubricating oil passages 50 arranged at intervals in the circumferential direction on at least one transmission member (in this embodiment, the second half 8b of the second transmission member 8), In particular, only the opening position of the oil outlet 52 is different from the first embodiment. That is, the oil outlet 52 of the second embodiment is located near the groove opening edge of the third transmission groove 24 so as to avoid the movement trajectory of the contacts 53 and 54 between the third transmission groove 24 and the second rolling ball 26. It opens to the inner surface (that is, between the groove opening edge and the movement locus of one contact 54).

また図７に本発明の第３実施形態が示される。この第３実施形態では、複数の潤滑油路５０が設けられる少なくとも１つの伝動部材（本実施形態では第２伝動部材８の第２半体８ｂ）の内周面の形態のみが第１実施形態と異なる。即ち、第３実施形態の第２伝動部材８の第２半体８ｂの内周面には、その全周に亘って連続する環状溝６０が凹設される。その環状溝６０の底面には、複数の潤滑油路５０の油入口５１が周方向に間隔をおいて開口する。   FIG. 7 shows a third embodiment of the present invention. In the third embodiment, only the form of the inner peripheral surface of at least one transmission member (in this embodiment, the second half 8b of the second transmission member 8) provided with a plurality of lubricating oil passages 50 is the first embodiment. And different. That is, an annular groove 60 that is continuous over the entire circumference is recessed in the inner circumferential surface of the second half 8b of the second transmission member 8 of the third embodiment. On the bottom surface of the annular groove 60, oil inlets 51 of the plurality of lubricating oil passages 50 open at intervals in the circumferential direction.

而して、第３実施形態の環状溝６０は、複数の潤滑油路５０の油入口５１の相互間を連通させるので、第２伝動部材８（第２半体８ｂ）の内周面に達した潤滑油を環状溝６０で効率よく捕捉して複数の潤滑油路５０に満遍なく分配可能となり、これにより、第３伝動溝２４を広範囲に亘り偏りなく効果的に潤滑可能となる。尚、その環状溝６０の一側端及び他側端は第２半体８ｂの軸方向一側面及び他側面にそれぞれ達していて、環状溝６０内（延いては潤滑油路５０内）に第２半体８ｂの軸方向両側より潤滑油を効率よく導入可能な構造となっている。   Thus, the annular groove 60 of the third embodiment communicates between the oil inlets 51 of the plurality of lubricating oil passages 50, and thus reaches the inner peripheral surface of the second transmission member 8 (second half 8b). The obtained lubricating oil is efficiently captured by the annular groove 60 and can be evenly distributed to the plurality of lubricating oil passages 50, whereby the third transmission groove 24 can be effectively lubricated without deviation over a wide range. Note that one end and the other end of the annular groove 60 reach the one side surface and the other side surface in the axial direction of the second half 8b, respectively, and the second end in the annular groove 60 (and in the lubricating oil passage 50). The lubricating oil can be efficiently introduced from both axial sides of the half body 8b.

以上、本発明の実施形態を説明したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。   As mentioned above, although embodiment of this invention was described, this invention can perform a various design change in the range which does not deviate from the summary.

例えば、前記実施形態では、伝動装置として差動装置Ｄを例示し、動力源からデフケースＣ（第１伝動部材５）に入力された動力を、第１，第２変速機構Ｔ１，Ｔ２を介して第１，第２駆動車軸Ｓ１，Ｓ２（ドライブ軸）に差動回転を許容しつつ分配するようにしたものを示したが、本発明は差動装置以外の種々の伝動装置にも実施可能である。例えば、前記実施形態のデフケースＣに対応するケーシングを固定の伝動ケースとし、第１，第２駆動車軸Ｓ１，Ｓ２の何れか一方を入力軸、またその何れか他方を出力軸とすることで、前記実施形態の差動装置Ｄを、入力軸に入力される回転トルクを変速（減速又は増速）して出力軸に伝達し得る変速機（減速機又は増速機）として転用実施可能であり、その場合には、そのような変速機（減速機又は増速機）が本発明の伝動装置となる。尚、この場合、変速機は、車両用の変速機でも、或いは車両以外の種々の機械装置のための変速機であってもよい。   For example, in the above embodiment, the differential device D is exemplified as the transmission device, and the power input from the power source to the differential case C (first transmission member 5) is transmitted via the first and second transmission mechanisms T1 and T2. Although the first and second drive axles S1 and S2 (drive shafts) are distributed while allowing differential rotation, the present invention can be implemented in various transmission devices other than the differential gear. is there. For example, the casing corresponding to the differential case C of the above embodiment is a fixed transmission case, one of the first and second drive axles S1, S2 is an input shaft, and one of the other is an output shaft. The differential device D of the embodiment can be diverted as a transmission (decelerator or speed increaser) that can change (decelerate or increase speed) the rotational torque input to the input shaft and transmit it to the output shaft. In such a case, such a transmission (reduction gear or speed increaser) is the transmission device of the present invention. In this case, the transmission may be a transmission for a vehicle or a transmission for various mechanical devices other than the vehicle.

