WO2017094795A1 - Transmission device - Google Patents

Abstract

A transmission device in which a ring-shaped first holding member is interposed between first and second transmission members, said first holding member having a plurality of holding holes uniformly restricting the interval between a plurality of first rolling bodies so as to suppress sudden random movements of the first rolling bodies inside first and second transmission grooves, when passing through a section of the grooves having a sudden change in curvature, and allow the first rolling bodies to roll smoothly. In the transmission device: the ring-shaped first holding member (R1) provided between first and second transmission members (5, 8) has a plurality of first holding holes (31) that uniformly restrict the intervals between and rotatably hold the plurality of first rolling bodies (23); each section of first and second transmission grooves (21, 22) is always open to the inner peripheral side or the outer peripheral side of the first holding member (R1); and lubricating oil is permitted to flow through these openings (IN1, IN2) to inside the first and second transmission grooves (21, 22). As a result, lubrication of a transmission groove inner surface and the rolling bodies can occur unhindered even if the first holding member is present.

Description

伝動装置Transmission

　本発明は、伝動装置、特に第１軸線を中心軸線とするように配置された第１伝動部材と、第１軸線回りに回転可能な主軸部、および第１軸線から偏心した第２軸線を中心軸線とする偏心軸部が互いに一体に連結された偏心回転部材と、その偏心軸部に回転自在に支持される第２伝動部材と、第１及び第２伝動部材間で変速しつつトルク伝達可能な第１変速機構とを伝動ケース内に備えた伝動装置に関する。 The present invention is centered on a transmission device, particularly a first transmission member arranged so that the first axis is a central axis, a main shaft portion rotatable around the first axis, and a second axis eccentric from the first axis. Torque can be transmitted while shifting between the first and second transmission members, an eccentric rotation member in which the eccentric shaft portions serving as axes are integrally connected to each other, a second transmission member rotatably supported by the eccentric shaft portion The present invention relates to a transmission device including a first transmission mechanism in a transmission case.

　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、上記第１変速機構が、第１伝動部材の第２伝動部材との対向面に第１軸線を中心として形成される波形環状の第１伝動溝と、第２伝動部材の第１伝動部材との対向面に第２軸線を中心として形成される、波形環状で波数が第１伝動溝とは異なる第２伝動溝と、第１及び第２伝動溝の複数の交差部にそれぞれ介装されて、第１及び第２伝動溝を転動しながら第１及び第２伝動部材間の変速伝動に関与する複数の転動ボールとより構成されている。 The transmission device is conventionally known as disclosed in, for example, Patent Document 1. In this device, the first transmission mechanism is centered on the first axis on the surface of the first transmission member facing the second transmission member. A wave-shaped second wave number different from that of the first transmission groove is formed around the second axis on the surface of the corrugated ring-shaped first transmission groove and the first transmission member of the second transmission member. A plurality of transmission grooves and a plurality of crossing portions of the first and second transmission grooves, respectively, which are involved in the transmission of the first and second transmission members while rolling on the first and second transmission grooves. It consists of rolling balls.

日本特許第４８１４３５１号公報Japanese Patent No. 4814351 日本特開２０１０－１４２１４号公報Japanese Unexamined Patent Publication No. 2010-14214

　ところで特許文献１の伝動装置では、転動ボールが第１、第２伝動溝の各々の曲率急変部を通過する際に、溝内で転動ボールが多少とも暴れてスムーズな溝通過の妨げとなり、延いては伝動効率を低下させる虞れがある。 By the way, in the transmission device of Patent Document 1, when the rolling ball passes through the suddenly changing portions of the first and second transmission grooves, the rolling ball is somewhat violated in the groove and hinders smooth passage of the groove. As a result, the transmission efficiency may be reduced.

　そこで、この問題を解決すべく転動ボールが伝動溝の曲率急変部を通過する際に溝内での暴れが抑制されてスムーズに転動できるようにするために、複数の転動ボール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保持孔を有した円環状の保持部材を第１及び第２伝動部材間に介装して、複数の転動ボールの、伝動溝相互の交差部での伝動溝への係合状態を維持し得るようにしたものが提案されている（特許文献２の図７参照）。 Therefore, in order to solve this problem, in order to prevent rolling in the groove and smoothly roll when the rolling ball passes through the sudden curvature change portion of the transmission groove, a plurality of rolling balls are mutually connected. An annular holding member having a plurality of holding holes that are rotatably held with a constant interval being interposed is interposed between the first and second transmission members, so that the plurality of rolling balls are connected to each other between the transmission grooves. The thing which can maintain the engagement state to the transmission groove in an intersection is proposed (refer to Drawing 7 of patent documents 2).

　ところが特許文献２のものでは、上記保持部材が各伝動溝の開口面に臨む配置であることから、その開口面を保持部材が塞いで溝内（従って転動ボール）に対する潤滑油供給の妨げとなる虞れがある。そして特許文献２には斯かる課題の所在や解決手段について何も開示されていない。 However, in Patent Document 2, since the holding member faces the opening surface of each transmission groove, the opening member is blocked by the holding member, and the supply of lubricating oil to the groove (and hence the rolling ball) is hindered. There is a risk of becoming. Patent Document 2 discloses nothing about the location and solution of such problems.

　本発明は、かかる事情に鑑みてなされたものであって、上記問題を一挙に解決することができる伝動装置を提供することを目的とする。 The present invention has been made in view of such circumstances, and an object thereof is to provide a transmission device that can solve the above-mentioned problems all at once.

　上記目的を達成するために、本発明は、第１軸線を中心軸線とするように配置された第１伝動部材と、第１軸線回りに回転可能な主軸部、および第１軸線から偏心した第２軸線を中心軸線とする偏心軸部が互いに一体に連結された偏心回転部材と、偏心軸部に回転自在に支持される第２伝動部材と、第１及び第２伝動部材間で変速しつつトルク伝達可能な第１変速機構とを伝動ケース内に備えており、第１変速機構が、第１伝動部材の第２伝動部材との対向面に第１軸線を中心として形成される波形環状の第１伝動溝と、第２伝動部材の第１伝動部材との対向面に第２軸線を中心として形成される、波形環状で波数が第１伝動溝とは異なる第２伝動溝と、第１及び第２伝動溝の複数の交差部にそれぞれ介装されて、第１及び第２伝動溝を転動しながら第１及び第２伝動部材間の変速伝動に関与する複数の第１転動体とを含む伝動装置において、第１及び第２伝動部材間には環状の第１保持部材が介装され、この第１保持部材は、複数の第１転動体の、第１及び第２伝動溝相互の交差部での両伝動溝への係合状態を維持し得るように該複数の第１転動体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第１保持孔を有しており、第１保持部材の内周側又は外周側には第１及び第２伝動溝の各一部が常に開口していて、その開口部を通して第１及び第２伝動溝内への潤滑油流動が許容されることを第１の特徴とする。 In order to achieve the above object, the present invention provides a first transmission member arranged so that the first axis is a central axis, a main shaft portion rotatable around the first axis, and a first shaft eccentric from the first axis. While shifting between the eccentric rotating member in which the eccentric shaft portions having the two axes as the central axis are integrally connected to each other, the second transmission member rotatably supported by the eccentric shaft portion, and the first and second transmission members A first transmission mechanism capable of transmitting torque is provided in the transmission case, and the first transmission mechanism is formed in a wavy annular shape formed around the first axis on the surface of the first transmission member facing the second transmission member. A first transmission groove and a second transmission groove formed around the second axis on the surface of the second transmission member facing the first transmission member, the second transmission groove having a wave shape and a wave number different from the first transmission groove; And interposed in a plurality of intersecting portions of the second transmission groove, respectively. In the transmission device including a plurality of first rolling elements involved in the transmission transmission between the first and second transmission members, an annular first holding member is interposed between the first and second transmission members, The first holding member holds the plurality of first rolling elements such that the plurality of first rolling elements can be kept engaged with both transmission grooves at the intersection of the first and second transmission grooves. A plurality of first holding holes are provided that are rotatably held while regulating their mutual spacing to be constant, and each of the first and second transmission grooves is provided on the inner peripheral side or the outer peripheral side of the first holding member. The first feature is that the portion is always open, and lubricating oil flow into the first and second transmission grooves is allowed through the opening.

