JP2017115993A - Differential device - Google Patents

Differential device Download PDF

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JP2017115993A
JP2017115993A JP2015252330A JP2015252330A JP2017115993A JP 2017115993 A JP2017115993 A JP 2017115993A JP 2015252330 A JP2015252330 A JP 2015252330A JP 2015252330 A JP2015252330 A JP 2015252330A JP 2017115993 A JP2017115993 A JP 2017115993A
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transmission
axis
transmission member
shaft portion
eccentric
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祥吾 相根
Shogo Aine
祥吾 相根
濱田　哲郎
Tetsuo Hamada
哲郎 濱田
慎弥 松岡
Shinya Matsuoka
慎弥 松岡
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Musashi Seimitsu Industry Co Ltd
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Musashi Seimitsu Industry Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To efficiently lubricate a first transmission mechanism while taking advantages of a differential device, in the differential device including a first transmission member having a first axis as a center axis, an eccentric rotary member configured by integrally connecting a main shaft portion rotatable around the first axis to an eccentric shaft portion applying a second axis eccentric from the first axis, as a center axis, a second transmission member opposed to the first transmission member and rotatably supported by the eccentric shaft portion, a third transmission member opposed to the second transmission member and rotatable around the first axis, a first transmission mechanism between the first and second transmission members, and a second transmission mechanism between the second and third transmission members.SOLUTION: A balance weight W accommodated in a space SP of a second transmission member 8 is disposed on a main shaft portion 6j in a state of being closed at its opening end, a spiral groove 18 capable of drawing in a lubricant in a mission case 1 is formed on fitting faces of a driving axle S1 and a differential case hub HB1, and an oil passage P1 for communicating a groove outlet to an inner peripheral side of a first transmission mechanism T1 is formed between the differential case c and an eccentric rotary member 6.SELECTED DRAWING: Figure 1

Description

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中空の主軸部、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、デフ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 hollow main shaft portion connected to the first shaft and rotatable about the first axis, and An eccentric rotating member in which an eccentric shaft portion having a second axis line eccentric from the first axis line as a central axis line is integrally connected, and a second transmission that is disposed to face the first transmission member and is rotatably supported by the eccentric shaft portion. Torque can be transmitted while shifting between the first transmission member, a third transmission member that is disposed opposite to the second transmission member, is connected to the second shaft, and is rotatable about the first axis. A first speed change mechanism and a second speed change mechanism capable of transmitting torque while shifting between the second and third transmission members, and having a structure capable of being driven to decelerate from one of the first and second shafts to the other. The device is known. And this thing of this patent document 2 is compact between the 1st, 3rd transmission member and the 2nd transmission member, and the 1st, 2nd transmission mechanism (for example, a ball and this rolls) compact in the axial direction of a differential case. 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.

特開２０１２−６７８８９号公報JP 2012-67889 A 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 flatten 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、例えばケースに入力された回転力を第１，第２軸に分配するようなことはできない。また、この特許文献２の伝動装置では、偏心回転部材の偏心軸部及び第２伝動部材を含む偏心回転系の重心位置が、第１軸線から第２軸線の方向に離間した位置に偏在するため、偏心回転部材の第１軸線回りの回転に伴い第２伝動部材が、偏心回転部材の偏心軸部に対し第２軸線回りに自転しつつ主軸部に対し第１軸線回りに公転するときに、上記偏心回転系の遠心力が第１軸線から見て特定方向（即ち第２軸線のオフセット側）に偏って大きく作用して、その偏心回転系の回転がアンバランスな状態となり、これが装置の振動発生要因となる。そこでこの特許文献２のものでは、上記偏心回転系の総合重心とは逆位相の位置に在って偏心回転系の回転のアンバランス状態を軽減し得るるバランスウェイトを第１軸に配設しているが、そのバランスウェイトの重心位置と偏心回転系の総合重心位置とが軸方向に少なからずオフセットしているため、その両者の重心に作用する逆向きの遠心力に因り偶力が発生し、これが振動発生要因となる。   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 speed ratio to a specific ratio), and therefore, for example, the rotational force input to the case cannot be distributed to the first and second shafts. Further, in the transmission device of Patent Document 2, the position of the center of gravity of the eccentric rotation system including the eccentric shaft portion of the eccentric rotation member and the second transmission member is unevenly distributed at a position separated from the first axis in the direction of the second axis. When the second transmission member revolves around the first axis with respect to the main shaft portion while rotating around the second axis with respect to the eccentric shaft portion of the eccentric rotation member as the eccentric rotation member rotates about the first axis, The centrifugal force of the eccentric rotation system acts largely in a specific direction (that is, the offset side of the second axis) when viewed from the first axis, and the rotation of the eccentric rotation system becomes unbalanced, which is the vibration of the device. It becomes a generation factor. Therefore, in this Patent Document 2, a balance weight is provided on the first shaft that is in a phase opposite to the total center of gravity of the eccentric rotating system and can reduce the unbalanced state of rotation of the eccentric rotating system. However, since the center of gravity of the balance weight and the total center of gravity of the eccentric rotating system are offset in the axial direction, couples are generated due to the reverse centrifugal force acting on the center of gravity of both. This is a cause of vibration.