また、前記実施形態では、伝動装置としての差動装置Ｄを自動車用として自動車のミッションケースＭ内に収容しているが、差動装置Ｄは自動車用の差動装置に限定されるものではなく、種々の機械装置のための差動装置としても実施可能である。   Moreover, in the said embodiment, although the differential device D as a transmission device is accommodated in the mission case M of a motor vehicle for vehicles, the differential device D is not limited to the differential device for motor vehicles. It can also be implemented as a differential for various mechanical devices.

また、前記実施形態では、伝動装置としての差動装置Ｄを、左・右輪伝動系に適用して、左右の駆動車軸Ｓ１，Ｓ２に対して差動回転を許容しつつ動力を分配するものを示したが、本発明では、伝動装置としての差動装置を、前・後輪駆動車両における前・後輪伝動系に適用して、前後の駆動車輪に対し差動回転を許容しつつ動力を分配できるようにしてもよい。   In the above embodiment, the differential device D as a transmission device is applied to the left and right wheel transmission systems to distribute power while allowing differential rotation to the left and right drive axles S1, S2. However, in the present invention, a differential device as a transmission device is applied to a front / rear wheel transmission system in a front / rear wheel drive vehicle to allow power to be driven while allowing differential rotation with respect to front and rear drive wheels. May be distributed.

また前記実施形態の第２伝動部材８は、第１，第２半体８ａ，８ｂ及び連結部材８ｃから構成されていたが、第２伝動部材８は、一体物の板状部材の一方の面に第２伝動溝２２が、また他方の面に第３伝動溝２４がそれぞれ設けられたものであってもよい。尚、この場合、１枚の板状部材からなる第２伝動部材８に前記実施形態と同様の複数の潤滑油路５０が、周方向に互いに間隔をおいて、しかも油入口５１が軸受７を避けた位置に開口されるようにして、配設される。この場合、油出口５２は、第２伝動溝２２及び第３伝動溝２４の各々に設けてもよいし、或いは、何れか一方の伝動溝２２又は２４だけに設けてもよい。   Moreover, although the 2nd transmission member 8 of the said embodiment was comprised from the 1st, 2nd half bodies 8a and 8b and the connection member 8c, the 2nd transmission member 8 is one surface of the plate-shaped member of an integral thing. Alternatively, the second transmission groove 22 may be provided, and the third transmission groove 24 may be provided on the other surface. In this case, a plurality of lubricating oil passages 50 similar to those of the above-described embodiment are provided in the second transmission member 8 formed of a single plate-like member at intervals in the circumferential direction, and the oil inlet 51 is provided with the bearing 7. It arrange | positions so that it may open in the position avoided. In this case, the oil outlet 52 may be provided in each of the second transmission groove 22 and the third transmission groove 24 or may be provided only in one of the transmission grooves 22 or 24.

また、前記実施形態では、第１，第２変速機構Ｔ１，Ｔ２の各伝動溝２１，２２；２４，２５をトロコイド曲線に沿った波形環状の波溝としているが、これら伝動溝は、実施形態に限定されるものでなく、例えば、サイクロイド曲線に沿った波形環状の波溝としてもよい。   Moreover, in the said embodiment, although each transmission groove 21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the corrugated cyclic | annular wave groove along a trochoid curve, these transmission grooves are embodiment. For example, it is good also as a wave-shaped wave groove | channel along a cycloid curve.