　また本発明は、前記第１の特徴に加えて、第１軸線を中心軸線とするように配置されると共に第２伝動部材に対向する第３伝動部材と、第２及び第３伝動部材間で変速しつつトルク伝達可能な第２変速機構とを伝動ケース内に更に備えており、第２変速機構が、第２伝動部材の第３伝動部材との対向面に第２軸線を中心として形成される波形環状の第３伝動溝と、第３伝動部材の第２伝動部材との対向面に第１軸線を中心として形成される、波形環状で波数が第３伝動溝とは異なる第４伝動溝と、第３及び第４伝動溝の複数の交差部にそれぞれ介装されて、第３及び第４伝動溝を転動しながら第２及び第３伝動部材間の変速伝動を行う複数の第２転動体とで構成され、第２及び第３伝動部材間には環状の第２保持部材が介装され、この第２保持部材は、複数の第２転動体の、第３及び第４伝動溝相互の交差部での両伝動溝への係合状態を維持し得るように該複数の第２転動体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第２保持孔を有しており、第１～第４伝動溝がトロコイド曲線に沿った溝であると共に、第１及び第２伝動溝のトロコイド係数と第３及び第４伝動溝のトロコイド係数が互いに異なっており、第２保持部材の内周側又は外周側には第３及び第４伝動溝の各一部が常に開口していて、その開口部を通して第３及び第４伝動溝内への潤滑油流動が許容されることを第２の特徴とする。 Moreover, in addition to the said 1st characteristic, this invention is arrange | positioned so that a 1st axis line may be set as a center axis line, and between the 3rd transmission member which opposes a 2nd transmission member, and between a 2nd and 3rd transmission member The transmission case further includes a second transmission mechanism capable of transmitting torque while shifting, and the second transmission mechanism is formed on a surface of the second transmission member facing the third transmission member around the second axis. The fourth transmission groove formed on the opposed surface of the third transmission groove and the second transmission member of the third transmission member with the first axis as the center and having a wave shape and a wave number different from that of the third transmission groove And a plurality of second gears that are respectively interposed at a plurality of intersecting portions of the third and fourth transmission grooves and perform transmission transmission between the second and third transmission members while rolling the third and fourth transmission grooves. A second rolling member, and an annular second holding member is interposed between the second and third transmission members. The holding member holds the plurality of second rolling elements to each other so that the plurality of second rolling elements can be maintained in engagement with both transmission grooves at the intersection of the third and fourth transmission grooves. A plurality of second holding holes are provided that are rotatably held with a constant spacing, and the first to fourth transmission grooves are grooves along a trochoid curve, and the first and second transmission grooves The trochoid coefficient and the trochoid coefficient of the third and fourth transmission grooves are different from each other, and each part of the third and fourth transmission grooves is always open on the inner peripheral side or the outer peripheral side of the second holding member, A second feature is that lubricating oil flow into the third and fourth transmission grooves is allowed through the opening.

　また本発明は、前記第１又は第２の特徴に加えて、第１保持部材の内周側又は外周側に第１及び第２伝動溝の各一部が常に開口するように、第１保持部材並びに第１及び第２伝動溝の各形状と第１，第２軸線相互の偏心量とが設定されることを第３の特徴とする。 In addition to the first or second feature, the present invention provides the first holding so that each part of the first and second transmission grooves always opens on the inner peripheral side or the outer peripheral side of the first holding member. A third feature is that each shape of the member and the first and second transmission grooves and the amount of eccentricity between the first and second axes are set.

　また本発明は、前記第１又は第２の特徴に加えて、第１及び第２伝動溝の最大外径をそれぞれＤｇ１及びＤｇ２とし、同じく第１及び第２伝動溝の最小内径をそれぞれｄｇ１及びｄｇ２とし、また第１保持部材の最大外径及び最小内径をそれぞれＤｒ１及びｄｒ１とし、また第１，第２軸線相互の偏心量をｅとしたときに、次式
　（Ｄｒ１－ｅ）＜Ｄｇ１　　（Ｄｒ１－ｅ）＜Ｄｇ２
　（ｄｒ１＋ｅ）＞ｄｇ１　　（ｄｒ１＋ｅ）＞ｄｇ２
を満たすように、第１保持部材並びに第１及び第２伝動溝の各形状が設定されることを第４の特徴とする。 In addition to the first or the second feature, the present invention sets the maximum outer diameters of the first and second transmission grooves to Dg1 and Dg2, respectively, and similarly sets the minimum inner diameters of the first and second transmission grooves to dg1 and dg2, where the maximum outer diameter and the minimum inner diameter of the first holding member are Dr1 and dr1, respectively, and the eccentricity between the first and second axes is e, the following equation (Dr1-e) <Dg1 ( Dr1-e) <Dg2
(Dr1 + e)> dg1 (dr1 + e)> dg2
The fourth feature is that each shape of the first holding member and the first and second transmission grooves is set so as to satisfy the above.

　本発明の第１の特徴によれば、第１及び第２伝動部材間には環状の第１保持部材が介装され、この第１保持部材は、複数の第１転動体の、伝動溝相互の複数の交差部での第１及び第２伝動溝への係合状態を維持し得るように複数の第１転動体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第１保持孔を有しているので、個々の第１転動ボールは、第１、第２伝動溝の各々の曲率急変部を通過する際にも溝内での暴れが、第１保持部材により効果的に抑制可能となって、その曲率急変部においてもスムーズに転動、通過可能となる。 According to the first feature of the present invention, an annular first holding member is interposed between the first and second transmission members, and the first holding member is formed between the transmission grooves of the plurality of first rolling elements. The plurality of first rolling elements are rotatably held while their mutual intervals are kept constant so as to maintain the engaged state with the first and second transmission grooves at the plurality of intersections. Since each holding ball has one holding hole, even if each first rolling ball passes through each of the suddenly changing curvature portions of the first and second transmission grooves, the fluctuation in the groove is caused by the first holding member. It can be effectively suppressed, and can smoothly roll and pass even in the sudden curvature change portion.

　その上、第１保持部材の内周側又は外周側には第１及び第２伝動溝の各一部が常に開口していて、その開口部を通して第１及び第２伝動溝内への潤滑油流動が許容されるので、第１保持部材が各伝動溝に臨む配置であっても、伝動ケース内を流動又は飛散する潤滑油が上記開口部を通して第１及び第２伝動溝内へ流入可能となり、その流入潤滑油により溝内面や第１転動ボールを効果的に潤滑できる。 In addition, a part of each of the first and second transmission grooves is always open on the inner peripheral side or the outer peripheral side of the first holding member, and the lubricating oil flows into the first and second transmission grooves through the opening. Since the flow is allowed, even when the first holding member faces each transmission groove, the lubricating oil that flows or scatters in the transmission case can flow into the first and second transmission grooves through the opening. The inflow lubricating oil can effectively lubricate the groove inner surface and the first rolling ball.

