WO2017146003A1 - Differential gear - Google Patents

Abstract

A differential gear according to the present invention is provided with: a first transmission member that has a first axis line as a central axis line; an eccentric rotation member in which a hollow first output boss that can be rotated about the first axis line and an eccentric shaft part that has, as a central axis line, a second axis line that is eccentric from the first axis line are integrally coupled; a second transmission member that is opposed to the first transmission member and that is rotatably supported by the eccentric shaft part; a third transmission member that has a hollow second output boss that can be rotated about the first axis line and that is opposed to the second transmission member; a first transmission mechanism between the first and second transmission members; and a second transmission mechanism between the second and third transmission members. A spiral groove (19) that can draw lubricant oil in a transmission case (1) thereinto is provided on one of fitting surfaces between a hub (HB2) of a differential case (C) and a second drive shaft (S2) that is fittingly supported by the hub. Oil holes (47) that allow the outlet of the spiral groove to communicate with the inner circumferential side of the second transmission mechanism (T2) are provided in the third transmission member (9). Accordingly, the second transmission mechanism is efficiently lubricated while taking advantage of this device.

Description

差動装置Differential

　本発明は、デフケースに入力された回転力をデフケース内の差動機構を介して第１，第２ドライブ軸に分配して伝達可能な差動装置に関する。 The present invention relates to a differential device capable of distributing and transmitting a rotational force input to a differential case to first and second drive shafts via a differential mechanism in the differential case.

　上記差動装置として、例えば特許文献１に示すように、デフケースに支持したベベルギヤよりなる差動ギヤに、これをデフケースの軸方向両側から挟む一対のサイドギヤを噛合させるようにした差動機構を用いるものが従来一般的であるが、この構造では、差動機構、従ってデフケースが軸方向に大型化する問題がある。 As the differential device, for example, as shown in Patent Document 1, a differential mechanism is used in which a differential gear made of a bevel gear supported by a differential case is engaged with a pair of side gears sandwiched from both sides in the axial direction of the differential case. In this structure, there is a problem that the differential mechanism, and hence the differential case, increases in size in the axial direction.

　また、例えば特許文献２に示される伝動装置のように、第１軸線を中心軸線とする第１伝動部材と、第１軸に接続されて第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一体に連結された偏心回転部材と、第１伝動部材に対向配置されて偏心軸部に回転自在に支持される第２伝動部材と、その第２伝動部材に対向配置されると共に第２軸に接続されて第１軸線回りに回転可能な第３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、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変速機構とを備え、第１，第２軸の一方から他方へ減速駆動可能とした構造の減速装置が知られている。そして、この特許文献２のものは、第１，第３伝動部材と第２伝動部材との各間を、ケースの軸方向にコンパクトな第１，第２変速機構（例えばボールとこれが転動する一対の環状波形の伝動溝とを各々有する転動ボール式変速機構）で連動させることで、ケースを軸方向に容易に扁平小型化し得る利点がある。 Further, for example, as in the transmission device disclosed in Patent Document 2, a first transmission member having a first axis as a central axis, a main shaft connected to the first shaft and rotatable about the first axis, and a first An eccentric rotation member integrally connected with an eccentric shaft portion having a second axis line eccentric from the axis as a central axis, and a second transmission member disposed opposite to the first transmission member and rotatably supported by the eccentric shaft portion; A third transmission member disposed opposite to the second transmission member and connected to the second shaft and capable of rotating about the first axis, and a second gear capable of transmitting torque while shifting between the first and second transmission members. There is provided a reduction gear having a structure in which a first transmission mechanism and a second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members are configured to be decelerated from one of the first and second shafts to the other. Are known. And this thing of this patent document 2 is compact between the 1st, 3rd transmission member, and the 2nd transmission member in the axial direction of a case with the 1st, 2nd speed change mechanism (for example, a ball and this roll). There is an advantage that the case can be easily made flat and small in the axial direction by interlocking with a rolling ball type transmission mechanism having a pair of annular corrugated transmission grooves.

日本特開２０１２－６７８８９号公報Japanese Unexamined Patent Publication No. 2012-67889 日本特許第４８１４３５１号明細書Japanese Patent No. 4814351

　特許文献１の伝動装置は、差動装置ではあるものの、上述のようにデフケースを軸方向に扁平小型化することが元々難しい構造である。 Although the transmission device of Patent Document 1 is a differential device, it is originally difficult to downsize the differential case in the axial direction as described above.

　一方、特許文献２の伝動装置は、ケース軸方向に容易に扁平小型化し得る構造ではあるものの、この構造を差動装置として利用可能とするための技術思想（例えば第１，第２変速機構の各変速比を特定比率に設定するような技術思想）はなく、そのため、例えばケースに回転力を入力しても、その回転力を第１，第２軸に分配できない。またこの特許文献２の伝動装置では、扁平小型化されたケースの狭隘な内部空間に存する変速機構（例えば第２変速機構）に潤滑油を効率よく供給する技術手段が設けられていない。 On the other hand, although the transmission device of Patent Document 2 has a structure that can be easily flattened in the case axial direction, a technical idea for making this structure usable as a differential device (for example, the first and second transmission mechanisms). There is no technical idea of setting each gear ratio to a specific ratio. Therefore, for example, even if a rotational force is input to the case, the rotational force cannot be distributed to the first and second shafts. Further, in the transmission device of Patent Document 2, there is no technical means for efficiently supplying the lubricating oil to the speed change mechanism (for example, the second speed change mechanism) existing in the narrow inner space of the flat and small case.

　本発明は、かかる事情に鑑みてなされたものであって、特許文献２のような伝動装置の上記利点を生かしつつ、これを差動装置として有効活用できるようにし、更にデフケースの狭隘の内部空間に存する第２変速機構に潤滑油を効率よく供給可能とした差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 makes it possible to effectively utilize this as a differential device while taking advantage of the above-described advantage of the transmission device as disclosed in Patent Document 2, and further, a narrow internal space of the differential case. An object of the present invention is to provide a differential gear that can efficiently supply lubricating oil to the second transmission mechanism existing in the above.

　上記目的を達成するために、本発明は、ミッションケース内に配置され、回転力を受けて第１軸線回りに回転するデフケースと、このデフケースと共に第１軸線回りに回転可能な第１伝動部材と、第１ドライブ軸に接続されて第１軸線回りに回転可能な第１出力ボス、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一体に連結された偏心回転部材と、前記第１伝動部材に対向配置されて前記偏心軸部に回転自在に支持される第２伝動部材と、前記第２伝動部材に対向配置され第１軸線回りに回転可能な第３伝動部材と、前記第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、前記第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変速機構とを備え、前記第１，第２変速機構が、前記偏心回転部材を固定したときに前記第１伝動部材から前記第３伝動部材を２倍の増速比を以て駆動するように構成されてなる差動装置であって、前記第３伝動部材には、前記デフケースに設けたハブに回転自在に嵌合支持される第２ドライブ軸が連結され、前記ハブと前記第２ドライブ軸との嵌合面の一方には、それらハブと第２ドライブ軸との相対回転により前記ミッションケース内の潤滑油を該ハブの外端側から内端側に引き込み可能な螺旋溝が設けられると共に、この螺旋溝の出口を前記第２変速機構の内周側に連通させる油孔が前記第３伝動部材に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 differential case that is arranged in a mission case and receives a rotational force and rotates around a first axis, and a first transmission member that can rotate around the first axis together with the differential case. A first output boss connected to the first drive shaft and rotatable about the first axis, and an eccentric rotating member integrally coupled with an eccentric shaft portion having a second axis that is eccentric from the first axis as a central axis; A second transmission member disposed opposite to the first transmission member and rotatably supported by the eccentric shaft portion; a third transmission member disposed opposite to the second transmission member and rotatable about the first axis; A first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members, and a second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members, The first and second speed change mechanisms are A differential device configured to drive the third transmission member from the first transmission member with a double speed increasing ratio when the rolling member is fixed, and the third transmission member includes: A second drive shaft that is rotatably fitted and supported is connected to a hub provided in the differential case, and one of the fitting surfaces of the hub and the second drive shaft has a relative relationship between the hub and the second drive shaft. A spiral groove capable of drawing the lubricating oil in the transmission case by rotation from the outer end side to the inner end side of the hub is provided, and oil that allows the outlet of the spiral groove to communicate with the inner peripheral side of the second transmission mechanism A first feature is that a hole is provided in the third transmission member.