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、更に上記偶力の問題を解消しつつバランスウェイトを設置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, making it possible to effectively utilize this as a differential device while taking advantage of the above-mentioned advantage of the transmission device as disclosed in Patent Document 2, and further to solve the above-mentioned problem of couples. It is an object of the present invention to provide a differential device that can install a balance weight while eliminating the problem.

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、前記デフケースのハブに回転自在に嵌合支持した第１ドライブ軸に接続されて第１軸線回りに回転可能な中空の主軸部、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、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、その第２伝動部材に対向配置されると共に第２ドライブ軸に接続されて第１軸線回りに回転可能な第３伝動部材と、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２伝動部材は、前記主軸部の一端部が臨むウェイト収容空間を備えており、第１軸線を挟んで前記偏心軸部及び前記第２伝動部材の総合重心とは逆位相の重心を有して前記ウェイト収容空間に収容されるバランスウェイトが前記主軸部の前記一端部に、該一端部の開放端面がバランスウェイトで閉塞されるように設けられ、前記第１ドライブ軸は、前記主軸部の中空部において該主軸部にスプライン嵌合され、前記第１ドライブ軸と前記デフケースの前記ハブとの嵌合面の一方には、それらハブと第１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１変速機構の内周側に連通させる油路が、前記デフケースと前記偏心回転部材との間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 first transmission member that can be rotated around a first axis together with a differential case that is arranged in a mission case and receives rotational force, and is rotatably fitted and supported on a hub of the differential case. A hollow main shaft portion that is connected to the first drive shaft and is rotatable about the first axis, and an eccentric rotation member in which an eccentric shaft portion having a second axis that is eccentric from the first axis as a central axis is integrally coupled; A second transmission member disposed opposite to the first transmission member and rotatably supported by the eccentric shaft portion; a first axis line disposed opposite to the second transmission member and connected to the second drive shaft; A third transmission member rotatable around, a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members, and torque transmission while shifting between the second and third transmission members Second transmission mechanism The first and second speed change mechanisms are configured to drive the third transmission member from the first transmission member with a double speed increasing ratio when the eccentric rotating member is fixed. The second transmission member includes a weight accommodating space where one end portion of the main shaft portion faces, and has a phase opposite to the total center of gravity of the eccentric shaft portion and the second transmission member across the first axis. A balance weight having a center of gravity and housed in the weight housing space is provided at the one end portion of the main shaft portion so that an open end surface of the one end portion is closed by the balance weight, and the first drive shaft is The hollow portion of the main shaft portion is spline-fitted to the main shaft portion, and one of the fitting surfaces of the first drive shaft and the hub of the differential case has a relative rotation between the hub and the first drive shaft. Mission case Is provided with a spiral groove capable of drawing the lubricating oil from the outer end side to the inner end side of the hub, and an oil passage that communicates an outlet of the spiral groove with the inner peripheral side of the first transmission mechanism. The first feature is that it is provided between the eccentric rotating member.

また本発明は、第１の特徴に加えて、前記螺旋溝の出口から前記第１ドライブ軸と前記主軸部とのスプライン嵌合部に流入した潤滑油を前記第１変速機構の内周側に導く油孔が、前記偏心回転部材に設けられることを第２の特徴とする。   According to the present invention, in addition to the first feature, the lubricating oil that has flowed into the spline fitting portion between the first drive shaft and the main shaft portion from the outlet of the spiral groove is disposed on the inner peripheral side of the first transmission mechanism. A second feature is that the guiding oil hole is provided in the eccentric rotating member.