　また特に第２の特徴によれば、第２及び第３伝動部材間に設けられる第２変速機構についても、前記第１の特徴による効果と同様の効果が得られる。この場合、第２保持部材の内周側又は外周側には第３及び第４伝動溝の各一部が常に開口していてその開口部を通して第３及び第４伝動溝内への潤滑油流動が許容されるので、第１及び第２伝動溝のトロコイド係数と第３及び第４伝動溝のトロコイド係数が互いに異なっても、第３及び第４伝動溝内への上記潤滑油の流入が可能となり、その流入潤滑油により溝内面や第２転動ボールを効果的に潤滑できる。 In particular, according to the second feature, the same effect as that of the first feature can be obtained for the second speed change mechanism provided between the second and third transmission members. In this case, each part of the third and fourth transmission grooves is always open on the inner peripheral side or the outer peripheral side of the second holding member, and the lubricating oil flows into the third and fourth transmission grooves through the opening. Therefore, even if the trochoid coefficients of the first and second transmission grooves and the trochoid coefficients of the third and fourth transmission grooves are different from each other, the lubricating oil can flow into the third and fourth transmission grooves. Therefore, the groove inner surface and the second rolling ball can be effectively lubricated by the inflow lubricant.

　また特に第３の特徴によれば、第１，第２軸線相互の偏心量を踏まえて、第１保持部材並びに第１及び第２伝動溝の各形状をそれぞれ設定するだけの簡単な構造で、上記潤滑効果が達成可能となり、潤滑手段を特別に設ける必要もないことからコスト節減に寄与することができる。 In particular, according to the third feature, with a simple structure in which each shape of the first holding member and the first and second transmission grooves is set based on the amount of eccentricity between the first and second axes, The above lubricating effect can be achieved, and it is not necessary to provide a special lubricating means, which can contribute to cost saving.

　また特に第４の特徴によれば、第１，第２軸線相互の偏心量を踏まえて、第１保持部材並びに第１及び第２伝動溝の各形状、特に各々の最大外径及び最小内径をそれぞれ設定するだけで、上記潤滑効果が達成可能となり、その設定を容易に行うことができる。 In particular, according to the fourth feature, the shapes of the first holding member and the first and second transmission grooves, particularly the maximum outer diameter and the minimum inner diameter, are determined based on the amount of eccentricity between the first and second axes. The lubrication effect can be achieved only by setting each, and the setting can be easily performed.

図１は本発明の一実施形態に係る差動装置の縦断正面図である。（第１の実施の形態）FIG. 1 is a longitudinal front view of a differential according to an embodiment of the present invention. (First embodiment) 図２は前記差動装置の要部（差動機構）の分解斜視図である。（第１の実施の形態）FIG. 2 is an exploded perspective view of a main part (differential mechanism) of the differential device. (First embodiment) 図３は前記差動装置の要部（差動機構）を潤滑油の流れと共に示す拡大縦断面図である。（第１の実施の形態）FIG. 3 is an enlarged longitudinal sectional view showing the main part (differential mechanism) of the differential device together with the flow of the lubricating oil. (First embodiment) 図４は図１の４－４矢視断面図（第１側壁板部Ｃａ等を軸方向内方から見た図）である。（第１の実施の形態）4 is a cross-sectional view taken along arrow 4-4 of FIG. 1 (a view of the first side wall plate portion Ca and the like viewed from the inside in the axial direction). (First embodiment) 図５は図１の５－５矢視断面図（第２伝動部材８等を第１側壁板部Ｃａ側から見た図）である。（第１の実施の形態）FIG. 5 is a cross-sectional view taken along the line 5-5 in FIG. 1 (the second transmission member 8 and the like viewed from the first side wall plate portion Ca side). (First embodiment) 図６は図１の６－６矢視断面図（第２伝動部材８等を第２側壁板部Ｃｂ側から見た図）である。（第１の実施の形態）6 is a cross-sectional view taken along line 6-6 in FIG. 1 (the second transmission member 8 and the like viewed from the second side wall plate portion Cb side). (First embodiment) 図７は図１の７－７矢視断面図（第２側壁板部Ｃｂ等を軸方向内方から見た図）である。（第１の実施の形態）FIG. 7 is a cross-sectional view taken along the line 7-7 in FIG. (First embodiment) 図８は図１の８－８矢視断面図である。（第１の実施の形態）8 is a cross-sectional view taken along the line 8-8 in FIG. (First embodiment)

Ｃ・・・・・伝動ケースとしてのデフケース
Ｄ・・・・・伝動装置としての差動装置
Ｄｇ１，Ｄｇ２・・第１，第２伝動溝の最大外径
Ｄｒ１，Ｄｒ２・・第１，第２保持部材の最大外径
ｄｇ１，ｄｇ２・・第１，第２伝動溝の最小内径
ｄｒ１，ｄｒ２・・第１，第２保持部材の最小内径
ＩＮ１～ＩＮ４・・開口部
Ｒ１，Ｒ２・・第１，第２保持部材
Ｔ１，Ｔ２・・第１，第２変速機構
Ｘ１，Ｘ２・・第１，第２軸線
５，８，９・・・第１，第２，第３伝動部材
６・・・・・偏心回転部材
６ｊ・・・・主軸部
６ｅ・・・・偏心軸部
２１，２２・・第１，第２伝動溝
２３・・・・・第１転動体としての第１転動ボール
２４，２５・・第３，第４伝動溝
２６・・・・・第２転動体としての第２転動ボール
３１，３２・・第１，第２保持孔 C... Differential case D as a transmission case... Differential gears Dg1, Dg2,..., Maximum outer diameters Dr1, Dr2,. Maximum outer diameters dg1, dg2 of the holding member, minimum inner diameters dr1, dr2 of the first and second transmission grooves, minimum inner diameters IN1 to IN4 of the first and second holding members, openings R1, R2,. , Second holding members T1, T2,..., First and second transmission mechanisms X1, X2,..., First and second axes 5, 8, 9. ..Eccentric rotating member 6j... Main shaft portion 6e... Eccentric shaft portions 21 and 22... First and second transmission grooves 23... First rolling ball 24 as first rolling element 25, 3rd, 4th transmission groove 26 ... 2nd rolling ball 31 as a 2nd rolling element, 32, ... 1st, 2nd holding hole

　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.

第１の実施の形態First embodiment

　先ず、図１～図８に示す本発明の一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, an embodiment of the present invention shown in FIGS. 1 to 8 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 is aligned on the central axis of the differential device D, that is, the first axis X1, are relatively rotatable. That is, with respect to the drive shaft), the drive shafts S1 and S2 are distributed while allowing differential rotation between them. 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側壁板部Ｃａ，Ｃｂとを備える。 The differential device D includes a differential case C that is supported by the mission case 1 so as to be rotatable about the first axis X1, and a differential mechanism 3 described later that is accommodated 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. Two side wall plate portions Ca and Cb are provided.

　その両側壁板部Ｃａ，Ｃｂは、各々の内周端部においてボス部Ｂを一体に有しており、そのボス部Ｂの外周部は、ミッションケース１に軸受２，２′を介して第１軸線Ｘ１回りに回転自在に支持される。またボス部Ｂの内周部には、第１軸線Ｘ１を回転軸線とする第１，第２駆動車軸Ｓ１，Ｓ２がそれぞれ回転自在に嵌合、支持される。尚、その嵌合面の少なくとも一方には、自動車の少なくとも前進時（即ち駆動車軸Ｓ１，Ｓ２の正転時）にボス部Ｂと各駆動車軸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内に積極的に誘導するための螺旋溝１８，１９が形成され、その各螺旋溝１８，１９の一端はミッションケース１内に、またその他端はデフケースＣ内にそれぞれ開口する。 The both side wall plate portions Ca and Cb integrally have a boss portion B at each inner peripheral end, and the outer peripheral portion of the boss portion B is connected to the transmission case 1 via bearings 2 and 2 '. It is supported so as to be rotatable about one axis X1. Further, first and second drive axles S1 and S2 having the first axis X1 as a rotation axis are rotatably fitted and supported on the inner peripheral portion of the boss portion B, respectively. It should be noted that at least one of the mating surfaces is provided in the transmission case 1 along with the relative rotation of the boss portion B and each of the drive axles S1 and S2 at least when the automobile is moving forward (ie, when the drive axles S1 and S2 are rotating forward). Spiral grooves 18 and 19 for positively guiding the scattered lubricating oil in the differential case C are formed. One end of each of the spiral grooves 18 and 19 is in the mission case 1 and the other end is in the differential case C. Open.