　また本発明は、ミッションケース内に配置され、回転力を受けて第１軸線回りに回転するデフケースと、このデフケースと共に第１軸線回りに回転可能な第１伝動部材と、第１ドライブ軸に接続されて第１軸線回りに回転可能な第１出力ボス、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一体に連結された偏心回転部材と、前記第１伝動部材に対向配置されて前記偏心軸部に回転自在に支持される第２伝動部材と、前記第２伝動部材に対向配置され第１軸線回りに回転可能な第３伝動部材と、前記第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、前記第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変速機構とを備え、前記第１，第２変速機構が、前記偏心回転部材を固定したときに前記第１伝動部材から前記第３伝動部材を２倍の増速比を以て駆動するように構成されてなる差動装置であって、前記第３伝動部材には、前記デフケースに設けたハブに回転自在に嵌合支持される筒軸が一体的に連設されると共に、その筒軸を通して該第３伝動部材が第２ドライブ軸に連結され、前記ハブと前記筒軸との嵌合面の一方には、それらハブと筒軸との相対回転により前記ミッションケース内の潤滑油を該ハブの外端側から内端側に引き込み可能な螺旋溝が設けられると共に、この螺旋溝の出口を前記第２変速機構の内周側に連通させる油孔が前記第３伝動部材に設けられることを第２の特徴とする。 Further, the present invention is connected to the first drive shaft, a differential case that is disposed in the transmission case and rotates around the first axis upon receiving a rotational force, a first transmission member that can rotate around the first axis together with the differential case, and A first output boss that is rotatable about the first axis, and an eccentric rotating member in which an eccentric shaft portion having a second axis that is eccentric from the first axis as a central axis is integrally connected; and the first transmission member A second transmission member disposed oppositely and rotatably supported by the eccentric shaft portion; a third transmission member disposed opposite to the second transmission member and rotatable about a first axis; and the first and second transmission members. A first transmission mechanism capable of transmitting torque while shifting between transmission members; and a second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members, the first and second transmission mechanisms. When the eccentric rotating member is fixed A differential device configured to drive the third transmission member from the first transmission member with a double speed increasing ratio, wherein the third transmission member is rotated by a hub provided in the differential case. A cylindrical shaft that is freely fitted and supported is integrally connected, and the third transmission member is connected to the second drive shaft through the cylindrical shaft, and one of the fitting surfaces of the hub and the cylindrical shaft is connected. Is provided with a spiral groove capable of drawing the lubricating oil in the transmission case from the outer end side to the inner end side of the hub by relative rotation between the hub and the cylindrical shaft, and the outlet of the spiral groove is connected to the first groove. A second feature is that an oil hole communicating with the inner peripheral side of the two speed change mechanism is provided in the third transmission member.

　また本発明は、第１又は第２の特徴に加えて、前記第３伝動部材の外側面と前記デフケースの内側面との相対向面間には、その間の相対回転を許容するスラストワッシャが介装され、前記螺旋溝の出口と前記油孔との間には、その間を連通させ且つ前記スラストワッシャの内周端を臨ませる油室が設けられることを第３の特徴とする。 Further, according to the present invention, in addition to the first or second feature, a thrust washer that allows relative rotation between the outer surface of the third transmission member and the inner surface of the differential case is interposed. A third feature is that an oil chamber is provided between the outlet of the spiral groove and the oil hole so as to communicate therewith and to face the inner peripheral end of the thrust washer.

　また本発明は、第１～第３の何れかの特徴に加えて、前記第１変速機構は、第１伝動部材の、第２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伝動溝と、第２伝動部材の、第１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各々介装され、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転動体とを有し、前記第２変速機構は、第２伝動部材の、第３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在り且つ第１軸線を中心とす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介装され、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転動体とを有し、前記第１伝動溝の波数をＺ１、第２伝動溝の波数をＺ２、第３伝動溝の波数をＺ３、第４伝動溝の波数をＺ４としたとき、次式　（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
が成立することを第４の特徴とする。 According to the present invention, in addition to any one of the first to third features, the first speed change mechanism is located on a surface of the first transmission member facing the second transmission member and is centered on the first axis. A first transmission groove having a wave shape and a second transmission groove having a wave number different from that of the first transmission groove in a wave shape centered on the second axis and located on a surface of the second transmission member facing the first transmission member. The first and second transmission grooves are respectively interposed at a plurality of intersecting portions, and the first and second transmission grooves are rolled and the first and second transmission members are involved in the transmission of the first and second transmissions. The second transmission mechanism is located on a surface of the second transmission member facing the third transmission member and has a corrugated annular third transmission groove centered on the second axis; and a third transmission member A fourth transmission groove on the surface facing the second transmission member and having a wave shape centered on the first axis and having a wave number different from that of the third transmission groove; A plurality of second rolling elements interposed at a plurality of intersections of the transmission grooves and performing transmission transmission between the second and third transmission members while rolling the third and fourth transmission grooves, When the wave number of one transmission groove is Z1, the wave number of the second transmission groove is Z2, the wave number of the third transmission groove is Z3, and the wave number of the fourth transmission groove is Z4, the following equation (Z1 / Z2) × (Z3 / Z4 ) = 2
The fourth characteristic is that is established.

　また本発明は、第２の特徴に加えて、前記第３伝動部材に設けられて該第３伝動部材を前記第２ドライブ軸に連結する連結孔の、第２ドライブ軸と反対側の端部が閉塞され、前記筒軸と前記ミッションケースとの間にシール部材が介装されることを第５の特徴とする。 According to the present invention, in addition to the second feature, an end portion on the opposite side of the second drive shaft of a connection hole provided in the third transmission member to connect the third transmission member to the second drive shaft Is closed, and a seal member is interposed between the cylindrical shaft and the transmission case.

　本発明の第１の特徴によれば、ミッションケース内に配置されて回転力を受けるデフケースと共に第１軸線回りに回転可能な第１伝動部材と、第１軸線回りに回転可能な第１出力ボス、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一体に連結された偏心回転部材と、第１伝動部材に対向配置されて偏心軸部に回転自在に支持される第２伝動部材と、第２伝動部材に対向配置されて第１軸線回りに回転可能な第３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、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変速機構とを備え、第１，第２変速機構が、偏心回転部材を固定したときに第１伝動部材から第３伝動部材を２倍の増速比を以て駆動するように構成されるので、軸方向に容易に扁平小型化し得る差動装置を提供することができる。その上、デフケースのハブと第２ドライブ軸との嵌合面の一方には、その相互の相対回転によりミッションケース内の潤滑油をハブの外端側から内端側に引き込み可能な螺旋溝が設けられると共に、この螺旋溝の出口を第２変速機構の内周側に連通させる油孔が第３伝動部材に設けられるので、螺旋溝を通してミッションケース側からデフケース側へ潤滑油を引き込み、次いでその潤滑油を第３伝動部材の油孔を通して第２変速機構の内周側に流入させ、そこから遠心力の作用で径方向外方に飛散させて第２変速機構に効率よく供給可能となり、その第２変速機構を効果的に潤滑することができる。 According to the first aspect of the present invention, the first transmission member that is rotatable about the first axis together with the differential case that is arranged in the transmission case and receives rotational force, and the first output boss that is rotatable about the first axis. , And an eccentric rotating member integrally connected to an eccentric shaft portion having a second axis line eccentric from the first axis as a central axis, and a first rotating member disposed so as to face the first transmission member and rotatably supported by the eccentric shaft portion. 2 transmission members, a third transmission member that is disposed opposite to the second transmission member and can rotate about the first axis, and a first transmission mechanism that can transmit torque while shifting between the first and second transmission members, And a second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members. When the first and second transmission mechanisms fix the eccentric rotation member, the first transmission member to the third transmission member. Is configured to be driven with a double speed increase ratio. It is possible to provide a differential device capable of easily flattened compact in the axial direction. In addition, on one of the mating surfaces of the differential case hub and the second drive shaft, there is a spiral groove that can draw the lubricating oil in the transmission case from the outer end side to the inner end side of the hub by the relative rotation of each other. And the third transmission member is provided with an oil hole that communicates the outlet of the spiral groove with the inner peripheral side of the second transmission mechanism, so that the lubricating oil is drawn from the transmission case side to the differential case side through the spiral groove. Lubricating oil is allowed to flow into the inner peripheral side of the second transmission mechanism through the oil hole of the third transmission member, and can be efficiently supplied to the second transmission mechanism by being scattered radially outward by the action of centrifugal force. The second speed change mechanism can be effectively lubricated.

　また特に第２の特徴によれば、第１の特徴による前記した効果と同等の効果を達成可能である。 In particular, according to the second feature, it is possible to achieve an effect equivalent to the above-described effect of the first feature.