また本発明は、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、前記デフケースのハブに回転自在に嵌合支持した第１ドライブ軸に接続されて第１軸線回りに回転可能な中空の主軸部、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、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、その第２伝動部材に対向配置されると共に第２ドライブ軸に接続されて第１軸線回りに回転可能な第３伝動部材と、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２伝動部材は、前記主軸部の一端部が臨むウェイト収容空間を備えており、第１軸線を挟んで前記偏心軸部及び前記第２伝動部材の総合重心とは逆位相の重心を有して前記ウェイト収容空間に収容されるバランスウェイトが前記主軸部の前記一端部に、該一端部の開放端面がバランスウェイトで閉塞されるように設けられ、前記第１ドライブ軸は、前記主軸部の中空部において該主軸部にスプライン嵌合され、前記主軸部には、前記デフケースの前記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、前記筒軸の、前記ハブから外方に延出する外端部と、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３の特徴とする。   Further, the present invention is connected to a first transmission member that is disposed in a transmission case and is rotatable around a first axis together with a differential case that receives rotational force, and a first drive shaft that is rotatably fitted and supported on a hub of the differential case. An eccentric rotating member in which a hollow main shaft portion that is rotatable about the first axis, and an eccentric shaft portion having a second axis that is eccentric from the first axis as a central axis, and the first transmission member A second transmission member disposed oppositely and rotatably supported by the eccentric shaft portion; and a third transmission member disposed opposite the second transmission member and connected to the second drive shaft and rotatable about the first axis. A transmission member; 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 transmissions Is a differential device configured to drive the third transmission member from the first transmission member with a double speed increasing ratio when the eccentric rotating member is fixed, the second transmission member Is provided with a weight housing space facing one end of the main shaft portion, and has a center of gravity opposite to the total center of gravity of the eccentric shaft portion and the second transmission member across the first axis. A balance weight accommodated in the space is provided at the one end portion of the main shaft portion so that an open end surface of the one end portion is closed by the balance weight, and the first drive shaft is formed in the hollow portion of the main shaft portion. The main shaft portion is spline-fitted to the main shaft portion, and a cylindrical shaft that is rotatably fitted to and supported by the hub of the differential case is integrally connected to the main shaft portion, and the cylindrical shaft extends outward from the hub. The outer end to be put out and the mission Seal member to a third feature of being interposed between the over scan.

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 transmission mechanism is located on a surface of the first transmission member facing the second transmission member and has the first axis as the center. 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.

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中空の主軸部、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、第２伝動部材は、主軸部の一端部が臨むウェイト収容空間を備え、第１軸線を挟んで偏心軸部及び第２伝動部材の総合重心とは逆位相の重心を有してウェイト収容空間に収容されるバランスウェイトが主軸部の一端部に、該一端部の開放端面がバランスウェイトで閉塞されるように設けられるので、偏心回転系の上記総合重心とバランスウェイトの重心との軸方向オフセット量をゼロ又は僅少にできて、両重心に作用する遠心力に起因した偶力の発生、延いてはその偶力に因る振動発生を効果的に抑制可能となり、しかもバランスウェイトが主軸部内端部（上記一端部）の開放端面を塞ぐ蓋部材に兼用可能となって構造簡素化が図られる。更にデフケースのハブに回転自在に嵌合支持した第１ドライブ軸が、主軸部の中空部において該主軸部にスプライン嵌合され、第１ドライブ軸とデフケースハブ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１変速機構の内周側に連通させる油路が、デフケースと偏心回転部材との間に設けられるので、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遠心力の作用によりデフケースと偏心回転部材間で放射状に飛散させて第１変速機構側へ効率よく供給することができる。この場合、螺旋溝出口は、主軸部の中空部とも連通しているが、その主軸部一端部の開放端面がバランスウェイトで閉塞されるため、螺旋溝出口を出た潤滑油が主軸部の中空部を素通りすることなく第１変速機構側に効率よく供給可能である。   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 disposed in the transmission case and receives rotational force, and the hollow main shaft portion 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. Two transmission members, a third transmission member that is disposed opposite to the second transmission member and is rotatable about the first axis, and a first transmission mechanism that is capable of transmitting torque while shifting between the first and second transmission members. A second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members, and when the first and second transmission mechanisms fix the eccentric rotating member to the third transmission. It is configured to drive the member 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, the second transmission member includes a weight accommodating space facing one end of the main shaft portion, and has a center of gravity opposite in phase to the eccentric shaft portion and the total center of gravity of the second transmission member across the first axis. Since the balance weight housed in the housing space is provided at one end portion of the main shaft portion and the open end face of the one end portion is closed by the balance weight, the axis of the above-mentioned total center of gravity of the eccentric rotation system and the center of gravity of the balance weight The amount of direction offset can be reduced to zero or small, and it is possible to effectively suppress the generation of couples due to the centrifugal force acting on both centers of gravity, and hence the vibration caused by the couples. The structure can be simplified because it can also be used as a lid member that closes the open end surface of the inner end portion (the one end portion). Further, the first drive shaft that is rotatably fitted and supported on the hub of the differential case is spline-fitted to the main shaft portion in the hollow portion of the main shaft portion, and on one of the fitting surfaces of the first drive shaft and the differential case hub, 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 the relative rotation is provided, and the outlet of the spiral groove is communicated with the inner peripheral side of the first transmission mechanism. Since the oil passage is provided between the differential case and the eccentric rotating member, the lubricating oil is drawn from the transmission case side to the differential case side through the spiral groove, and then the lubricating oil is radially distributed between the differential case and the eccentric rotating member by the action of centrifugal force. Can be efficiently supplied to the first speed change mechanism side. In this case, the spiral groove outlet communicates with the hollow portion of the main shaft portion, but since the open end surface of one end portion of the main shaft portion is closed with a balance weight, the lubricating oil that has exited the spiral groove outlet is hollow in the main shaft portion. It can be efficiently supplied to the first speed change mechanism without passing through the section.