　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板部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。 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 alternatively), as another lubricating oil supply means, for example, lubricating oil pumped by pump means such as an oil pump is passed through an oil passage (not shown) provided in the drive axle S1, S2 or the differential case C. Then, it may be supplied into the differential case C. Alternatively, as still 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 plates Ca and Cb of the differential case C.

　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側壁板部Ｃａに一体的に設けられて第１軸線Ｘ１回りに回転自在な第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回りに回転自在な主軸部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を互いに一体に連結してなる偏心回転部材６と、第１伝動部材５に一側部が対向配置され且つ前記偏心軸部６ｅに軸受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回りに回転自在な円環状の第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 plate portion Ca and is spline-fitted 16 to the first drive axle S1 by the first transmission member 5 that is rotatable about the first axis X1. An eccentric rotation member 6 formed by integrally connecting a main shaft portion 6j rotatable around X1 and an eccentric shaft portion 6e having a second axis line X2 eccentric from the first axis line X1 by a predetermined eccentricity amount e as a central axis line; An annular second transmission member 8 having one side facing the first transmission member 5 and rotatably supported by the eccentric shaft portion 6e via a bearing 7, and the other side of the second transmission member 8 Between the first and second transmission members 5 and 8 and the annular third transmission member 9 which is disposed opposite to the first portion and is spline-fitted 17 to the second drive axle S2 and rotatable about the first axis X1. First transmission mechanism T1 capable of transmitting torque while shifting, and second and third transmission members 8 While shifting between 9 and a second transmission mechanism T2 possible torque transmission.

　而して、第１軸線Ｘ１回りに回転自在に支持される主軸部６ｊを有した偏心回転部材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、その第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 fitted to and supported by the eccentric shaft portion 6e of the eccentric rotating member 6 having the main shaft portion 6j rotatably supported about the first axis X1 so as to be rotatable about the second axis X2. As a result, the second transmission member 8 rotates around the first axis X1 of the eccentric rotation member 6 and rotates around the second axis X2 with respect to the eccentric shaft portion 6e, while rotating to the main shaft portion 6j. On the other hand, it can revolve 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円環状の第１半体８ａと、その第１半体８ａに後述するバランスウェイトＷの収容空間ＳＰを挟んで対向する円環状の第２半体８ｂと、その収容空間ＳＰを囲むようにして両半体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とを備えていて、第１半体８ａと第１伝動部材５との間に前記第１変速機構Ｔ１が、また第２半体８ｂと第３伝動部材９との間に前記第２変速機構Ｔ２がそれぞれ設けられる。 The second transmission member 8 includes an annular first half 8a that is rotatably supported by the eccentric shaft portion 6e of the eccentric rotating member 6 via a bearing 7, and a balance weight described later on the first half 8a. An annular second half 8b opposed across the accommodation space SP of W, and a basically cylindrical connecting member 8c integrally connecting the two halves 8a, 8b so as to surround the accommodation space SP. The first transmission mechanism T1 is provided between the first half body 8a and the first transmission member 5, and the second transmission mechanism T2 is provided between the second half body 8b and the third transmission member 9. Are provided respectively.

　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回りに回転自在な主軸部９ｊと、その主軸部９ｊの内端部に同軸状に連設される円板部９ｃとを結合一体化して構成される。尚、第２側壁板部Ｃｂの内側面と第３伝動部材９（円板部９ｃの背面）との間には、スラストワッシャ１５が相対回転自在に介装される。 The third transmission member 9 is spline-fitted 17 to the second drive axle S2 and is connected coaxially to the main shaft portion 9j rotatable around the first axis X1 and the inner end portion of the main shaft portion 9j. The disc portion 9c is combined and integrated. A thrust washer 15 is interposed between the inner side surface of the second side wall plate portion Cb and the third transmission member 9 (the back surface of the disc portion 9c) so as to be relatively rotatable.

　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、環状の取付基部Ｗｍと、その取付基部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。 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 attached to the main shaft portion 6j of the eccentric rotating member 6. This balance weight W is comprised from the cyclic | annular attachment base Wm and the weight part Ww fixedly provided in the circumferential direction specific area | region of the attachment base Wm.

　第２伝動部材８（連結部材８ｃ）の内部空間ＳＰは、前記したバランスウェイトＷを収容する収容空間ＳＰとして機能する。そして、偏心回転部材６の主軸部６ｊは、その内端部が前記収容空間ＳＰに延出しており、その延出端部６ｊａの外周にバランスウェイトＷが装着される。そして、前記取付基部Ｗｍは、主軸部６ｊの延出端部６ｊａ外周に嵌合されており、その嵌合面間には、その間の軸方向摺動は許容するが相対回転を規制する回り止め用の平坦な係合面１４が設けられる。バランスウェイトＷの主軸部６ｊへの固定は、前記取付基部Ｗｍの主軸部６ｊからの離脱を阻止する抜け止め部材としてのサークリップ等の止輪１０を主軸部６ｊの延出端部６ｊａに着脱可能に装着することで行われる。その装着のために、主軸部６ｊの延出端部６ｊａの外周には、止輪１０が弾力的に係止可能な係止溝が凹設される。 The internal space SP of the second transmission member 8 (the connecting member 8c) functions as an accommodation space SP that accommodates the balance weight W described above. The main shaft portion 6j of the eccentric rotating member 6 has an inner end portion extending into the accommodation space SP, and a balance weight W is attached to the outer periphery of the extended end portion 6ja. The mounting base portion Wm is fitted to the outer periphery of the extended end portion 6ja of the main shaft portion 6j, and the anti-rotation that allows axial sliding between the fitting surfaces but restricts relative rotation. A flat engagement surface 14 is provided. The balance weight W is fixed to the main shaft portion 6j by attaching or detaching a retaining ring 10 such as a circlip as a retaining member that prevents the attachment base portion Wm from being detached from the main shaft portion 6j to the extension end portion 6ja of the main shaft portion 6j. It is done by wearing it as possible. For the mounting, a locking groove that can elastically lock the retaining ring 10 is formed in the outer periphery of the extended end portion 6ja of the main shaft portion 6j.

　図１～図３に示すように、第１伝動部材５の、第２伝動部材８の一側面（即ち第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に対向する一側面（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 to 3, the inner surface of the first transmission member 5 facing the one side surface (that is, the first half 8a) of the second transmission member 8 has a waveform centered on the first axis X1. 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 surface (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Ｒ１が介装される。この第１保持部材Ｒ１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。これにより、各々の第１転動ボール２３は、第１、第２伝動溝２１，２２の各々の曲率急変部を通過する際にも溝内での暴れが効果的に抑制されるため、その曲率急変部でもスムーズに転動可能となり、伝動効率が高められる。 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 R1 is interposed. The first holding member R1 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. As a result, each first rolling ball 23 is effectively restrained from violating in the groove even when passing through each of the suddenly changing curvature portions of the first and second transmission grooves 21, 22. Smooth rolling is possible even in sudden curvature changing parts, increasing transmission efficiency.

　また、図１，２，４に示すように、第２伝動部材８の他側面（即ち第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円板部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 surface of the second transmission member 8 (that is, the second half 8 b). 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 side surface of the disc portion 9c, a corrugated annular fourth transmission groove 25 centering 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Ｒ２が介装される。この第２保持部材Ｒ２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。これにより、各々の第２転動ボール２６は、第３、第４伝動溝２４，２５の各々の曲率急変部を通過する際にも溝内での暴れが効果的に抑制されるため、その曲率急変部でもスムーズに転動可能となり、伝動効率が高められる。 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 R2 is interposed. The second holding member R2 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. As a result, each of the second rolling balls 26 is effectively restrained from violating in the grooves even when passing through the suddenly changing portions of the curvatures of the third and fourth transmission grooves 24, 25. Smooth rolling is possible even in sudden curvature changing parts, increasing transmission efficiency.