　また特に第３の特徴によれば、第３伝動部材の外側面とデフケースの内側面との相対向面間にはスラストワッシャが介装されるので、スラストワッシャの厚みを調整することで、第１及び第３伝動部材間の軸方向の遊びを排除して第１，第２変速機構の良好な伝動機能を確保すると共に、第３伝動部材とデフケースとの対向面相互の円滑な摺動も確保することができる。しかも螺旋溝の出口と油孔との間には、その間を連通させ且つスラストワッシャの内周端を臨ませる油室が設けられるので、螺旋溝を通してミッションケース側からデフケース側へ引き込まれた潤滑油は、先ず油室に流入し、そこから上記油孔側とスラストワッシャ側とに分流するため、前述のように第２変速機構を効果的に潤滑できると同時に、スラストワッシャと第３伝動部材及びデフケースとの各間の摺動面を効果的に潤滑できる。 In particular, according to the third feature, since the thrust washer is interposed between the opposing surfaces of the outer surface of the third transmission member and the inner surface of the differential case, the thickness of the thrust washer can be adjusted by adjusting the thickness of the thrust washer. The axial play between the first and third transmission members is eliminated to ensure a good transmission function of the first and second transmission mechanisms, and smooth sliding between the opposing surfaces of the third transmission member and the differential case is also possible. Can be secured. Moreover, an oil chamber is provided between the spiral groove outlet and the oil hole so as to communicate between them and to face the inner peripheral end of the thrust washer, so that the lubricating oil drawn from the mission case side to the differential case side through the spiral groove First flows into the oil chamber and then splits into the oil hole side and the thrust washer side, so that the second transmission mechanism can be effectively lubricated as described above, and at the same time, the thrust washer, the third transmission member, The sliding surface between each of the differential cases can be effectively lubricated.

　また特に第４の特徴によれば、各々複数ある第１，第２転動体が全て同時に伝動に関与可能となるので、伝達トルクが転動体両側の各伝動部材の周方向に分散することになり、軽量且つ耐久性の高い差動装置を提供可能となる。 In particular, according to the fourth feature, the plurality of first and second rolling elements can be involved in the transmission at the same time, so that the transmission torque is distributed in the circumferential direction of the transmission members on both sides of the rolling element. Thus, it is possible to provide a differential device that is lightweight and highly durable.

　また第５の特徴によれば、第３伝動部材に設けられて第３伝動部材を第２ドライブ軸に連結する連結孔の、第２ドライブ軸と反対側の端部が閉塞され、第３伝動部材に一体的に連結されてデフケースのハブに回転自在に嵌合支持される筒軸と、ミッションケースとの間にシール部材が介装されるので、第２ドライブ軸を筒軸から引き抜いた場合でも、ミッションケース及びデフケース内の潤滑油の外部漏出を防止でき、メンテナンス作業性が良好となる。 According to the fifth feature, the end of the connecting hole provided in the third transmission member for connecting the third transmission member to the second drive shaft is closed on the side opposite to the second drive shaft, so that the third transmission When the second drive shaft is pulled out from the cylinder shaft because the seal member is interposed between the transmission case and the cylindrical shaft that is integrally connected to the member and rotatably supported by the hub of the differential case However, external leakage of the lubricating oil in the transmission case and differential case can be prevented, and maintenance workability is improved.

図１は本発明の第１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 gear according to a first 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は図１の３－３矢視断面図である。（第１の実施の形態）FIG. 3 is a cross-sectional view taken along arrow 3-3 in FIG. (First embodiment) 図４は図１の４－４矢視断面図である。（第１の実施の形態）4 is a cross-sectional view taken along arrow 4-4 of FIG. (First embodiment) 図５は図１の５－５矢視断面図である。（第１の実施の形態）FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. (First embodiment) 図６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. 6 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７は本発明の第２実施形態に係る差動装置の縦断正面図（図１対応図）である。（第２の実施の形態）FIG. 7 is a longitudinal sectional front view (corresponding to FIG. 1) of the differential according to the second embodiment of the present invention. (Second Embodiment)

Ｃ・・・・・・デフケース
Ｄ・・・・・・差動装置
ＨＢ２・・・・ハブとしての第２ハブ
Ｐ２ｉ・・・・油室としての第２油路の内周側油路部分
Ｓ１，Ｓ２・・第１，第２ドライブ軸としての第１，第２駆動車軸
ＳＢ１・・・・出力ボスとしての第１スプラインボス
Ｔ１，Ｔ２・・第１，第２変速機構
ＴＨ２・・・・スラストワッシャとしての第２スラストワッシャ
Ｘ１，Ｘ２・・第１，第２軸線
１・・・・・・ミッションケース
４′・・・・・シール部材
５，８，９・・第１，第２，第３伝動部材
６・・・・・・偏心回転部材
６ｅ・・・・・偏心軸部
１８，１９・・第１，第２螺旋溝
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
４２・・・・・筒軸としての第２筒軸
４７・・・・・油孔 C .... Differential case D .... Differential gear HB2 .... Second hub P2i as hub .... Inner circumference side oil passage portion S1 of second oil passage as oil chamber , S2... First and second drive axles SB1 as first and second drive shafts... First spline bosses T1 and T2 as output bosses. 2nd thrust washers X1, X2 as thrust washers, 1st, 2nd axis 1 ... Mission case 4 '... Seal members 5, 8, 9 ... 1st, 2nd Third transmission member 6... Eccentric rotation member 6 e... Eccentric shaft portions 18 and 19... First and second spiral grooves 21 and 22. ... the first rolling balls 24, 25 as the first rolling elements, the third and fourth transmission grooves 26, the second rolling elements as the second rolling elements The second cylindrical shaft 47 as the rolling ball 42 ----- tube axis ..... oil holes

　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６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 6 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側壁板部Ｃａ，Ｃｂとを備える。その少なくとも一方の側壁板部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 supported by the transmission case 1 so as to be rotatable about the first axis X1, and a differential mechanism 3 to be described later 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. Two side wall plate portions Ca and Cb are provided. At least one of the side wall plate 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側壁板部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 plate 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 the hubs 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 axles S1 when the vehicle is moving forward (ie, when the drive axles S1 and S2 are rotating forward). The 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 along with the relative rotation with S2. 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。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 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. 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側壁板部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 plate 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. 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 X1, 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 a central axis is coupled and integrated, and one side portion of the eccentric rotating member 6 is disposed to face the first transmission member 5, and the eccentric shaft portion 6e is rotatable via a bearing 7 formed of a ball bearing. The annular second transmission member 8 supported by the second transmission member 8 and the other side of the second transmission member 8 are arranged opposite to each other and are spline fitted 17 to the second drive axle S2 so as to be rotatable around 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 8, 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円環状の第１半体８ａと、その第１半体８ａに間隔をおいて対向する円環状の第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。そして、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。第１，第２半体８ａ，８ｂ及び連結部材８ｃの相互間には第２伝動部材８の中空部ＳＰが画成される。 The second transmission member 8 has 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 an interval between the first half 8a. An opposed annular second half 8b and a basically cylindrical connecting member 8c for integrally connecting the two halves 8a, 8b are provided. The first transmission mechanism T1 is provided between the first half 8a and the first transmission member 5, and the second transmission mechanism T2 is provided between the second half 8b and the third transmission member 9. It is done. A hollow portion SP of the second transmission member 8 is defined between the first and second half bodies 8a and 8b and the connecting member 8c.

　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、この第３伝動部材９の中空部において第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る円板部９ｃとが結合一体化されて構成される。 Further, the third transmission member 9 is a cylindrical second spline boss SB2 (that is, can be rotated around the first axis X1 by being spline fitted 17 to the second drive axle S2 in the hollow portion of the third transmission member 9 (that is, the third transmission member 9). A main shaft portion 9j integrally including a second output boss) and a disc portion 9c coaxially connected to the inner end portion of the main shaft portion 9j are combined and integrated.

　また、連結部材８ｃの一端部及び他端部の内周面には、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、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。 Further, the first half body 8a and the second half body 8b are respectively fitted in the inner peripheral surfaces of the one end portion and the other end portion of the connecting member 8c, and the fitting portions are appropriately fixed by welding, caulking or the like. It is fixed by means.