また特に第２の特徴によれば、螺旋溝の出口から第１ドライブ軸と主軸部とのスプライン嵌合部に流入した潤滑油を第１変速機構の内周側に導く油孔が、偏心回転部材に設けられるので、スプライン嵌合部（即ち主軸部の中空部）への流入潤滑油を上記油孔を通して第１変速機構の内周側に供給可能となり、第１変速機構をより効率よく潤滑することができる。   In particular, according to the second feature, the oil hole for guiding the lubricating oil flowing from the outlet of the spiral groove into the spline fitting portion between the first drive shaft and the main shaft portion to the inner peripheral side of the first transmission mechanism is eccentrically rotated. Since it is provided on the member, the lubricating oil flowing into the spline fitting portion (that is, the hollow portion of the main shaft portion) can be supplied to the inner peripheral side of the first transmission mechanism through the oil hole, and the first transmission mechanism can be lubricated more efficiently. can do.

また第３の特徴によれば、第１の特徴による前記効果と同様に、偏心回転系の総合重心とバランスウェイトの重心とに作用する遠心力に起因した偶力の発生、延いてはその偶力に因る振動発生を効果的に抑制可能となる。また、主軸部には、デフケースの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、筒軸の、ハブから外方に延出する外端部と、ミッションケースとの間にシール部材が介装され、しかもバランスウェイトが主軸部内端部の開放端面を塞ぐ蓋部材に兼用可能となっているので、第１ドライブ軸を主軸部（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。   Further, according to the third feature, similar to the effect by the first feature, generation of a couple due to the centrifugal force acting on the total center of gravity of the eccentric rotation system and the center of gravity of the balance weight, and further, Generation of vibration due to force can be effectively suppressed. In addition, a cylindrical shaft that is rotatably fitted to and supported by the hub of the differential case is integrally connected to the main shaft portion, and an outer end portion of the cylindrical shaft that extends outward from the hub, and a transmission case Since a seal member is interposed between them and the balance weight can also be used as a lid member that closes the open end surface of the inner end portion of the main shaft portion, even when the first drive shaft is pulled out from the main shaft portion (cylinder shaft), The external leakage of the lubricating oil in the transmission case and the differential case can be prevented, and the maintenance workability is improved.

また第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。   Further, according to the fourth feature, since the plurality of first and second rolling elements can be involved in transmission at the same time, the transmission torque is distributed in the circumferential direction of each transmission member on both sides of the rolling element, It is possible to provide a lightweight and highly durable differential device.

本発明の第１実施形態に係る差動装置の縦断正面図1 is a longitudinal front view of a differential gear according to a first embodiment of the present invention. 前記差動装置の要部（差動機構）の分解斜視図Exploded perspective view of the main part (differential mechanism) of the differential device 図１の３−３矢視断面図3-3 arrow sectional view of FIG. 図１の４−４矢視断面図4-4 cross-sectional view of FIG. 図１の５−５矢視断面図Sectional view along arrow 5-5 in FIG. 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Enlarged longitudinal sectional view showing the main part (differential mechanism) of the differential device together with the flow of lubricating oil 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）Longitudinal front view of the differential according to the second embodiment of the present invention (corresponding to FIG. 1)

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

先ず、図１〜図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 rotatably supported by the transmission case 1 around the first axis X1, and a differential mechanism 3 described later that is housed in the differential case C. The differential case C includes a ring gear Cg made of a helical gear having oblique teeth Cga provided on the outer periphery of a short cylindrical gear body, and a pair of left and right first and first pairs whose outer peripheral ends are joined to both axial ends of the ring gear Cg. 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 integrally including a cylindrical first spline boss SB1 rotatable around X1 and an eccentric shaft portion having a second axis line X2 eccentric from the first axis line X1 by a predetermined eccentric amount e as a central axis line An eccentric rotating member 6 in which 6e is coupled and integrated, and an annular member whose one side is opposed to the first transmission member 5 and rotatably supported by a bearing 7 comprising a ball bearing on the eccentric shaft portion 6e. An annular third transmission member which is disposed opposite to the second transmission member 8 and the other side of the second transmission member 8 and is spline-fitted 17 to the second drive axle S2 and rotatable about the first axis X1. 9 and the first and second transmission members 5, 8 It comprises a first transmission mechanism T1 phrase can be transmitted, and a second transmission mechanism that transmit the torque T2 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 integrally formed with a cylindrical second spline boss SB2 that is spline fitted 17 to the second drive axle S2 in the hollow portion of the third transmission member 9 and is rotatable about the first axis X1. The main shaft portion 9j included in the main shaft portion 9j 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。而して、第１油路Ｐ１は、螺旋溝としての第１螺旋溝１８の出口を第１変速機構Ｔ１の内周側に連通させる本発明の油路を構成する。   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. Thus, the first oil passage P1 constitutes the oil passage of the present invention in which the outlet of the first spiral groove 18 as a spiral groove communicates with the inner peripheral side of the first transmission mechanism T1.