　ところで仮に、上記第１及び第２保持部材Ｒ１，Ｒ２が、これと対向する伝動溝２１，２２；２４，２５の開口面を全部覆う（即ち実質的に塞ぐ）形状・配置であれば、伝動溝２１，２２；２４，２５の内面や第１及び第２転動ボール２３，２６への潤滑油供給の妨げとなり、潤滑不足の事態を招く虞れがある。 By the way, if the first and second holding members R1, R2 have a shape / arrangement that covers (i.e., substantially closes) all the opening surfaces of the transmission grooves 21, 22; This may hinder the supply of lubricating oil to the inner surfaces of the grooves 21, 22; 24, 25 and the first and second rolling balls 23, 26, possibly resulting in insufficient lubrication.

　これに対して、本実施形態では、第１保持部材Ｒ１の内周側又は外周側に第１及び第２伝動溝２１，２２の各一部が常に開口していてその開口部ＩＮ１，ＩＮ２を通して第１及び第２伝動溝２１，２２内への潤滑油流動が許容されるように、第１，第２軸線Ｘ１，Ｘ２相互の偏心量ｅに配慮しながら、第１保持部材Ｒ１並びに第１及び第２伝動溝２１，２２の各形状が設定される。また上記と同様に、第２保持部材Ｒ２の内周側又は外周側にも第３及び第４伝動溝２４，２５の各一部が常に開口していてそれらの開口部ＩＮ３，ＩＮ４を通して第３及び第４伝動溝２４，２５内への潤滑油流動が許容されるように、前記偏心量ｅに配慮しながら、第２保持部材Ｒ２並びに第３及び第４伝動溝２４，２５の各形状が設定される。 On the other hand, in this embodiment, a part of each of the first and second transmission grooves 21 and 22 is always open on the inner peripheral side or the outer peripheral side of the first holding member R1, and through the openings IN1 and IN2. The first holding member R1 and the first holding member R1 and the first holding member R1 are arranged in consideration of the eccentricity e between the first and second axes X1 and X2 so that the lubricating oil flow into the first and second transmission grooves 21 and 22 is allowed. And each shape of the 2nd transmission grooves 21 and 22 is set up. Similarly to the above, a part of each of the third and fourth transmission grooves 24, 25 is always open on the inner peripheral side or the outer peripheral side of the second holding member R2, and the third through the openings IN3, IN4. In addition, the shapes of the second holding member R2 and the third and fourth transmission grooves 24 and 25 are determined in consideration of the eccentricity e so that the lubricating oil flow into the fourth transmission grooves 24 and 25 is allowed. Is set.

　上記形状設定に際しては、例えば第１及び第２保持部材Ｒ１，Ｒ２の、次のような運動形態が考慮される。即ち、差動装置Ｄによるトルク伝達時において、第１伝動部材５に第１変速機構Ｔ１を介して連動する第２伝動部材８が第１軸線Ｘ１回りに公転しつつ第２軸線Ｘ２回りに自転する過程では、第１及び第２伝動溝２１，２２の各交差部に存する複数の第１転動ボール２３を等間隔で保持する第１保持部材Ｒ１が、第２伝動部材８に同期して同一周期で第１軸線Ｘ１回りに公転しつつ、第１，第２軸線Ｘ１，Ｘ２の中間（即ち第１，第２軸線Ｘ１，Ｘ２を結ぶ仮想線の二等分点上）に位置する第３軸線Ｘｍ回りに自転するように運動する。同様に、第３及び第４伝動溝２４，２５の各交差部に存する複数の第２転動ボール２６を等間隔で保持する第２保持部材Ｒ２もまた、第２伝動部材８に同期して同一周期で第１軸線Ｘ１回りに公転しつつ、前記第３軸線Ｘｍ回りに自転するように運動する。 In the shape setting, for example, the following movement modes of the first and second holding members R1, R2 are considered. That is, at the time of torque transmission by the differential device D, the second transmission member 8 interlocked with the first transmission member 5 via the first transmission mechanism T1 revolves around the first axis X1 and rotates around the second axis X2. In the process, the first holding member R1 that holds the plurality of first rolling balls 23 existing at the intersections of the first and second transmission grooves 21 and 22 at equal intervals is synchronized with the second transmission member 8. A first revolved around the first axis X1 with the same period and located in the middle of the first and second axes X1 and X2 (ie, on the bisector of the imaginary line connecting the first and second axes X1 and X2). It moves to rotate around the 3 axis Xm. Similarly, the second holding member R <b> 2 that holds the plurality of second rolling balls 26 existing at the intersections of the third and fourth transmission grooves 24, 25 at equal intervals is also synchronized with the second transmission member 8. While revolving around the first axis X1 in the same cycle, it moves so as to rotate around the third axis Xm.

　従って、このような運動形態をとる第１保持部材Ｒ１の内周側又は外周側に第１及び第２伝動溝２１，２２の各一部を常に開口させるために、例えば本実施形態においては、第１保持部材Ｒ１の最大外径及び最小内径をそれぞれＤｒ１及びｄｒ１とし、第１伝動溝２１の最大外径及び最小内径をそれぞれＤｇ１及びｄｇ１とし、第２伝動溝２２の最大外径及び最小内径をそれぞれＤｇ２及びｄｇ２とし、また第１，第２軸線Ｘ１，Ｘ２相互の偏心量をｅとしたときに、
　第１保持部材Ｒ１並びに第１及び第２伝動溝２１，２２の各形状が次式
　　（Ｄｒ１－ｅ）＜Ｄｇ１  　（ｄｒ１＋ｅ）＞ｄｇ１  
　　（Ｄｒ１－ｅ）＜Ｄｇ２  　（ｄｒ１＋ｅ）＞ｄｇ２  
を満たすように設定される（図４，図５参照）。 Therefore, in order to always open each part of the first and second transmission grooves 21 and 22 on the inner peripheral side or the outer peripheral side of the first holding member R1 taking such a motion form, for example, in this embodiment, The maximum outer diameter and the minimum inner diameter of the first holding member R1 are respectively Dr1 and dr1, the maximum outer diameter and the minimum inner diameter of the first transmission groove 21 are respectively Dg1 and dg1, and the maximum outer diameter and the minimum inner diameter of the second transmission groove 22 are respectively. Is Dg2 and dg2, respectively, and when the eccentricity between the first and second axes X1 and X2 is e,
Each shape of the first holding member R1 and the first and second transmission grooves 21 and 22 has the following formula (Dr1-e) <Dg1 (dr1 + e)> dg1
(Dr1-e) <Dg2 (dr1 + e)> dg2
(See FIGS. 4 and 5).

　また同様の運動形態をとる第２保持部材Ｒ２の内周側又は外周側に第３及び第４伝動溝２４，２５の各一部を常に開口させるために、例えば本実施形態においては、第２保持部材Ｒ２の最大外径及び最小内径をそれぞれＤｒ２及びｄｒ２とし、第３伝動溝２４の最大外径及び最小内径をそれぞれＤｇ３及びｄｇ３とし、第４伝動溝２５の最大外径及び最小内径をそれぞれＤｇ４及びｄｇ４としたときに、
　第２保持部材Ｒ２並びに第３及び第４伝動溝２４，２５の各形状が次式
　　（Ｄｒ２－ｅ）＜Ｄｇ３  　（ｄｒ２＋ｅ）＞ｄｇ３  
　　（Ｄｒ２－ｅ）＜Ｄｇ４  　（ｄｒ２＋ｅ）＞ｄｇ４  
を満たすように設定される（図６，図７参照）。 Moreover, in order to always open each part of the 3rd and 4th transmission grooves 24 and 25 to the inner peripheral side or outer peripheral side of 2nd holding member R2 which takes the same motion form, for example in this embodiment, it is 2nd The maximum outer diameter and the minimum inner diameter of the holding member R2 are Dr2 and dr2, respectively, the maximum outer diameter and the minimum inner diameter of the third transmission groove 24 are Dg3 and dg3, respectively, and the maximum outer diameter and the minimum inner diameter of the fourth transmission groove 25 are respectively When Dg4 and dg4,
Each shape of the second holding member R2 and the third and fourth transmission grooves 24, 25 is expressed by the following formula (Dr2-e) <Dg3 (dr2 + e)> dg3
(Dr2-e) <Dg4 (dr2 + e)> dg4
(See FIGS. 6 and 7).