　デフケースＣの第１側壁板部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第１油路Ｐ１が形成される。この第１油路Ｐ１は、第１螺旋溝１８の出口が臨む環状の内周側油路部分Ｐ１ｉと、第１側壁板部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Ｐ１ｍ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Ｐ１ｏとで構成される。その外周側油路部分Ｐ１ｏ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、第１油路Ｐ１を流れる潤滑油は、外周側油路部分Ｐ１ｏ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。 A first thrust washer TH1 that allows relative rotation between the inner surface of the first side wall plate portion Ca of the differential case C and the eccentric rotating member 6 is interposed between the inner surface and the first spiral. A first oil passage P1 is formed that connects the inner end opening (that is, the outlet) of the groove 18 to the inner peripheral side of the first transmission mechanism T1 through the back surface of the first thrust washer TH1. The first oil passage P1 includes an annular inner circumferential oil passage portion P1i facing the outlet of the first spiral groove 18, a plurality of concave grooves 40 provided on the inner side surface of the first side wall plate portion Ca, and a first thrust washer. An intermediate oil passage portion P1m defined between the rear face of TH1 and an annular outer peripheral oil passage portion P1o communicating directly with the inner peripheral side of the first transmission mechanism T1. Not only the inner peripheral side of the first transmission mechanism T1 but also the bearing 7 faces the outer peripheral oil passage portion P1o, and the lubricating oil flowing through the first oil passage P1 is shifted from the outer peripheral oil passage portion P1o 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側壁板部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が介装されると共に、第２螺旋溝１９の内端開口（即ち出口）を第２スラストワッシャＴＨ２の背面を経由してデフケースＣの内部空間（図示例では第２変速機構Ｔ２の外周部周辺）に連通させる第２油路Ｐ２が形成される。この第２油路Ｐ２は、第２螺旋溝１９の出口が臨む環状の内周側油路部分Ｐ２ｉと、第２側壁板部Ｃｂの内側面に設けた複数の凹溝５０と第２スラストワッシャＴＨ２の背面との間に画成される中間油路部分Ｐ２ｍと、デフケースＣの内部空間に直接連通する外周側油路部分Ｐ２ｏとで構成される。 A second thrust washer TH2 that allows relative rotation between the inner surface of the second side wall plate portion Cb of the differential case C and the outer surface of the third transmission member 9 is interposed. At the same time, the inner end opening (that is, the outlet) of the second spiral groove 19 communicates with the internal space of the differential case C (in the illustrated example, around the outer periphery of the second transmission mechanism T2) via the back surface of the second thrust washer TH2. Two oil passages P2 are formed. The second oil passage P2 includes an annular inner peripheral oil passage portion P2i facing the outlet of the second spiral groove 19, a plurality of concave grooves 50 provided on the inner side surface of the second side wall plate portion Cb, and a second thrust washer. An intermediate oil passage portion P2m defined between the rear surface of TH2 and an outer peripheral oil passage portion P2o that directly communicates with the internal space of the differential case C.

　第３伝動部材９の円板部９ｃには、第２螺旋溝１９の出口を第２変速機構Ｔ２の内周側に連通させる複数の油孔４７が周方向に間隔をおいて形成される。その各油孔４７は、図示例では円板部９ｃを軸方向に貫通し且つ径方向に長い長孔で構成される。そして、各油孔４７の上流側開口端には、その開口面の一部に露出するように第２スラストワッシャＴＨ２の内周端部が張り出している。 In the disc portion 9c of the third transmission member 9, a plurality of oil holes 47 that communicate the outlet of the second spiral groove 19 to the inner peripheral side of the second transmission mechanism T2 are formed at intervals in the circumferential direction. In the illustrated example, each oil hole 47 is constituted by a long hole that penetrates the disk portion 9c in the axial direction and is long in the radial direction. And the inner peripheral edge part of 2nd thrust washer TH2 protrudes from the upstream opening edge of each oil hole 47 so that it may be exposed to a part of opening surface.

　尚、本実施形態では、上記油孔４７が４個設けられており、その４個を、第３伝動部材９の円板部９ｃに後述する如く形成される波形環状の第４伝動溝２５の４つの波の山部の内側位置に各々配置（図２参照）することにより、各油孔４７が第４伝動溝２５との干渉を無理なく回避しつつ径方向に長く形成できるようにしている。 In the present embodiment, the four oil holes 47 are provided, and the four oil holes 47 are formed on the disc-shaped portion 9c of the third transmission member 9 to form a corrugated annular fourth transmission groove 25. Each oil hole 47 can be formed long in the radial direction while avoiding the interference with the fourth transmission groove 25 without difficulty by arranging each of the four wave crests inside the crest (see FIG. 2). .

　また第２油路Ｐ２の内周側油路部分Ｐ２ｉは、上記油孔４７と第２螺旋溝１９の出口との間を連通させる本発明の油室を構成するものであって、第２螺旋溝１９の出口に直接連通する上流側油室部と、その上流側油室部よりも径方向幅広に形成され且つ円板部９ｃの背面が臨む下流側油室部とより構成される。そして、その内周側油路部分Ｐ２ｉ（特に上記した径方向幅広の下流側油室部）には、第２スラストワッシャＴＨ２の内周端部が臨んでいると共に油孔４７の上流側開口端が直接連通している。 Further, the inner peripheral oil passage portion P2i of the second oil passage P2 constitutes an oil chamber of the present invention that communicates between the oil hole 47 and the outlet of the second spiral groove 19, and the second spiral. An upstream oil chamber portion that directly communicates with the outlet of the groove 19 and a downstream oil chamber portion that is formed wider in the radial direction than the upstream oil chamber portion and faces the back surface of the disk portion 9c. And the inner peripheral end of the second thrust washer TH2 faces the inner peripheral oil passage portion P2i (particularly the above-described radially wide downstream oil chamber) and the upstream opening end of the oil hole 47 Are in direct communication.

　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、円板状の取付基部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. The balance weight W is composed of a disk-shaped attachment base Wm and a weight part Ww fixed to a specific region in the circumferential direction of the attachment base Wm.

　第２伝動部材８（連結部材８ｃ）の中空部ＳＰは、バランスウェイトＷを収容する収容空間として利用される。即ち、偏心回転部材６の主軸部６ｊ、特に第１スプラインボスＳＢ１は、それの内端部６ｊａが前記中空部ＳＰに延出しており、その延出端部（前記内端部６ｊａ）の開放端にバランスウェイトＷの上記取付基部Ｗｍが嵌合固定され、その取付基部Ｗｍにより、中空の主軸部６ｊ（第１スプラインボスＳＢ１）の内端側の開口部が閉塞される。その取付基部Ｗｍの固定手段としては、溶接、かしめ、圧入、接着等の従来周知の固定手段が適宜選択可能である。尚、バランスウェイトＷ（取付基部Ｗｍ）は、これを主軸部６ｊと一体に形成してもよい。 The hollow portion SP of the second transmission member 8 (the connecting member 8c) is used as an accommodation space for accommodating the balance weight W. That is, the main shaft portion 6j of the eccentric rotating member 6, especially the first spline boss SB1, has an inner end portion 6ja extending to the hollow portion SP, and an extension end portion (the inner end portion 6ja) is opened. The mounting base portion Wm of the balance weight W is fitted and fixed to the end, and the opening portion on the inner end side of the hollow main shaft portion 6j (first spline boss SB1) is closed by the mounting base portion Wm. As fixing means for the mounting base Wm, conventionally known fixing means such as welding, caulking, press-fitting, and adhesion can be appropriately selected. The balance weight W (mounting base Wm) may be formed integrally with the main shaft portion 6j.

　また偏心回転部材６（主軸部６ｊ）には、第１螺旋溝１８の出口から第１駆動車軸Ｓ１と主軸部６ｊ（即ち第１スプラインボスＳＢ１）とのスプライン嵌合部１６に流入した潤滑油を第１変速機構Ｔ１の内周側に導く少なくとも１つの油孔４５が、主軸部６ｊを径方向に貫通するよう形成される。この油孔４５の内端開口は、図３に明示したように第１駆動車軸Ｓ１外周側のスプライン欠歯部４３に直接連通しており、そのスプライン欠歯部４３を流れる潤滑油を効率よく油孔４５に供給し、そこから第１変速機構Ｔ１の内周側にスムーズに導けるようになっている。 Further, the eccentric rotating member 6 (main shaft portion 6j) has lubricating oil that has flowed into the spline fitting portion 16 between the first drive axle S1 and the main shaft portion 6j (ie, the first spline boss SB1) from the outlet of the first spiral groove 18. Is formed so as to penetrate the main shaft portion 6j in the radial direction. As shown in FIG. 3, the inner end opening of the oil hole 45 communicates directly with the spline missing tooth portion 43 on the outer periphery side of the first drive axle S1, and the lubricating oil flowing through the spline missing tooth portion 43 is efficiently obtained. The oil is supplied to the oil hole 45 and can be smoothly guided from there to the inner peripheral side of the first transmission mechanism T1.