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 (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 first transmission member 5 has a waveform centered on the first axis X <b> 1 on the inner surface facing the one side portion (first half 8 a) of the second transmission member 8. An annular first transmission groove 21 is formed, and the first transmission groove 21 extends in the circumferential direction along a hypotrochoid curve having a virtual circle centered on the first axis X1 in the illustrated example. On the other hand, a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side portion (first half 8a) of the second transmission member 8 facing the first transmission member 5. . In the illustrated example, the second transmission groove 22 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the second axis X2 as a base circle, and is smaller than the wave number of the first transmission groove 21. It has a wave number and intersects the first transmission groove 21 at a plurality of locations. A plurality of first rolling balls 23 as first rolling elements are interposed at intersections (that is, overlapping portions) of the first transmission groove 21 and the second transmission groove 22, and each first rolling groove is provided. The ball 23 can roll on the inner surfaces of the first and second transmission grooves 21 and 22.

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

また、図１，２，４に示すように、第２伝動部材８の他側部（第２半体８ｂ）には、第２軸線Ｘ２を中心とした波形環状の第３伝動溝２４が形成され、この第３伝動溝２４は、図示例では第２軸線Ｘ２を中心とする仮想円を基礎円としたハイポトロコイド曲線に沿って周方向に延びている。一方、第３伝動部材９の、第２伝動部材８との対向面すなわち円板部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 (second half 8 b) of the second transmission member 8. In the illustrated example, the third transmission groove 24 extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the second axis X2 as a base circle. On the other hand, on the surface of the third transmission member 9 facing the second transmission member 8, that is, on the inner 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
望ましくは、図示例のように、Ｚ１＝８、Ｚ２＝６、Ｚ３＝６、Ｚ４＝４とするか、又はＺ１＝６、Ｚ２＝４、Ｚ３＝８、Ｚ４＝６とするとよい。 In the present embodiment described above, the wave number of the first transmission groove 21 is Z1, the wave number of the second transmission groove 22 is Z2, the wave number of the third transmission groove 24 is Z3, and the wave number of the fourth transmission groove 25 is Z4. The first to fourth transmission grooves 21, 22, 24, and 25 are formed so that the following expression is established.
(Z1 / Z2) × (Z3 / Z4) = 2
Desirably, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, and Z4 = 6 as shown in the illustrated example.

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

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

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 torque transmission process of the differential device D, as described above, the stored lubricating oil at the bottom of the mission case 1 is stirred by the differential case C or the like and scattered in the mission case 1 over a wide range. 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.

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変速機構Ｔ１、軸受７、スラストワッシャＴＨ１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, sliding portions such as the first transmission mechanism T1, the bearing 7, and the thrust washer TH1 are effectively lubricated inside 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、その第２伝動部材８に対向配置されて第１軸線Ｘ１回りに回転可能な扁平な第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 that is disposed opposite to the second transmission member 8 and can rotate about the first axis X1 and a first that can transmit torque while shifting between the first and second transmission members 5 and 8. When a transmission mechanism T1 and a second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 8 and 9 are provided, and 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. To be configured in a differential device D which are readily flattened compact in the axial direction is obtained.

その上、第２伝動部材８は、主軸部６ｊの内端部６ｊａが臨むウェイト収容空間としての中空部ＳＰを備え、第１軸線Ｘ１を挟んで偏心軸部６ｅ及び第２伝動部材８の総合重心Ｇとは逆位相の重心を有して中空部ＳＰに収容されるバランスウェイトＷが主軸部６ｊの内端部６ｊａに、該内端部の開放端面がバランスウェイトＷで閉塞されるように設けられるため、偏心回転系の上記総合重心ＧとバランスウェイトＷの重心との軸方向オフセット量をゼロ又は僅少にできて、両重心に作用する遠心力に起因した偶力の発生、延いてはその偶力に因る振動発生を効果的に抑制可能となり、しかもバランスウェイトＷが主軸部６ｊの内端側の開口部を塞ぐ蓋部材に兼用可能となって構造簡素化が図られる。   In addition, the second transmission member 8 includes a hollow portion SP as a weight accommodating space where the inner end portion 6ja of the main shaft portion 6j faces, and the eccentric shaft portion 6e and the second transmission member 8 are integrated with the first axis X1 interposed therebetween. The balance weight W having a center of gravity opposite to the center of gravity G and accommodated in the hollow portion SP is closed by the inner end portion 6ja of the main shaft portion 6j, and the open end surface of the inner end portion is closed by the balance weight W. Therefore, the amount of axial offset between the total center of gravity G of the eccentric rotation system and the center of gravity of the balance weight W can be reduced to zero or very small. Generation of vibration due to the couple can be effectively suppressed, and the balance weight W can also be used as a lid member that closes the opening on the inner end side of the main shaft portion 6j, thereby simplifying the structure.