　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, 25 are formed so that the following formula 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.

　次に、前記実施形態の作用について説明する。 Next, the operation of the 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の円板部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 disk 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.

　上記した差動装置Ｄのトルク伝達過程においては、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内に広範囲に飛散する。そして、その飛散潤滑油の一部は、図３に示すようにデフケースＣのボス部Ｂと駆動車軸Ｓ１，Ｓ２との相対回転に伴い前記した螺旋溝１８，１９によりデフケースＣ内に積極的に供給され、そこから更に前記したスプライン嵌合部１６，１７を通して差動機構３の内部空間に（従って第２伝動部材８の内部空間ＳＰにも）導入される。そして、その導入潤滑油は、更に遠心力で径方向外方に流動して第１，第２変速機構Ｔ１，Ｔ２や軸受７に向かって流動する。 In the torque transmission process of the differential device D described above, the stored lubricating oil at the bottom of the transmission case 1 is stirred by the differential case C and the like and scattered in the transmission case 1 over a wide range as described above. As shown in FIG. 3, a part of the scattered lubricating oil is positively introduced into the differential case C by the spiral grooves 18 and 19 with the relative rotation between the boss portion B of the differential case C and the drive axles S1 and S2. From there, it is further introduced into the internal space of the differential mechanism 3 (and thus also into the internal space SP of the second transmission member 8) through the spline fitting portions 16 and 17 described above. The introduced lubricating oil further flows radially outward by centrifugal force and flows toward the first and second transmission mechanisms T1 and T2 and the bearing 7.

　また、一方（図３で右方）の螺旋溝１８からデフケースＣ内に供給された潤滑油の一部は、偏心回転部材６及び第１伝動部材５間の隙間と、軸受７とを経由しても差動機構３の内部空間に導入される。更に第２伝動部材８に形成した窓１１は、これがデフケースＣの内部空間に広く開口しているため、この窓１１を通しても、デフケースＣの内部空間と第２伝動部材８の内部空間ＳＰとの間で潤滑油がスムーズに流通、即ち出入り可能である。 A part of the lubricating oil supplied into the differential case C from the spiral groove 18 on one side (right side in FIG. 3) passes through the gap between the eccentric rotating member 6 and the first transmission member 5 and the bearing 7. However, it is introduced into the internal space of the differential mechanism 3. Further, since the window 11 formed in the second transmission member 8 is wide open in the internal space of the differential case C, the internal space of the differential case C and the internal space SP of the second transmission member 8 are also passed through the window 11. Between them, the lubricating oil can smoothly flow, that is, enter and exit.

　かくして、差動装置Ｄのトルク伝達過程では、デフケースＣの内部において、第１，第２変速機構Ｔ１，Ｔ２の周辺空間（例えば第１，第２保持部材Ｒ１，Ｒ２の外周側及び内周側の周辺空間）に、潤滑油が少なからず飛散し或いは流動する。 Thus, in the torque transmission process of the differential device D, in the differential case C, the peripheral spaces of the first and second transmission mechanisms T1, T2 (for example, the outer peripheral side and the inner peripheral side of the first and second holding members R1, R2) ), The lubricating oil scatters or flows not a little.

　ところで差動装置Ｄによるトルク伝達過程では、第２伝動部材８が前述の如く第１伝動部材５に連動して第１軸線Ｘ１回りに公転しつつ第２軸線Ｘ２回りに自転する。このとき、第１及び第２伝動溝２１，２２の各交差部に存する第１転動ボール２３を保持する第１保持部材Ｒ１と、第３及び第４伝動溝２４，２５の各交差部に存する第２転動ボール２６を保持する第２保持部材Ｒ２とは、何れも前述の如く第２伝動部材８に同期して第１軸線Ｘ１回りに公転しながら前記第３軸線Ｘｍ回りに自転する運動形態をとる。 Incidentally, in the torque transmission process by the differential device D, the second transmission member 8 rotates around the second axis X2 while revolving around the first axis X1 in conjunction with the first transmission member 5 as described above. At this time, the first holding member R1 holding the first rolling ball 23 existing at each intersection of the first and second transmission grooves 21, 22 and the intersection of the third and fourth transmission grooves 24, 25 are provided. The second holding member R2 that holds the existing second rolling ball 26 rotates around the third axis Xm while revolving around the first axis X1 in synchronism with the second transmission member 8 as described above. Takes exercise form.

　そして、本実施形態では、このような第１及び第２保持部材Ｒ１，Ｒ２の運動形態に配慮して、前述のように
　第１保持部材Ｒ１並びに第１及び第２伝動溝２１，２２の各形状が次式
　　（Ｄｒ１－ｅ）＜Ｄｇ１  　（ｄｒ１＋ｅ）＞ｄｇ１  
　　（Ｄｒ１－ｅ）＜Ｄｇ２  　（ｄｒ１＋ｅ）＞ｄｇ２  
を満たすように設定され、
　また第２保持部材Ｒ２並びに第３及び第４伝動溝２４，２５の各形状が次式
　　（Ｄｒ２－ｅ）＜Ｄｇ３  　（ｄｒ２＋ｅ）＞ｄｇ３  
　　（Ｄｒ２－ｅ）＜Ｄｇ４  　（ｄｒ２＋ｅ）＞ｄｇ４  
を満たすように設定される。 In the present embodiment, the first holding member R1 and the first and second transmission grooves 21 and 22 are each considered in consideration of the movement form of the first and second holding members R1 and R2 as described above. The shape is the following formula (Dr1-e) <Dg1 (dr1 + e)> dg1
(Dr1-e) <Dg2 (dr1 + e)> dg2
Set to meet
Each shape of the second holding member R2 and the third and fourth transmission grooves 24, 25 is expressed by the following formula (Dr2-e) <Dg3 (dr2 + e)> dg3
(Dr2-e) <Dg4 (dr2 + e)> dg4
It is set to satisfy.

　そして、特に第１保持部材Ｒ１並びに第１及び第２伝動溝２１，２２の上記設定形状によれば、第１保持部材Ｒ１の内周側又は外周側には第１及び第２伝動溝２１，２２の各一部を常に開口させることができるため、それらの開口部ＩＮ１，ＩＮ２を通して第１及び第２伝動溝２１，２２内への潤滑油流動が確保される。従って、デフケースＣ内の第１変速機構Ｔ１周辺を流動又は飛散する潤滑油が、上記開口部ＩＮ１，ＩＮ２から第１及び第２伝動溝２１，２２内へ流入可能となり、その流入潤滑油により溝内面や第１転動ボール２３を効果的に潤滑できる。しかも本実施形態では、前記偏心量ｅを踏まえて、第１保持部材Ｒ１並びに第１及び第２伝動溝２１，２２の各形状、特に各々の最大外径（即ちＤｒ１，Ｄｇ１，Ｄｇ２）及び最小内径（即ちｄｒ１，ｄｇ１，ｄｇ２）を設定するだけの簡単な構造で、上記した潤滑効果が確保可能となり、その設定作業も容易である。 In particular, according to the set shape of the first holding member R1 and the first and second transmission grooves 21, 22, the first and second transmission grooves 21, Since each part of 22 can always be opened, lubricating oil flow into the first and second transmission grooves 21 and 22 is ensured through the openings IN1 and IN2. Accordingly, the lubricating oil that flows or scatters around the first transmission mechanism T1 in the differential case C can flow into the first and second transmission grooves 21 and 22 from the openings IN1 and IN2, and the inflow lubricating oil allows the groove to flow. The inner surface and the first rolling ball 23 can be effectively lubricated. In addition, in the present embodiment, based on the amount of eccentricity e, each shape of the first holding member R1 and the first and second transmission grooves 21, 22, particularly the maximum outer diameter (ie, Dr1, Dg1, Dg2) and the minimum With a simple structure that only sets the inner diameter (that is, dr1, dg1, dg2), the above-described lubrication effect can be secured, and the setting operation is easy.