　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 to 3, the inner surface of the first transmission member 5 facing the one side portion (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 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 portion (second half body 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 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.

　また本実施形態では、第１保持部材Ｈ１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保持部材Ｈ１並びに第１及び第２伝動溝２１，２２の各形状が設定される。また第２保持部材Ｈ２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ように、第２保持部材Ｈ２並びに第３及び第４伝動溝２４，２５の各形状が設定される。 Further, 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 H1, and the first and second transmission grooves 21 and 22 pass through the openings IN1 and IN2. The shapes of the first holding member H1 and the first and second transmission grooves 21 and 22 are set so that the lubricating oil flow into the two transmission grooves 21 and 22 is allowed. Further, 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 H2, and the third and fourth transmission grooves 24, 25 are opened through the openings IN3, IN4. The shapes of the second holding member H2 and the third and fourth transmission grooves 24 and 25 are set so that the lubricating oil flow into the 25 is allowed.

　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 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

　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。 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.

　差動装置Ｄの上記した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６に示すようにデフケースＣのハブＨＢ１，ＨＢ２と駆動車軸Ｓ１，Ｓ２との相対回転に伴う螺旋溝１８，１９の引き込み作用により、デフケースＣ内に積極的に供給される。 In the above-described torque transmission process of the differential device D, the stored lubricating oil at the bottom of the transmission case 1 is stirred by the differential case C or the like and scattered in the transmission case 1 over a wide range as described above. As shown in FIG. 6, a part of the scattered lubricating oil is brought into the differential case C by the pulling action of the spiral grooves 18 and 19 accompanying the relative rotation between the hubs HB1 and HB2 of the differential case C and the drive axles S1 and S2. Actively supplied.

　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第１油路Ｐ１（即ち内周側油路部分Ｐ１ｉ→中間油路部分Ｐ１ｍ→外周側油路部分Ｐ１ｏ）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。また第１螺旋溝１８の出口に達した潤滑油の残部は、スプライン嵌合部１６（特に前記したスプライン欠歯部４３）から油孔４５を経由して第１油路Ｐ１の外周側油路部分Ｐ１ｏに合流し、第１変速機構Ｔ１及び軸受７を潤滑する。この場合、本実施形態では偏心回転部材６の中空の主軸部６ｊの内端側の開口部がバランスウェイトＷで閉塞されるため、主軸部６ｊ内での潤滑油の素通りが規制される。尚、第１変速機構Ｔ１を通過した油は、デフケースＣの内部空間ＩＣに流入する。 At this time, in particular, a part of the lubricating oil that has reached the outlet of the first spiral groove 18 is the first oil passage P1 (that is, the inner oil passage portion P1i → the intermediate oil passage portion P1m → the outer periphery side) due to the centrifugal force. It flows to the bearing 7 on the inner peripheral side of the first transmission mechanism T1 and the eccentric shaft portion 6e via the oil passage portion P1o), and lubricates the first thrust washer TH1, the first transmission mechanism T1, and the bearing 7. Further, the remaining portion of the lubricating oil that has reached the outlet of the first spiral groove 18 passes through the oil hole 45 from the spline fitting portion 16 (particularly, the aforementioned spline toothless portion 43) to the outer peripheral oil passage of the first oil passage P1. Joining the portion P1o, the first transmission mechanism T1 and the bearing 7 are lubricated. In this case, in this embodiment, since the opening on the inner end side of the hollow main shaft portion 6j of the eccentric rotating member 6 is closed by the balance weight W, the passage of the lubricating oil in the main shaft portion 6j is restricted. The oil that has passed through the first transmission mechanism T1 flows into the internal space IC of the differential case C.

　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第２油路Ｐ２（即ち内周側油路部分Ｐ２ｉ→中間油路部分Ｐ２ｍ→外周側油路部分Ｐ２ｏ）を経由してデフケースＣの内部空間ＩＣ（特に第２変速機構Ｔ２の外周部近傍）に流動すると共に、その途中（即ち油室としての内周側油路部分Ｐ２ｉ）から油孔４７を経由して第３伝動部材９の内方空間に分流して、遠心力で第２変速機構Ｔ２の内周側に向かい、第２スラストワッシャＴＨ２や第２変速機構Ｔ２を潤滑する。また第２螺旋溝１９の出口に達した潤滑油の残部は、スプライン嵌合部１７を通して第３伝動部材９の内方空間に導入され、更に第２油流通孔１２を経て第２伝動部材８の中空部ＳＰにも導入される。その導入潤滑油は、遠心力で径方向外方に流動して第２変速機構Ｔ２の内周側や偏心軸部６ｅ上の軸受７に向かって流動し、それらを潤滑する。そして、第２変速機構Ｔ２を通過した油は、デフケースＣの内部空間ＩＣに流入する。 On the other hand, a part of the lubricating oil that has reached the outlet of the second spiral groove 19 is subjected to the centrifugal force by the second oil passage P2 (that is, the inner oil passage portion P2i → the intermediate oil passage portion P2m → the outer oil passage). The oil hole 47 flows into the internal space IC of the differential case C (particularly in the vicinity of the outer peripheral portion of the second transmission mechanism T2) via the portion P2o), and from the middle (that is, the inner peripheral oil passage portion P2i as an oil chamber) To the inner space of the third transmission member 9, and toward the inner peripheral side of the second transmission mechanism T2 by centrifugal force to lubricate the second thrust washer TH2 and the second transmission mechanism T2. Further, the remaining portion of the lubricating oil that has reached the outlet of the second spiral groove 19 is introduced into the inner space of the third transmission member 9 through the spline fitting portion 17, and further through the second oil circulation hole 12 to the second transmission member 8. The hollow portion SP is also introduced. The introduced lubricating oil flows radially outward by centrifugal force, flows toward the inner peripheral side of the second transmission mechanism T2 and the bearing 7 on the eccentric shaft portion 6e, and lubricates them. The oil that has passed through the second speed change mechanism T2 flows into the internal space IC of the differential case C.

　また第２伝動部材８（連結部材８ｃ）に設けた複数の第１油流通孔１１は、これらがデフケースＣの内部空間ＩＣに広く開口するため、第１油流通孔１１を通してデフケースＣの内部空間ＩＣと第２伝動部材８の中空部ＳＰとの間で潤滑油がスムーズに出入り可能である。従って、デフケースＣの内部空間ＩＣに流入飛散する潤滑油の一部は、第１油流通孔１１からも第２伝動部材８の中空部ＳＰに戻される。 Further, since the plurality of first oil circulation holes 11 provided in the second transmission member 8 (the connecting member 8 c) are widely opened in the internal space IC of the differential case C, the internal space of the differential case C through the first oil circulation hole 11. Lubricating oil can smoothly enter and exit between the IC and the hollow portion SP of the second transmission member 8. Accordingly, part of the lubricating oil that flows into and diffuses into the internal space IC of the differential case C is also returned from the first oil circulation hole 11 to the hollow portion SP of the second transmission member 8.

　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、軸受７、各スラストワッシャＴＨ１，ＴＨ２等の摺動部が効果的に潤滑される。 Thus, in the torque transmission process of the differential device D, the sliding portions such as the first and second transmission mechanisms T1 and T2, the bearing 7 and the thrust washers TH1 and TH2 are effectively lubricated in the differential case C. .

　特に本実施形態によれば、第１軸線Ｘ１回りに回転可能な扁平な第１伝動部材５と、第１軸線Ｘ１回りに回転可能な中空の主軸部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を一体に有する偏心回転部材６と、第１伝動部材５に対向配置されて偏心軸部６ｅに回転自在に支持される第２伝動部材８と、第１軸線Ｘ１回りに回転可能な第２伝動部材８に対向配置される扁平な第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、両変速機構Ｔ１，Ｔ２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ため、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 particular, according to the present embodiment, the flat first transmission member 5 that can rotate around the first axis X1, the hollow main shaft portion 6j that can rotate around the first axis X1, and the first axis X1 that is eccentric from the first axis X1. An eccentric rotation member 6 integrally including an eccentric shaft portion 6e having a biaxial line X2 as a central axis; a second transmission member 8 disposed opposite to the first transmission member 5 and rotatably supported by the eccentric shaft portion 6e; A flat third transmission member 9 disposed opposite to the second transmission member 8 rotatable around the first axis X1 and a first transmission capable of transmitting torque while shifting between the first and second transmission members 5 and 8. A mechanism T1 and a second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 8 and 9, and when both the transmission mechanisms T1 and T2 fix the eccentric rotating member 6; The first transmission member 5 to the third transmission member 9 are driven with a double speed increase ratio. For constitution, differential D which are readily flattened compact in the axial direction is obtained.