更に第１駆動車軸Ｓ１とデフケースＣの第１ハブＨＢ１との嵌合面の一方に、その相互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螺旋溝１８が設けられると共に、この螺旋溝１８の出口を第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ので、螺旋溝１８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み、次いでその潤滑油を遠心力の作用によりデフケースＣと偏心回転部材６間（第１油路Ｐ１）で放射状に飛散させて第１変速機構Ｔ１側へ効率よく供給可能である。この場合、螺旋溝１８の出口は、主軸部６ｊの中空部とも連通しているが、その主軸部６ｊの内端部６ｊａの開放端面がバランスウェイトＷで閉塞されるため、螺旋溝１８の出口を出た潤滑油が主軸部６ｊの中空部を素通りすることなく第１変速機構Ｔ１側に効率よく供給可能となる。   Furthermore, the lubricating oil in the transmission case 1 is transferred from the outer end side to the inner end side of the first hub HB1 on one of the fitting surfaces of the first drive axle S1 and the first hub HB1 of the differential case C by their relative rotation. A retractable spiral groove 18 is provided, and a first oil passage P1 that communicates the outlet of the spiral groove 18 with the inner peripheral side of the first transmission mechanism T1 is provided between the differential case C and the eccentric rotating member 6. Therefore, the lubricating oil is drawn from the mission case 1 side to the differential case C side through the spiral groove 18, and then the lubricating oil is scattered radially between the differential case C and the eccentric rotating member 6 (first oil passage P1) by the action of centrifugal force. Thus, it can be efficiently supplied to the first transmission mechanism T1 side. In this case, the outlet of the spiral groove 18 communicates with the hollow portion of the main shaft portion 6j. However, the open end surface of the inner end portion 6ja of the main shaft portion 6j is closed by the balance weight W. The lubricating oil that has exited can be efficiently supplied to the first transmission mechanism T1 without passing through the hollow portion of the main shaft portion 6j.

その上、螺旋溝１８の出口から第１駆動車軸Ｓ１と主軸部６ｊ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の内周側に導く油孔４５を偏心回転部材６が有するので、スプライン嵌合部１６（即ち主軸部６ｊの中空部）への流入潤滑油を油孔４５を通して第１変速機構Ｔ１の内周側に供給可能となり、第１変速機構Ｔ１をより効率よく潤滑できる。   In addition, the eccentric rotation member 6 has an oil hole 45 that guides the lubricating oil flowing from the outlet of the spiral groove 18 into the spline fitting portion 16 between the first drive axle S1 and the main shaft portion 6j to the inner peripheral side of the first transmission mechanism T1. Therefore, the lubricating oil flowing into the spline fitting portion 16 (that is, the hollow portion of the main shaft portion 6j) can be supplied to the inner peripheral side of the first transmission mechanism T1 through the oil hole 45, and the first transmission mechanism T1 is made more efficient. Can be well lubricated.

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。尚、第１，第２螺旋溝１８，１９及び第１油路Ｐ１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. Is provided with a second spiral groove 19 capable of drawing the lubricating oil from the outer end side to the inner end side of the second hub HB2. The configurations of the first and second spiral grooves 18 and 19 and the first oil passage P1 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。更に第３伝動部材９の中空の主軸部９ｊ（即ち第２スプラインボスＳＢ２）には、これの内端側（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。   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. Further, the hollow main shaft portion 9j (that is, the second spline boss SB2) of the third transmission member 9 is integrally provided with a closing wall 44 that closes the opening portion on the inner end side (the side opposite to the second drive axle S2). Formed. 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。   Since the other configuration is the same as that of the first embodiment, 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, an effect equivalent to the above-described effect of the first embodiment can be achieved.

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。   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, the passage of the lubricating oil reaching the outlets of the first and second spiral grooves 18 and 19 in both the main shaft portions 6j and 9j is eliminated.

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

例えば、前記実施形態では、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, but the differential device D is not limited to the differential apparatus for automobiles, 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変速機構または第２変速機構の一方また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 are both configured using a rolling ball type transmission mechanism, 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 reduction gear (speed increaser) of various structures, or a trochoid reduction gear (speed increase gear) to one or both of a 1st transmission mechanism or a 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間にボール状の第１及び第２転動体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。   In the above-described embodiment, the first and second ball-shaped first and second transmission grooves 21 and 22 and the third and fourth transmission grooves 24 and 25 of the first and second transmission mechanisms T1 and T2 are provided. Although two rolling elements 23 and 26 are interposed, the rolling elements may be in the form of a roller or a pin. In this case, the first and second transmission grooves 21 and 22, and the third and fourth The transmission grooves 24 and 25 are formed in an inner surface shape so that a roller-like or pin-like rolling element can roll.