　また、第３及び第４伝動溝２４，２５のトロコイド係数は、第１及び第２伝動溝２１，２２のトロコイド係数とは異なっているが、第２保持部材Ｒ２並びに第３及び第４伝動溝２４，２５の上記設定形状によれば、第２保持部材Ｒ２の内周側又は外周側にも、第３及び第４伝動溝２４，２５の各一部を常に開口させることができるため、それらの開口部ＩＮ３，ＩＮ４を通して第３及び第４伝動溝２４，２５内への潤滑油流動が確保される。従って、デフケースＣ内の第２変速機構Ｔ２周辺を流動又は飛散する潤滑油が、上記開口部ＩＮ３，ＩＮ４から第３及び第４伝動溝２４，２５内へ流入可能となり、その流入潤滑油により溝内面や第２転動ボール２６を効果的に潤滑できる。 The trochoidal coefficients of the third and fourth transmission grooves 24 and 25 are different from the trochoidal coefficients of the first and second transmission grooves 21 and 22, but the second holding member R2 and the third and fourth transmission grooves. According to the set shapes of 24 and 25, the third and fourth transmission grooves 24 and 25 can always be partially opened on the inner peripheral side or the outer peripheral side of the second holding member R2. The lubricating oil flow into the third and fourth transmission grooves 24 and 25 through the openings IN3 and IN4 is ensured. Accordingly, the lubricating oil that flows or scatters around the second transmission mechanism T2 in the differential case C can flow into the third and fourth transmission grooves 24 and 25 from the openings IN3 and IN4, and the inflow lubricating oil allows the groove to flow. The inner surface and the second rolling ball 26 can be effectively lubricated.

　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。 The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

　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に入力された動力を、第２伝動部材８や第１，第２変速機構Ｔ１，Ｔ２を介して偏心回転部材６及び第３伝動部材９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。 For example, in the above-described embodiment, the differential device D is exemplified as the transmission device, and the power input from the power source to the differential case C is decentered via the second transmission member 8 and the first and second transmission mechanisms T1 and T2. Although the rotation member 6 and the third transmission member 9 are distributed while allowing differential rotation, the present invention can be applied to various transmission devices other than the differential device.

　また、前記実施形態のデフケースＣに相当するケーシングを固定のミッションケースとし、偏心回転部材６又は第３伝動部材９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。 Further, a casing corresponding to the differential case C of the above embodiment is a fixed mission case, and either one of the eccentric rotating member 6 or the third transmission member 9 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.

　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、種々の機械装置用の差動装置として実施可能である。 In the embodiment, the differential device D as a transmission device is accommodated in the transmission case M of the automobile. However, the differential device D is not limited to the differential apparatus for the automobile, It can be implemented as a differential for a mechanical device.

　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す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 / right wheel transmission system to distribute power while allowing differential rotation to the left and right drive axles S1, S2. Although shown in the present invention, the differential device as a transmission device is applied to the front / rear wheel transmission system in the front / rear wheel drive vehicle to allow power to be driven while allowing differential rotation with respect to the front and rear drive wheels. You may make it distribute.

　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、１枚の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。 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 the 1st on one surface of one member. The second transmission groove 22 may be provided, and the third transmission groove 24 may be provided on the other surface.

　また、前記実施形態では、第１，第２変速機構Ｔ１，Ｔ２として何れも転動ボール式の変速機構を用いたものを示したが、第２変速機構については、前記実施形態の構造に限定されない。即ち、偏心回転部材と、それの回転に連動して第２軸線回りの自転及び第１軸線回りの公転が可能な第２伝動部材とを少なくとも含む種々の変速機構、例えば内接式遊星歯車機構や、種々の構造のサイクロイド減速機（増速機）或いはトロコイド減速機（増速機）を第２変速機構に適用するようにしてもよい。 In the above-described embodiment, the first and second transmission mechanisms T1 and T2 are each configured using a rolling ball type transmission mechanism. However, the second transmission mechanism is limited to the structure of the above-described embodiment. Not. That is, various speed change mechanisms including at least an eccentric rotating member and a second transmission member capable of rotating around the second axis and revolving around the first axis in conjunction with the rotation thereof, such as an inscribed planetary gear mechanism Alternatively, a cycloid speed reducer (speed increaser) or a trochoid speed reducer (speed increaser) having various structures may be applied to the second speed change mechanism.

　また、前記実施形態では、バランスウェイトＷを第２伝動部材８の内部空間ＳＰに収容したものを示したが、バランスウェイトＷの配設部位は実施形態に限定されず、例えば、第２伝動部材８の外側等に配設してもよい。 In the above embodiment, the balance weight W is stored in the internal space SP of the second transmission member 8. However, the location of the balance weight W is not limited to the embodiment, and for example, the second transmission member. You may arrange | position on the outer side of 8 etc.

　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 may be a wave-shaped wave groove 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間に転動体として第１及び第２転動ボール２３，２６を介装したものを示したが、その転動体をローラ状又はピン状としてもよく、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。 Moreover, in the said embodiment, 1st and 2nd as a rolling element between the 1st and 2nd transmission grooves 21 and 22 of the 1st, 2nd transmission mechanisms T1 and T2, and the 3rd and 4th transmission grooves 24 and 25 are used. Although two rolling balls 23 and 26 are interposed, the rolling elements may be in the form of rollers or pins. In this case, the first and second transmission grooves 21 and 22, and the third and second The four transmission grooves 24 and 25 are formed in an inner surface shape such that a roller-shaped or pin-shaped rolling element can roll.

　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）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 fitting), and the differential case C is connected via the drive axles S1 and S2. In the present invention, the eccentric rotating 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Ｒ１，Ｒ２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 R1 and R2 are each constituted by an annular ring having inner and outer peripheral surfaces each having a perfect circle. However, the first and second holding members of the present invention are not limited thereto. 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.

Claims (4)