　その上、本実施形態では、第３伝動部材９とデフケースＣ（第２側壁板部Ｃｂ）との相対向面間にスラストワッシャとしての第２スラストワッシャＴＨ２が介装されるので、そのスラストワッシャＴＨ２の厚みを調整することで、第１及び第３伝動部材５，９間の軸方向の遊びが容易且つ的確に排除可能となり、第１，第２変速機構Ｔ１，Ｔ２の良好な伝動機能を確保することができ、のみならず、第３伝動部材９とデフケースＣとの対向面相互の円滑な摺動も確保可能となる。 In addition, in the present embodiment, since the second thrust washer TH2 as a thrust washer is interposed between the opposing surfaces of the third transmission member 9 and the differential case C (second sidewall plate portion Cb), the thrust washer By adjusting the thickness of TH2, the axial play between the first and third transmission members 5, 9 can be easily and accurately eliminated, and the good transmission function of the first and second transmission mechanisms T1, T2 can be achieved. As well as ensuring smooth sliding between the opposing surfaces of the third transmission member 9 and the differential case C can be ensured.

　さらに本実施形態では、第２駆動車軸Ｓ２と第２ハブＨＢ２との嵌合面の一方に、ミッションケース１内の潤滑油を第２ハブＨＢ２の外端側から内端側に引き込み可能な螺旋溝としての第２螺旋溝１９が設けられると共に、この第２螺旋溝１９の出口を第２変速機構Ｔ２の内周側に連通させる油孔４７が第３伝動部材９に設けられるので、第２螺旋溝１９を通してミッションケース１側からデフケースＣ側へ潤滑油を引き込んだ潤滑油を第３伝動部材９の油孔４７を通して第２変速機構Ｔ２の内周側に流入させ、そこから遠心力の作用で径方向外方に飛散させて第２変速機構Ｔ２に潤滑油を効率よく供給可能となり、その第２変速機構Ｔ２を効果的に潤滑できる。しかも油孔４７と第２螺旋溝１９の出口との間には、その間を連通させ且つスラストワッシャＴＨ２の内周端を臨ませる油室（即ち第２油路Ｐ２の内周側油路部分Ｐ２ｉ）が設けられるので、第２螺旋溝１９を通してミッションケース１側からデフケースＣ側へ引き込まれて油室（即ち第２油路Ｐ２の内周側油路部分Ｐ２ｉ）に流入した潤滑油は、そこから油孔４７側とスラストワッシャＴＨ２側とに分流し、これにより、上述のように第２変速機構Ｔ２を効果的に潤滑できるばかりか、スラストワッシャＴＨ２と第３伝動部材９及びデフケースＣとの各間の摺動面をも効果的に潤滑できる。 Furthermore, in the present embodiment, the spiral in which the lubricating oil in the transmission case 1 can be drawn from the outer end side to the inner end side of the second hub HB2 on one of the fitting surfaces of the second drive axle S2 and the second hub HB2. A second spiral groove 19 as a groove is provided, and an oil hole 47 that communicates the outlet of the second spiral groove 19 with the inner peripheral side of the second transmission mechanism T2 is provided in the third transmission member 9. The lubricating oil drawn in from the transmission case 1 side to the differential case C side through the spiral groove 19 is caused to flow into the inner peripheral side of the second transmission mechanism T2 through the oil hole 47 of the third transmission member 9, and the action of centrifugal force is generated therefrom. Thus, the lubricating oil can be efficiently supplied to the second speed change mechanism T2 by being scattered radially outward, and the second speed change mechanism T2 can be effectively lubricated. Moreover, between the oil hole 47 and the outlet of the second spiral groove 19, an oil chamber (that is, the inner peripheral oil passage portion P2i of the second oil passage P2) that communicates between the oil hole 47 and the inner peripheral end of the thrust washer TH2 is provided. ) Is provided, the lubricating oil drawn into the differential case C side from the transmission case 1 side through the second spiral groove 19 and flowing into the oil chamber (that is, the inner peripheral side oil passage portion P2i of the second oil passage P2) To the oil hole 47 side and the thrust washer TH2 side, thereby not only can the second transmission mechanism T2 be effectively lubricated as described above, but also the thrust washer TH2, the third transmission member 9 and the differential case C The sliding surface between each can be effectively lubricated.

第２の実施の形態Second embodiment

　次に図７を参照して本発明の第２実施形態について説明する。この第２実施形態の偏心回転部材６の主軸部６ｊ（第１スプラインボスＳＢ１）には、デフケースＣの第１ハブＨＢ１に回転自在に嵌合支持される第１筒軸４１が同軸且つ一体的に連設され、また第３伝動部材９の主軸部９ｊ（第２スプラインボスＳＢ２）には、デフケースＣの第２ハブＨＢ２に回転自在に嵌合支持される第２筒軸４２が同軸且つ一体的に連設される。 Next, a second embodiment of the present invention will be described with reference to FIG. A first cylindrical shaft 41 rotatably fitted to and supported by the first hub HB1 of the differential case C is coaxially and integrally formed on the main shaft portion 6j (first spline boss SB1) of the eccentric rotating member 6 of the second embodiment. The second cylindrical shaft 42 is coaxially and integrally provided on the main shaft portion 9j (second spline boss SB2) of the third transmission member 9 and rotatably fitted to and supported by the second hub HB2 of the differential case C. Connected continuously.

　第１ハブＨＢ１と第１筒軸４１との嵌合面の一方（図示例では第１ハブＨＢ１）には、それら第１筒軸４１と第１ハブＨＢ１との相対回転によりミッションケース１内の潤滑油を第１ハブＨＢ１の外端側から内端側に引き込み可能な第１螺旋溝１８が設けられると共に、この第１螺旋溝１８の出口を第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第１油路Ｐ１が、デフケースＣと偏心回転部材６との間に設けられる。 One of the fitting surfaces of the first hub HB1 and the first cylinder shaft 41 (the first hub HB1 in the illustrated example) has a relative rotation between the first cylinder shaft 41 and the first hub HB1 so that the inside of the transmission case 1 A first spiral groove 18 capable of drawing lubricating oil from the outer end side to the inner end side of the first hub HB1 is provided, and an outlet of the first spiral groove 18 is passed through the back surface of the first thrust washer TH1. A first oil passage P <b> 1 communicating with the inner peripheral side of the first transmission mechanism T <b> 1 is provided between the differential case C and the eccentric rotating member 6.

　また第２ハブＨＢ２と第２筒軸４２との嵌合面の一方（図示例では第２ハブＨＢ２）には、それら第２筒軸４２と第２ハブＨＢ２との相対回転によりミッションケース１内の潤滑油を第２ハブＨＢ２の外端側から内端側に引き込み可能な第２螺旋溝１９が設けられると共に、この第２螺旋溝１９の出口を第２スラストワッシャＴＨ２の背面を経由してデフケースＣの内部空間（図示例では第２変速機構Ｔ２の外周部周辺）に連通させる第２油路Ｐが、デフケースＣと第３伝動部材９との間に設けられる。尚、第１，第２螺旋溝１８，１９及び第１，第２油路Ｐ１，Ｐ２の構成は、第１実施形態と同様である。尚また、第１，第２筒軸４１，４２の肉厚が十分有る場合には、第１，第２筒軸４１，４２側に第１，第２螺旋溝１８，１９を形成するようにしてもよい。 One of the fitting surfaces (second hub HB2 in the illustrated example) between the second hub HB2 and the second cylinder shaft 42 is placed in the transmission case 1 by relative rotation between the second cylinder shaft 42 and the second hub HB2. Of the second hub HB2 from the outer end side to the inner end side is provided, and the outlet of the second spiral groove 19 is routed through the back surface of the second thrust washer TH2. A second oil passage P communicating with the internal space of the differential case C (in the illustrated example, around the outer periphery of the second speed change mechanism T2) is provided between the differential case C and the third transmission member 9. The configurations of the first and second spiral grooves 18 and 19 and the first and second oil passages P1 and P2 are the same as those in the first embodiment. If the first and second cylinder shafts 41 and 42 are sufficiently thick, the first and second spiral grooves 18 and 19 are formed on the first and second cylinder shafts 41 and 42 side. May be.

　そして、第１，第２筒軸４１，４２の、第１，第２ハブＨＢ１，ＨＢ２から外方に延出する外端部４１ａ，４２ａの外周部と、ミッションケース１との間には、その間をシールする環状のシール部材４，４′がそれぞれ介装される。 And between the outer periphery of the outer end portions 41a and 42a extending outward from the first and second hubs HB1 and HB2 of the first and second cylindrical shafts 41 and 42, and the transmission case 1, Annular seal members 4 and 4 ′ for sealing the gap are interposed.