また前記実施形態では、第１，第２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、第１，第２保持部材Ｈ１，Ｈ２無しでも第１，第２伝動ボール２３，２６が円滑に転動可能である場合には、第１，第２保持部材Ｈ１，Ｈ２を省略してもよい。   If the first and second transmission balls 23 and 26 can smoothly roll without the first and second holding members H1 and H2, the first and second holding members H1 and H2 are omitted. Also good.

Ｃ・・・・・・デフケース
Ｄ・・・・・・差動装置
ＨＢ１・・・・ハブとしての第１ハブ
Ｐ１・・・・・油路としての第１油路
Ｓ１，Ｓ２・・第１，第２ドライブ軸としての第１，第２駆動車軸
ＳＰ・・・・・ウェイト収容空間としての中空部
Ｔ１，Ｔ２・・第１，第２変速機構
Ｗ・・・・・・バランスウェイト
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
６ｊ・・・・・主軸部
６ｊａ・・・・一端部としての内端部
６ｅ・・・・・偏心軸部
１６・・・・・スプライン嵌合
１８・・・・・螺旋溝としての第１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
４１・・・・・筒軸としての第１筒軸
４５・・・・・油孔 C ... Differential case D ... Differential gear HB1 ... First hub P1 as a hub ... First oil passages S1, S2 as an oil passage First , First and second drive axles SP as the second drive shaft ... hollow portions T1, T2 as the weight accommodating space, first and second transmission mechanisms W, balance weight X1, X2 ··· First and second axis 1 ··· Mission case 4 ······ Seal members 5, 8, 9 ··· First, second and third transmission members 6 ··· · Eccentric rotating member 6j ··· Main shaft portion 6ja ··· Inner end portion 6e as one end portion ··· Eccentric shaft portion 16 ··· Spline fitting 18 ··· Spiral groove First spiral grooves 21, 22... First and second transmission grooves 23... First rolling balls 24, 25. Transmission groove 26 ..... first cylindrical shaft 45 of the second rolling ball 41 ----- cylinder axis of the second rolling element ----- oil hole

Claims (4)