1. 　第１軸線（Ｘ１）を中心軸線とするように配置された第１伝動部材（５）と、
   　第１軸線（Ｘ１）回りに回転可能な主軸部（６ｊ）、および第１軸線（Ｘ１）から偏心した第２軸線（Ｘ２）を中心軸線とする偏心軸部（６ｅ）が互いに一体に連結された偏心回転部材（６）と、
   　偏心軸部（６ｅ）に回転自在に支持される第２伝動部材（８）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）とを伝動ケース（Ｃ）内に備えており、
   　第１変速機構（Ｔ１）が、第１伝動部材（５）の第２伝動部材（８）との対向面に第１軸線（Ｘ１）を中心として形成される波形環状の第１伝動溝（２１）と、第２伝動部材（８）の第１伝動部材（５）との対向面に第２軸線（Ｘ２）を中心として形成される、波形環状で波数が第１伝動溝（２１）とは異なる第２伝動溝（２２）と、第１及び第２伝動溝（２１，２２）の複数の交差部にそれぞれ介装されて、第１及び第２伝動溝（２１，２２）を転動しながら第１及び第２伝動部材（５，８）間の変速伝動に関与する複数の第１転動体（２３）とを含む伝動装置において、
   　第１及び第２伝動部材（５，８）間には環状の第１保持部材（Ｒ１）が介装され、
   　この第１保持部材（Ｒ１）は、複数の第１転動体（２３）の、第１及び第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該複数の第１転動体（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第１保持孔（３１）を有しており、
   　第１保持部材（Ｒ１）の内周側又は外周側には第１及び第２伝動溝（２１，２２）の各一部が常に開口していて、その開口部（ＩＮ１，ＩＮ２）を通して第１及び第２伝動溝（２１，２２）内への潤滑油流動が許容されることを特徴とする伝動装置。 A first transmission member (5) disposed so as to have the first axis (X1) as a central axis;
   A main shaft portion (6j) rotatable around the first axis (X1) and an eccentric shaft portion (6e) having a second axis (X2) eccentric from the first axis (X1) as a central axis are integrally connected to each other. An eccentric rotating member (6),
   A second transmission member (8) rotatably supported by the eccentric shaft portion (6e);
   The transmission case (C) includes a first transmission mechanism (T1) capable of transmitting torque while shifting between the first and second transmission members (5, 8),
   The first transmission mechanism (T1) is a corrugated annular first transmission groove (21) formed around the first axis (X1) on the surface of the first transmission member (5) facing the second transmission member (8). ) And the first transmission member (8) of the second transmission member (8) and the first transmission member (5). The first and second transmission grooves (21, 22) roll on the different second transmission grooves (22) and a plurality of intersections of the first and second transmission grooves (21, 22), respectively. However, in the transmission including the plurality of first rolling elements (23) involved in the transmission transmission between the first and second transmission members (5, 8),
   An annular first holding member (R1) is interposed between the first and second transmission members (5, 8),
   This first holding member (R1) is engaged with both transmission grooves (21, 22) at the intersection of the first and second transmission grooves (21, 22) of the plurality of first rolling elements (23). A plurality of first holding holes (31) for holding the plurality of first rolling elements (23) so as to be able to rotate freely while maintaining their mutual spacing constant so as to maintain a combined state;
   A part of each of the first and second transmission grooves (21, 22) is always open on the inner peripheral side or outer peripheral side of the first holding member (R1), and the first through the openings (IN1, IN2). And a lubricating oil flow into the second transmission groove (21, 22) is allowed.
2. 　第１軸線（Ｘ１）を中心軸線とするように配置されると共に第２伝動部材（８）に対向する第３伝動部材（９）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）とを伝動ケース（Ｃ）内に更に備えており、
   　第２変速機構（Ｔ２）が、第２伝動部材（８）の第３伝動部材（９）との対向面に第２軸線（Ｘ２）を中心として形成される波形環状の第３伝動溝（２４）と、第３伝動部材（９）の第２伝動部材（８）との対向面に第１軸線（Ｘ１）を中心として形成される、波形環状で波数が第３伝動溝（２４）とは異なる第４伝動溝（２５）と、第３及び第４伝動溝（２４，２５）の複数の交差部にそれぞれ介装されて、第３及び第４伝動溝（２４，２５）を転動しながら第２及び第３伝動部材（８，９）間の変速伝動を行う複数の第２転動体（２６）とで構成され、
   　第２及び第３伝動部材（８，９）間には環状の第２保持部材（Ｒ２）が介装され、
   　この第２保持部材（Ｒ２）は、複数の第２転動体（２６）の、第３及び第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該複数の第２転動体（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第２保持孔（３２）を有しており、
   　第１～第４伝動溝（２１，２２，２４，２５）がトロコイド曲線に沿った溝であると共に、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）のトロコイド係数が互いに異なっており、
   　第２保持部材（Ｒ２）の内周側又は外周側には第３及び第４伝動溝（２４，２５）の各一部が常に開口していて、その開口部（ＩＮ３，ＩＮ４）を通して第３及び第４伝動溝（２４，２５）内への潤滑油流動が許容されることを特徴とする、請求項１に記載の伝動装置。 Between the 3rd transmission member (9) which is arranged so that the 1st axis (X1) may become a central axis, and is opposed to the 2nd transmission member (8), and the 2nd and 3rd transmission members (8, 9) The transmission case (C) further includes a second transmission mechanism (T2) capable of transmitting torque while shifting,
   The second transmission mechanism (T2) has a wave-shaped annular third transmission groove (24) formed around the second axis (X2) on the surface of the second transmission member (8) facing the third transmission member (9). ) And the second transmission member (8) of the third transmission member (9), and the third transmission groove (24) having a wave shape and a wave number formed around the first axis (X1) as a center. Rolled through the third and fourth transmission grooves (24, 25), respectively, are interposed at different intersections of the fourth transmission groove (25) and the third and fourth transmission grooves (24, 25). However, it is composed of a plurality of second rolling elements (26) that perform transmission transmission between the second and third transmission members (8, 9),
   An annular second holding member (R2) is interposed between the second and third transmission members (8, 9),
   The second holding member (R2) is engaged with both transmission grooves (24, 25) at the intersections of the third and fourth transmission grooves (24, 25) of the plurality of second rolling elements (26). A plurality of second holding holes (32) for holding the plurality of second rolling elements (26) in a freely rotating manner while maintaining their mutual spacing constant so as to maintain a combined state;
   The first to fourth transmission grooves (21, 22, 24, 25) are grooves along the trochoid curve, and the trochoid coefficient of the first and second transmission grooves (21, 22) and the third and fourth transmission grooves. (24,25) have different trochoidal coefficients,
   A part of each of the third and fourth transmission grooves (24, 25) is always open on the inner peripheral side or outer peripheral side of the second holding member (R2), and the third through the openings (IN3, IN4). The transmission device according to claim 1, characterized in that lubricating oil flow into the fourth transmission groove (24, 25) is allowed.
3. 　第１保持部材（Ｒ１）の内周側又は外周側に第１及び第２伝動溝（２１，２２）の各一部が常に開口するように、第１保持部材（Ｒ１）並びに第１及び第２伝動溝（２１，２２）の各形状と第１，第２軸線（Ｘ１，Ｘ２）相互の偏心量（ｅ）とが設定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 first holding member (R1) and the first and second first and second transmission grooves (21, 22) are always opened on the inner peripheral side or the outer peripheral side of the first holding member (R1). The transmission according to claim 1 or 2, wherein each shape of the two transmission grooves (21, 22) and the amount of eccentricity (e) between the first and second axes (X1, X2) are set. apparatus.
4. 　第１及び第２伝動溝（２１，２２）の最大外径をそれぞれＤｇ１及びＤｇ２とし、同じく第１及び第２伝動溝（２１，２２）の最小内径をそれぞれｄｇ１及びｄｇ２とし、また第１保持部材（Ｒ１）の最大外径及び最小内径をそれぞれＤｒ１及びｄｒ１とし、また第１，第２軸線（Ｘ１，Ｘ２）相互の偏心量をｅとしたときに、次式
   　　（Ｄｒ１－ｅ）＜Ｄｇ１　　（Ｄｒ１－ｅ）＜Ｄｇ２
   　　（ｄｒ１＋ｅ）＞ｄｇ１　　（ｄｒ１＋ｅ）＞ｄｇ２
   を満たすように、第１保持部材（Ｒ１）並びに第１及び第２伝動溝（２１，２２）の各形状が設定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 maximum outer diameters of the first and second transmission grooves (21, 22) are Dg1 and Dg2, respectively. Similarly, the minimum inner diameters of the first and second transmission grooves (21, 22) are dg1 and dg2, respectively. When the maximum outer diameter and the minimum inner diameter of the member (R1) are Dr1 and dr1, respectively, and the eccentricity between the first and second axes (X1, X2) is e, the following formula (Dr1-e) <Dg1 (Dr1-e) <Dg2
   (Dr1 + e)> dg1 (dr1 + e)> dg2
   The transmission device according to claim 1 or 2, wherein each shape of the first holding member (R1) and the first and second transmission grooves (21, 22) is set so as to satisfy the above.

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