　また第３伝動部材９の中空の主軸部９ｊ（第２スプラインボスＳＢ２）の、スプライン歯が刻設された内周面は、第２ドライブ軸としての第２駆動車軸Ｓ２に一体に回転するよう連結される本発明の連結孔を構成するものであり、その連結孔（従って主軸部９ｊの中空部）の内端側、即ち第２駆動車軸Ｓ２とは反対側の開口部を閉塞する閉塞壁４４が主軸部９ｊ（第２スプラインボスＳＢ２）に一体に形成される。尚、この閉塞壁４４を主軸部９ｊとは別体に形成して、主軸部９ｊに後付けで固着してもよい。 Further, the inner peripheral surface of the hollow main shaft portion 9j (second spline boss SB2) of the third transmission member 9 on which the spline teeth are engraved rotates integrally with the second drive axle S2 as the second drive shaft. A blocking wall that constitutes the connecting hole of the present invention to be connected and closes the inner end side of the connecting hole (and hence the hollow portion of the main shaft portion 9j), that is, the opening opposite to the second drive axle S2. 44 is formed integrally with the main shaft portion 9j (second spline boss SB2). The blocking wall 44 may be formed separately from the main shaft portion 9j and fixed to the main shaft portion 9j by retrofitting.

　また第２実施形態の偏心回転部材６には、第１実施形態の油孔４５に相当する孔は形成されない。 Further, the eccentric rotating member 6 of the second embodiment is not formed with a hole corresponding to the oil hole 45 of the first embodiment.

　その他の構成は、第１実施形態と同様であるので、各構成要素に第１実施形態と同様の参照符号を付すに止め、説明を省略する。 Other configurations are the same as those of the first embodiment, and therefore, the same reference numerals as those of the first embodiment are assigned to the respective components, and the description thereof is omitted.

　而して、本第２実施形態によれば、第１実施形態の前記した効果と同等の効果を達成可能である。 Thus, according to the second embodiment, it is possible to achieve an effect equivalent to the above-described effect of the first embodiment.

　その上、本第２実施形態では、偏心回転部材６の中空の主軸部６ｊ（第１スプラインボスＳＢ１）の内端側の開口部がバランスウェイトＷで閉塞されるのみならず、第３伝動部材９の中空の主軸部９ｊ（第２スプラインボスＳＢ２）の内端側の開口部が閉塞壁４４で閉塞され、更に第１実施形態の油孔４５を偏心回転部材６が有しないため、第１駆動車軸Ｓ１を偏心回転部材６の主軸部６ｊ（第１筒軸４１）から引き抜いた場合でも、また第２駆動車軸Ｓ２を第３伝動部材９の主軸部９ｊ（第２筒軸４２）から引き抜いた場合でも、ミッションケース１及びデフケースＣ内の潤滑油の外部漏出を防止でき、メンテナンス作業性が良好となる。しかも第１，第２螺旋溝１８，１９の出口に達した潤滑油の、両主軸部６ｊ，９ｊ内での素通りが無くなるため、その潤滑油を第１，第２油路Ｐ１，Ｐ２側に十分に供給でき、その両油路Ｐ１，Ｐ２による潤滑効果がより高められる。 In addition, in the second embodiment, the opening on the inner end side of the hollow main shaft portion 6j (first spline boss SB1) of the eccentric rotating member 6 is not only closed by the balance weight W, but also the third transmission member. 9 because the opening on the inner end side of the hollow main shaft portion 9j (second spline boss SB2) 9 is closed by the closing wall 44, and the eccentric rotation member 6 does not have the oil hole 45 of the first embodiment. Even when the driving axle S1 is pulled out from the main shaft portion 6j (first cylindrical shaft 41) of the eccentric rotating member 6, the second driving axle S2 is pulled out from the main shaft portion 9j (second cylindrical shaft 42) of the third transmission member 9. Even in this case, external leakage of the lubricating oil in the transmission case 1 and the differential case C can be prevented, and the maintenance workability is improved. Moreover, since the lubricating oil that has reached the outlets of the first and second spiral grooves 18 and 19 does not pass through the main shaft portions 6j and 9j, the lubricating oil is moved to the first and second oil passages P1 and P2 side. Sufficient supply is possible, and the lubrication effect by both the oil passages P1, P2 is further enhanced.

　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、差動装置Ｄを自動車のミッションケース１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。 For example, in the above-described embodiment, the differential device D is accommodated in the transmission case 1 of the automobile. However, the differential device D is not limited to the differential apparatus for automobiles, and is used for various mechanical devices. It can be implemented as a differential device.

　また、前記実施形態では、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、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-described embodiment, the differential device D 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. In the present invention, the differential device may be applied to a front / rear wheel transmission system in a front / rear wheel drive vehicle to distribute power while allowing differential rotation to the front and rear drive wheels.

　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、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Ｘ１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１又は第２変速機構の一方又は両方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, T2 both use rolling ball type transmission mechanisms, but are not limited to the structure of the above-described embodiment. That is, various transmission 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 X1 in conjunction with the rotation thereof, for example, an internal planetary gear You may make it apply a mechanism, a cycloid reducer (speed increaser) of various structures, or a trochoid reduction gear (speed increaser) to one or both of a 1st or 2nd transmission mechanism.

　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、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.

　また前記実施形態では、第３伝動部材９に設けられて第２螺旋溝１９の出口を第２変速機構Ｔ２の内周側に連通させる油孔４７の上流側開口端が、第２油路Ｐ２の一部（即ち油室としての内周側油路部分Ｐ２ｉ）やスラストワッシャＴＨ２を経由して第２螺旋溝１９の出口に連通するものを例示したが、第３伝動部材９の形状変更や油孔４７のレイアウト変更によっては、油孔４７の上流側開口端を第２螺旋溝１９の出口に直接（即ち第２油路Ｐ２やスラストワッシャＴＨ２を経由せずに）連通させるようにしてもよい。
  In the above embodiment, the upstream opening end of the oil hole 47 provided in the third transmission member 9 and communicating the outlet of the second spiral groove 19 to the inner peripheral side of the second transmission mechanism T2 is the second oil passage P2. Are illustrated (that is, the inner circumferential oil passage portion P2i as the oil chamber) and the one communicating with the outlet of the second spiral groove 19 via the thrust washer TH2, but the shape change of the third transmission member 9 Depending on the layout change of the oil hole 47, the upstream opening end of the oil hole 47 may be directly communicated with the outlet of the second spiral groove 19 (that is, not via the second oil passage P2 or the thrust washer TH2). Good.

Claims (5)