ミッションケース（１）内に配置されて回転力を受けるデフケース（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、
前記デフケース（Ｃ）のハブ（ＨＢ１）に回転自在に嵌合支持した第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）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、
その第２伝動部材（８）に対向配置されると共に第２ドライブ軸（Ｓ２）に接続されて第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２伝動部材（８）は、前記主軸部（６ｊ）の一端部が臨むウェイト収容空間（ＳＰ）を備えており、
第１軸線（Ｘ１）を挟んで前記偏心軸部（６ｅ）及び前記第２伝動部材（８）の総合重心（Ｇ）とは逆位相の重心を有して前記ウェイト収容空間（ＳＰ）に収容されるバランスウェイト（Ｗ）が前記主軸部（６ｊ）の前記一端部（６ｊａ）に、該一端部（６ｊａ）の開放端面がバランスウェイト（Ｗ）で閉塞されるように設けられ、
前記第１ドライブ軸（Ｓ１）は、前記主軸部（６ｊ）の中空部において該主軸部（６ｊ）にスプライン嵌合（１６）され、
前記第１ドライブ軸（Ｓ１）と前記デフケース（Ｃ）の前記ハブ（ＨＢ１）との嵌合面の一方には、それらハブ（ＨＢ１）と第１ドライブ軸（Ｓ１）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（ＨＢ１）の外端側から内端側に引き込み可能な螺旋溝（１８）が設けられると共に、この螺旋溝（１８）の出口を前記第１変速機構（Ｔ１）の内周側に連通させる油路（Ｐ１）が、前記デフケース（Ｃ）と前記偏心回転部材（６）との間に設けられることを特徴とする差動装置。 A first transmission member (5) disposed in the mission case (1) and capable of rotating about a first axis (X1) together with a differential case (C) that receives rotational force;
A hollow main shaft portion (6j) connected to the first drive shaft (S1) rotatably fitted and supported on the hub (HB1) of the differential case (C) and rotatable about the first axis (X1), and the first An eccentric rotating member (6) integrally connected with an eccentric shaft portion (6e) having a second axis (X2) eccentric from the first axis (X1) 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 third transmission member (9) disposed opposite to the second transmission member (8) and connected to the second drive shaft (S2) and rotatable about the 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 second transmission member (8) includes a weight accommodating space (SP) facing one end of the main shaft portion (6j),
The eccentric shaft portion (6e) and the second transmission member (8) have a center of gravity opposite to the total center of gravity (G) across the first axis (X1) and are accommodated in the weight accommodation space (SP). The balance weight (W) is provided at the one end (6ja) of the main shaft (6j) so that the open end face of the one end (6ja) is closed by the balance weight (W),
The first drive shaft (S1) is spline-fitted (16) to the main shaft portion (6j) in the hollow portion of the main shaft portion (6j),
One of the fitting surfaces of the first drive shaft (S1) and the differential case (C) with the hub (HB1) has a relative rotation between the hub (HB1) and the first drive shaft (S1). A spiral groove (18) capable of drawing the lubricating oil in the case (1) from the outer end side to the inner end side of the hub (HB1) is provided, and the outlet of the spiral groove (18) is connected to the first transmission mechanism. An oil passage (P1) communicating with the inner peripheral side of (T1) is provided between the differential case (C) and the eccentric rotating member (6). 前記螺旋溝（１８）の出口から前記第１ドライブ軸（Ｓ１）と前記主軸部（６ｊ）とのスプライン嵌合部（１６）に流入した潤滑油を前記第１変速機構（Ｔ１）の内周側に導く油孔（４５）が、前記偏心回転部材（６）に設けられることを特徴とする、請求項１に記載の差動装置。   Lubricating oil that has flowed into the spline fitting portion (16) between the first drive shaft (S1) and the main shaft portion (6j) from the outlet of the spiral groove (18) is the inner periphery of the first transmission mechanism (T1). The differential device according to claim 1, characterized in that an oil hole (45) leading to the side is provided in the eccentric rotating member (6). ミッションケース（１）内に配置されて回転力を受けるデフケース（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、
前記デフケース（Ｃ）のハブ（ＨＢ１）に回転自在に嵌合支持した第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）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、
その第２伝動部材（８）に対向配置されると共に第２ドライブ軸（Ｓ２）に接続されて第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２伝動部材（８）は、前記主軸部（６ｊ）の一端部（６ｊａ）が臨むウェイト収容空間（ＳＰ）を備えており、
第１軸線（Ｘ１）を挟んで前記偏心軸部（６ｅ）及び前記第２伝動部材（８）の総合重心（Ｇ）とは逆位相の重心を有して前記ウェイト収容空間（ＳＰ）に収容されるバランスウェイト（Ｗ）が前記主軸部（６ｊ）の前記一端部（６ｊａ）に、該一端部（６ｊａ）の開放端面がバランスウェイト（Ｗ）で閉塞されるように設けられ、
前記第１ドライブ軸（Ｓ１）は、前記主軸部（６ｊ）の中空部において該主軸部（６ｊ）にスプライン嵌合（１６）され、
前記主軸部（６ｊ）には、前記デフケース（Ｃ）の前記ハブ（ＨＢ１）に回転自在に嵌合支持される筒軸（４１）が一体的に連設され、
前記筒軸（４１）の、前記ハブ（ＨＢ１）から外方に延出する外端部（４１ａ）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差動装置。 A first transmission member (5) disposed in the mission case (1) and capable of rotating about a first axis (X1) together with a differential case (C) that receives rotational force;
A hollow main shaft portion (6j) connected to the first drive shaft (S1) rotatably fitted and supported on the hub (HB1) of the differential case (C) and rotatable about the first axis (X1), and the first An eccentric rotating member (6) integrally connected with an eccentric shaft portion (6e) having a second axis (X2) eccentric from the first axis (X1) 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 third transmission member (9) disposed opposite to the second transmission member (8) and connected to the second drive shaft (S2) and rotatable about the 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 second transmission member (8) includes a weight accommodating space (SP) facing one end portion (6ja) of the main shaft portion (6j),
The eccentric shaft portion (6e) and the second transmission member (8) have a center of gravity opposite to the total center of gravity (G) across the first axis (X1) and are accommodated in the weight accommodation space (SP). The balance weight (W) is provided at the one end (6ja) of the main shaft (6j) so that the open end face of the one end (6ja) is closed by the balance weight (W),
The first drive shaft (S1) is spline-fitted (16) to the main shaft portion (6j) in the hollow portion of the main shaft portion (6j),
A cylindrical shaft (41) that is rotatably fitted and supported by the hub (HB1) of the differential case (C) is integrally connected to the main shaft portion (6j),
A seal member (4) is interposed between the outer end (41a) of the cylindrical shaft (41) extending outward from the hub (HB1) and the transmission case (1). Features a differential. 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 claim 1, wherein: is established.
JP2015252330A 2015-12-24 2015-12-24 Differential device Pending JP2017115993A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020180656A (en) * 2019-04-25 2020-11-05 トヨタ自動車株式会社 Differential device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020180656A (en) * 2019-04-25 2020-11-05 トヨタ自動車株式会社 Differential device
JP7135992B2 (en) 2019-04-25 2022-09-13 トヨタ自動車株式会社 Differential device

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