また、前記実施形態では、第１，第２変速機構Ｔ１，Ｔ２の第１及び第２伝動溝２１，２２間、並びに第３及び第４伝動溝２４，２５間に第１及び第２転動体としての第１及び第２転動ボール２３，２６を介装したものを示したが、その転動体としてローラ状又はピン状の転動体を用いてもよく、この場合に、第１及び第２伝動溝２１，２２、並びに第３及び第４伝動溝２４，２５は、ローラ状又はピン状の転動体が転動し得るような内側面形状に形成される。   In the embodiment, the first and second rolling elements are provided between the first and second transmission grooves 21 and 22 and between the third and fourth transmission grooves 24 and 25 of the first and second transmission mechanisms T1 and T2. The first and second rolling balls 23 and 26 are interposed, but a roller-shaped or pin-shaped rolling element may be used as the rolling element. In this case, the first and second rolling balls may be used. The transmission grooves 21 and 22 and the third and fourth transmission grooves 24 and 25 are formed in an inner surface shape so that a roller-like or pin-like rolling element can roll.

また、前記実施形態では、第１，第２転動ボール２３，２６を円滑に転動させるために第１，第２保持部材Ｈ１，Ｈ２を用いたものを示したが、第１，第２保持部材Ｈ１，Ｈ２無しでも第１，第２転動ボール２３，２６が円滑に転動可能な場合は、第１，第２保持部材Ｈ１，Ｈ２を省略してもよい。   In the above embodiment, the first and second holding members H1 and H2 are used to smoothly roll the first and second rolling balls 23 and 26. When the first and second rolling balls 23 and 26 can smoothly roll without the holding members H1 and H2, the first and second holding members H1 and H2 may be omitted.

また前記実施形態では、偏心回転部材６及び第３伝動部材９を、デフケースＣに支持される駆動車軸Ｓ１，Ｓ２に接続（スプライン嵌合１６，１７）して、これら駆動車軸Ｓ１，Ｓ２を介してデフケースＣに支持させるようにしたものを示したが、本発明では、偏心回転部材６及び第３伝動部材９をデフケースＣに直接支持させるようにしてもよい。   In the above-described embodiment, the eccentric rotating member 6 and the third transmission member 9 are connected to the drive axles S1 and S2 supported by the differential case C (spline fittings 16 and 17), and the drive axles S1 and S2 are interposed therebetween. In the present invention, the eccentric rotation member 6 and the third transmission member 9 may be directly supported by the differential case C.

また前記実施形態では、第１，第２保持部材Ｈ１，Ｈ２を、内・外周面が各々真円の円環状リングより構成したものを示したが、本発明の第１，第２保持部材の形状は、前記実施形態に限定されず、少なくとも複数の第１，第２転動ボール２３，２６を各々一定間隔で保持し得る環状体であればよく、例えば楕円状の環状体、或いは波形に湾曲した環状体であってもよい。   In the above-described embodiment, the first and second holding members H1 and H2 are configured by circular rings having inner and outer peripheral surfaces each having a perfect circle. The shape is not limited to the above-described embodiment, and may be any annular body that can hold at least a plurality of first and second rolling balls 23 and 26 at regular intervals, for example, an elliptical annular body or a waveform. A curved annular body may be used.

さらに、前記実施形態では、少なくとも一方の変速機構Ｔ１，Ｔ２の潤滑性能を高めるための潤滑油路５０を、第２伝動部材８（第２半体８ｂ）にのみ設けたものを示したが、本発明では、この構造に加えて（又は代えて）、他の伝動部材即ち第１，第３伝動部材５，９のうちの少なくとも一方に、同様の潤滑油路を設けるようにしてもよい。例えば、図１の二点鎖線で示す第４実施形態のように、潤滑油路５０′を第３伝動部材９に設けて、それの油入口５１を第３伝動部材９の内周面（例えば主軸部９ａ内周のスプライン歯（望ましくはスプライン欠歯部）に開口させ、且つその油出口５２を第４伝動溝２５に開口させるようにしてもよい。また、例えば、図１の二点鎖線で示す第５実施形態のように、潤滑油路５０″を第１伝動部材５に設けて、それの油入口５１を第１伝動部材５の内周面（油路４１に臨む部分）に開口させ、且つその油出口５２を第１伝動溝２１に開口させるようにしてもよい。   Furthermore, in the said embodiment, although what showed the lubricating oil path 50 for improving the lubricating performance of at least one transmission mechanism T1, T2 only in the 2nd transmission member 8 (2nd half body 8b) was shown, In the present invention, in addition to (or instead of) this structure, a similar lubricating oil passage may be provided in at least one of the other transmission members, that is, the first and third transmission members 5 and 9. For example, as in the fourth embodiment shown by a two-dot chain line in FIG. 1, a lubricating oil passage 50 ′ is provided in the third transmission member 9, and its oil inlet 51 is connected to the inner peripheral surface of the third transmission member 9 (for example, An opening may be provided in the spline teeth (desirably, spline missing teeth) on the inner periphery of the main shaft portion 9a, and the oil outlet 52 thereof may be opened in the fourth transmission groove 25. For example, the two-dot chain line in FIG. As shown in the fifth embodiment, a lubricating oil passage 50 ″ is provided in the first transmission member 5, and an oil inlet 51 thereof is opened on the inner peripheral surface of the first transmission member 5 (part facing the oil passage 41). The oil outlet 52 may be opened in the first transmission groove 21.