1. 　ミッションケース（１）内に配置され、回転力を受けて第１軸線（Ｘ１）回りに回転するデフケース（Ｃ）と、
   　このデフケース（Ｃ）と共に第１軸線（Ｘ１）回りに回転可能な第１伝動部材（５）と、
   　第１ドライブ軸（Ｓ１）に接続されて第１軸線（Ｘ１）回りに回転可能な第１出力ボス（ＳＢ１）、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）が一体に連結された偏心回転部材（６）と、
   　前記第１伝動部材（５）に対向配置されて前記偏心軸部（６ｅ）に回転自在に支持される第２伝動部材（８）と、
   　前記第２伝動部材（８）に対向配置され第１軸線（Ｘ１）回りに回転可能な第３伝動部材（９）と、
   　前記第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、
   　前記第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、
   　前記第１，第２変速機構（Ｔ１，Ｔ２）が、前記偏心回転部材（６）を固定したときに前記第１伝動部材（５）から前記第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てなる差動装置であって、
   　前記第３伝動部材（９）には、前記デフケース（Ｃ）に設けたハブ（ＨＢ２）に回転自在に嵌合支持される第２ドライブ軸（Ｓ２）が連結され、
   　前記ハブ（ＨＢ２）と前記第２ドライブ軸（Ｓ２）との嵌合面の一方には、それらハブ（ＨＢ２）と第２ドライブ軸（Ｓ２）との相対回転により前記ミッションケース（１）内の潤滑油を該ハブ（ＨＢ２）の外端側から内端側に引き込み可能な螺旋溝（１９）が設けられると共に、この螺旋溝（１９）の出口を前記第２変速機構（Ｔ２）の内周側に連通させる油孔（４７）が前記第３伝動部材（９）に設けられることを特徴とする差動装置。 A differential case (C) disposed in the mission case (1) and rotating around the first axis (X1) upon receiving a rotational force;
   A first transmission member (5) rotatable around the first axis (X1) together with the differential case (C);
   A first output boss (SB1) connected to the first drive shaft (S1) and rotatable about the first axis (X1), and a second axis (X2) eccentric from the first axis (X1) are defined as a central axis. An eccentric rotation member (6) integrally connected to the eccentric shaft portion (6e),
   A second transmission member (8) disposed opposite to the first transmission member (5) and rotatably supported by the eccentric shaft portion (6e);
   A third transmission member (9) disposed opposite to the second transmission member (8) and rotatable about a first axis (X1);
   A first transmission mechanism (T1) capable of transmitting torque while shifting between the first and second transmission members (5, 8);
   A second transmission mechanism (T2) capable of transmitting torque while shifting between the second and third transmission members (8, 9);
   When the first and second speed change mechanisms (T1, T2) fix the eccentric rotation member (6), the first transmission member (5) to the third transmission member (9) are doubled. A differential configured to be driven with a ratio,
   The third drive member (9) is connected to a second drive shaft (S2) rotatably fitted and supported by a hub (HB2) provided in the differential case (C),
   One of the fitting surfaces of the hub (HB2) and the second drive shaft (S2) has a relative rotation between the hub (HB2) and the second drive shaft (S2) so that the inside of the transmission case (1) A spiral groove (19) capable of drawing lubricating oil from the outer end side to the inner end side of the hub (HB2) is provided, and an outlet of the spiral groove (19) is provided at the inner periphery of the second transmission mechanism (T2). An oil hole (47) communicating with the side is provided in the third transmission member (9).
2. 　ミッションケース（１）内に配置され、回転力を受けて第１軸線（Ｘ１）回りに回転するデフケース（Ｃ）と、
   　このデフケース（Ｃ）と共に第１軸線（Ｘ１）回りに回転可能な第１伝動部材（５）と、
   　第１ドライブ軸（Ｓ１）に接続されて第１軸線（Ｘ１）回りに回転可能な第１出力ボス（ＳＢ１）、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）が一体に連結された偏心回転部材（６）と、
   　前記第１伝動部材（５）に対向配置されて前記偏心軸部（６ｅ）に回転自在に支持される第２伝動部材（８）と、
   　前記第２伝動部材（８）に対向配置され第１軸線（Ｘ１）回りに回転可能な第３伝動部材（９）と、
   　前記第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、
   　前記第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、
   　前記第１，第２変速機構（Ｔ１，Ｔ２）が、前記偏心回転部材（６）を固定したときに前記第１伝動部材（５）から前記第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てなる差動装置であって、
   　前記第３伝動部材（９）には、前記デフケース（Ｃ）に設けたハブ（ＨＢ２）に回転自在に嵌合支持される筒軸（４２）が一体的に連設されると共に、その筒軸（４２）を通して該第３伝動部材（９）が第２ドライブ軸（Ｓ２）に連結され、
   　前記ハブ（ＨＢ２）と前記筒軸（４２）との嵌合面の一方には、それらハブ（ＨＢ２）と筒軸（４２）との相対回転により前記ミッションケース（１）内の潤滑油を該ハブ（ＨＢ２）の外端側から内端側に引き込み可能な螺旋溝（１９）が設けられると共に、この螺旋溝（１９）の出口を前記第２変速機構（Ｔ２）の内周側に連通させる油孔（４７）が前記第３伝動部材（９）に設けられることを特徴とする差動装置。 A differential case (C) disposed in the mission case (1) and rotating around the first axis (X1) upon receiving a rotational force;
   A first transmission member (5) rotatable around the first axis (X1) together with the differential case (C);
   A first output boss (SB1) connected to the first drive shaft (S1) and rotatable about the first axis (X1), and a second axis (X2) eccentric from the first axis (X1) are defined as a central axis. An eccentric rotation member (6) integrally connected to the eccentric shaft portion (6e),
   A second transmission member (8) disposed opposite to the first transmission member (5) and rotatably supported by the eccentric shaft portion (6e);
   A third transmission member (9) disposed opposite to the second transmission member (8) and rotatable about a first axis (X1);
   A first transmission mechanism (T1) capable of transmitting torque while shifting between the first and second transmission members (5, 8);
   A second transmission mechanism (T2) capable of transmitting torque while shifting between the second and third transmission members (8, 9);
   When the first and second speed change mechanisms (T1, T2) fix the eccentric rotation member (6), the first transmission member (5) to the third transmission member (9) are doubled. A differential configured to be driven with a ratio,
   The third transmission member (9) is integrally provided with a cylindrical shaft (42) rotatably fitted to and supported by a hub (HB2) provided in the differential case (C). The third transmission member (9) is connected to the second drive shaft (S2) through (42),
   On one of the fitting surfaces of the hub (HB2) and the cylindrical shaft (42), the lubricating oil in the transmission case (1) is caused by the relative rotation of the hub (HB2) and the cylindrical shaft (42). A spiral groove (19) that can be pulled in from the outer end side to the inner end side of the hub (HB2) is provided, and the outlet of the spiral groove (19) communicates with the inner peripheral side of the second transmission mechanism (T2). An oil hole (47) is provided in the third transmission member (9).
3. 　前記第３伝動部材（９）の外側面と前記デフケース（Ｃ）の内側面との相対向面間には、その間の相対回転を許容するスラストワッシャ（ＴＨ２）が介装され、前記螺旋溝（１９）の出口と前記油孔（４７）との間には、その間を連通させ且つ前記スラストワッシャ（ＴＨ２）の内周端を臨ませる油室（Ｐ２ｉ）が設けられることを特徴とする、請求項１又は２に記載の差動装置。 A thrust washer (TH2) allowing relative rotation between the outer surface of the third transmission member (9) and the inner surface of the differential case (C) is interposed between the spiral groove ( 19) An oil chamber (P2i) is provided between the outlet of 19) and the oil hole (47) so as to communicate therewith and to face the inner peripheral end of the thrust washer (TH2). Item 3. The differential device according to Item 1 or 2.
4. 　前記第１変速機構（Ｔ１）は、第１伝動部材（５）の、第２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）との対向面に在り且つ第２軸線（Ｘ２）を中心とす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）の複数の交差部に各々介装され、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）とを有し、
   　前記第２変速機構（Ｔ２）は、第２伝動部材（８）の、第３伝動部材（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）との対向面に在り且つ第１軸線（Ｘ１）を中心とする波形環状で波数が第３伝動溝（２５）とは異なる第４伝動溝（２５）と、第３及び第４伝動溝（２４，２５）の複数の交差部に介装され、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）とを有し、
   　前記第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、次式
   　（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
   が成立することを特徴とする、請求項１～３の何れか１項に記載の差動装置。 The first transmission mechanism (T1) is located on a surface of the first transmission member (5) facing the second transmission member (8) and has a corrugated annular first transmission groove centered on the first axis (X1). (21) and the second transmission member (8) on the surface facing the first transmission member (5) and having a corrugated annular shape centered on the second axis (X2) and having a wave number of the first transmission groove (21) Different from the second transmission groove (22) and the plurality of intersecting portions of the first and second transmission grooves (21, 22), and rolls through the first and second transmission grooves (21, 22). While having a plurality of first rolling elements (23) involved in the transmission transmission between the first and second transmission members (5, 8),
   The second transmission mechanism (T2) is located on the surface of the second transmission member (8) facing the third transmission member (9) and has a wave-shaped third transmission groove centered on the second axis (X2). (24) and the third transmission member (9) on the surface facing the second transmission member (8) and having a corrugated annular shape centered on the first axis (X1) and having a wave number of the third transmission groove (25) Different from the fourth transmission groove (25) and a plurality of intersections of the third and fourth transmission grooves (24, 25), and rolls on the third and fourth transmission grooves (24, 25). A plurality of second rolling elements (26) for performing transmission transmission between the second and third transmission members (8, 9),
   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. Then, the following formula (Z1 / Z2) × (Z3 / Z4) = 2
   The differential device according to any one of claims 1 to 3, wherein:
5. 　前記第３伝動部材（９）に設けられて該第３伝動部材（９）を前記第２ドライブ軸（Ｓ２）に連結する連結孔の、第２ドライブ軸（Ｓ２）と反対側の端部が閉塞され、前記筒軸（４２）と前記ミッションケース（１）との間にシール部材（４′）が介装されることを特徴とする、請求項２に記載の差動装置。
     An end portion of the connecting hole provided on the third transmission member (9) for connecting the third transmission member (9) to the second drive shaft (S2) is opposite to the second drive shaft (S2). 3. The differential device according to claim 2, wherein the differential member is closed and a sealing member (4 ') is interposed between the cylindrical shaft (42) and the transmission case (1).
   

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