また前記実施形態（第１〜第３実施形態）では、潤滑油路５０の縦油路部分５０ａの外端開口を、第２伝動部材８の第２半体８ｂ外周を囲繞する連結部材８ｃで閉塞するようにしているが、連結部材８ｃが縦油路部分５０ａの外端開口を閉塞し得ない形状・位置である場合には、その縦油路部分５０ａの外端開口を、栓体５５と同様の専用栓体で閉塞するようにしてもよい。   In the embodiment (first to third embodiments), the outer end opening of the vertical oil passage portion 50a of the lubricating oil passage 50 is connected to the outer periphery of the second half 8b of the second transmission member 8 by the connecting member 8c. When the connecting member 8c has a shape and position where the outer end opening of the vertical oil passage portion 50a cannot be closed, the outer end opening of the vertical oil passage portion 50a is plugged into the plug body 55. You may make it obstruct | occlude with the same exclusive stopper.

Ｃ・・・・・・デフケース（伝動ケース）
Ｄ・・・・・・差動装置（伝動装置）
Ｔ１，Ｔ２・・第１，第２変速機構（変速機構）
Ｘ１，Ｘ２・・第１，第２軸線
５，９・・・・第１伝動部材（第１の伝動部材）
６・・・・・・偏心回転部材
８・・・・・・第２伝動部材（第２の伝動部材）
９・・・・・・第３伝動部材（第１の伝動部材）
２１，２５・・第１，第４伝動溝（第１の伝動溝）
２２，２４・・第２，第３伝動溝（第２の伝動溝）
２３，２６・・第１，第２転動ボール（転動体）
５０・・・・・潤滑油路
５１，５２・・油入口，油出口
５３，５４・・接点
６０・・・・・環状溝 C ・ ・ ・ ・ ・ ・ Differential case (Transmission case)
D ・ ・ ・ ・ ・ ・ Differential device (Transmission device)
T1, T2, ... 1st and 2nd transmission mechanism (transmission mechanism)
X1, X2, ···, first and second axes 5, 9, ··· first transmission member (first transmission member)
6... Eccentric rotating member 8... 2nd transmission member (second transmission member)
9 .... Third transmission member (first transmission member)
21, 25 .. 1st and 4th transmission groove (1st transmission groove)
22, 24 ... Second and third transmission grooves (second transmission grooves)
23, 26 .. First and second rolling balls (rolling elements)
50... Lubricating oil passage 51, 52 ..oil inlet, oil outlet 53, 54 .. contact 60.

Claims (3)

第１軸線（Ｘ１）回りに回転する第１の伝動部材（５，９）と、
その第１の伝動部材（５，９）に対向配置されて、第１軸線（Ｘ１）から偏心した第２軸線（Ｘ２）回りを自転しながら第１軸線（Ｘ１）回りに公転し得る第２の伝動部材（８）と、
前記第１の伝動部材（５，９）及び前記第２の伝動部材（８）の相互間に設けられて、その両伝動部材（５，９；８）間で変速しつつトルク伝達可能な変速機構（Ｔ１，Ｔ２）とを備え、
前記変速機構（Ｔ１，Ｔ２）が、前記第１の伝動部材（５，９）の、前記第２の伝動部材（８）との対向面に在り且つ第１軸線（Ｘ１）を中心とする波形環状の第１の伝動溝（２１，２５）と、前記第２の伝動部材（８）の、前記第１の伝動部材（５，９）との対向面に在り且つ第２軸線（Ｘ２）を中心とする波形環状で波数が前記第１の伝動溝（２１，２５）とは異なる第２の伝動溝（２２，２４）と、前記第１の伝動溝（２１，２５）及び前記第２の伝動溝（２２，２４）の複数の交差部に介装され、その両伝動溝（２１，２５；２２，２４）を転動しながら前記両伝動部材（５，９；８）間の変速伝動を行う複数の転動体（２３，２６）とを有する伝動装置であって、
前記第１の伝動部材（５，９）及び前記第２の伝動部材（８）のうちの少なくとも一方が環状であり、
前記少なくとも一方の環状の伝動部材（５，９；８）には、その伝動部材（５，９；８）の内周部に油入口（５１）が開口し且つその伝動部材（５，９；８）の伝動溝（２１，２５；２４）に油出口（５２）が開口した潤滑油路（５０′，５０″，５０）が設けられることを特徴とする伝動装置。 A first transmission member (5, 9) that rotates about a first axis (X1);
A second member disposed opposite to the first transmission member (5, 9) and capable of revolving around the first axis (X1) while rotating around the second axis (X2) eccentric from the first axis (X1). A transmission member (8) of
A shift that is provided between the first transmission member (5, 9) and the second transmission member (8) and that can transmit torque while shifting between the two transmission members (5, 9; 8). Mechanism (T1, T2),
The transmission mechanism (T1, T2) is on the surface of the first transmission member (5, 9) facing the second transmission member (8) and has a waveform centered on the first axis (X1). An annular first transmission groove (21, 25) and the second transmission member (8) are on the surface facing the first transmission member (5, 9) and the second axis (X2) is A second transmission groove (22, 24) having a corrugated annular shape and a wave number different from that of the first transmission groove (21, 25), the first transmission groove (21, 25), and the second transmission groove Shift transmission between the two transmission members (5, 9; 8) while interposing at a plurality of intersections of the transmission grooves (22, 24) and rolling the transmission grooves (21, 25; 22, 24). A plurality of rolling elements (23, 26) for performing
At least one of the first transmission member (5, 9) and the second transmission member (8) is annular;
The at least one annular transmission member (5, 9; 8) has an oil inlet (51) opened at the inner periphery of the transmission member (5, 9; 8) and the transmission member (5, 9; 8. A transmission device characterized in that a lubricating oil passage (50 ', 50 ", 50) having an oil outlet (52) opened is provided in the transmission groove (21, 25; 24) of 8). 前記転動体（２３，２６）がボールで構成される一方、前記両伝動溝（２１，２５；２２，２４）は、各伝動溝（２１，２５；２２，２４）の、前記ボール（２３，２６）との接点（５３，５４）が２点となるよう溝幅が溝底に向かうにつれて減少する断面形状を有しており、
前記油出口（５２）は、前記接点（５３，５４）の軌跡を避けるように前記少なくとも一方の環状の伝動部材（５，９；８）の伝動溝（２１，２５；２４）の溝底に開口していることを特徴とする請求項１に記載の伝動装置。 While the rolling elements (23, 26) are formed of balls, the two transmission grooves (21, 25; 22, 24) are formed in the balls (23, 25, 22, 24) of the respective transmission grooves (21, 25; 22, 24). 26) has a cross-sectional shape in which the groove width decreases toward the groove bottom so that the contacts (53, 54) with two points become two points,
The oil outlet (52) is formed in the groove bottom of the transmission groove (21, 25; 24) of the at least one annular transmission member (5, 9; 8) so as to avoid the locus of the contact (53, 54). The transmission device according to claim 1, wherein the transmission device is open. 前記少なくとも一方の環状の伝動部材（８）には、その周方向に間隔をおいて複数の前記潤滑油路（５０）が設けられ、それら潤滑油路（５０）の前記油入口（５１）を相互に連通させる環状溝（６０）が、前記少なくとも一方の環状の伝動部材（８）の内周面に凹設されることを特徴とする請求項１又は２に記載の伝動装置。   The at least one annular transmission member (8) is provided with a plurality of the lubricating oil passages (50) at intervals in the circumferential direction, and the oil inlet (51) of the lubricating oil passages (50) is provided. The transmission device according to claim 1, wherein annular grooves (60) communicating with each other are recessed in an inner peripheral surface of the at least one annular transmission member (8).

Images