JP6157425B2

JP6157425B2 - Continuously variable transmission

Info

Publication number: JP6157425B2
Application number: JP2014162098A
Authority: JP
Inventors: 優史西村
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2014-08-08
Filing date: 2014-08-08
Publication date: 2017-07-05
Anticipated expiration: 2034-08-08
Also published as: JP2016038035A; CN105370829A

Description

本発明は、入力軸により偏心回転する複数の偏心ディスクに接続されて往復運動するコネクティングロッドで複数の揺動部材を往復揺動させ、揺動部材の往復揺動をワンウェイクラッチを介して出力軸の連続回転に変換するとともに、複数の偏心ディスクの偏心量を変化させて揺動部材の往復揺動角を変化させることで変速比を無段階に増減する無段変速機に関する。 According to the present invention, a plurality of rocking members are reciprocally swung by a connecting rod that is reciprocated and connected to a plurality of eccentric disks that are eccentrically rotated by an input shaft, and the reciprocating rocking of the rocking members is performed via a one-way clutch. The present invention relates to a continuously variable transmission that continuously increases and decreases the gear ratio by changing the amount of eccentricity of a plurality of eccentric disks and changing the reciprocating swing angle of the swing member.

かかる無段変速機の一例が、下記特許文献１により公知である。この無段変速機は、相互に平行に配置されて入力軸と一体に回転する第１クランク部材および第２クランク部材を備えており、第１クランク部材および第２クランク部材にそれぞれ設けた第１ピン部および第２ピン部に、偏心ディスクに設けた第１ピン部嵌合孔および第２ピン部嵌合孔を支持し、第１クランク部材および第２クランク部材を入力軸に対して相対回転させることで入力軸線に対する偏心ディスクの偏心量を変化させるようになっている。 An example of such a continuously variable transmission is known from Patent Document 1 below. The continuously variable transmission includes a first crank member and a second crank member that are arranged in parallel to each other and rotate integrally with an input shaft, and the first crank member and the second crank member are provided respectively. The pin portion and the second pin portion support the first pin portion fitting hole and the second pin portion fitting hole provided in the eccentric disk, and the first crank member and the second crank member are rotated relative to the input shaft. By doing so, the amount of eccentricity of the eccentric disk with respect to the input axis is changed.

特許第５１４２２３４号公報Japanese Patent No. 5142234

ところで、上記従来の無段変速機は、偏心ディスクに接続されたコネクティングロッドが一方向に移動して揺動部材を駆動するときにワンウェイクラッチが係合して出力軸に駆動力を伝達するが、コネクティングロッドが伝達する駆動力の反力が偏心ディスクを介して第１、第２クランク部材に加わるため、第１、第２クランク部材に撓みが発生する可能性がある。第１、第２クランク部材に撓みが発生すると第１、第２ピン部が傾くため、その第１、第２ピン部と偏心ディスクの第１、第２ピン部嵌合孔との摺動部の摩擦損失や、偏心ディスクにコネクティングロッドを支持するベアリングの摩擦損失が増加する問題がある。 By the way, in the conventional continuously variable transmission, when the connecting rod connected to the eccentric disk moves in one direction to drive the swinging member, the one-way clutch is engaged and the driving force is transmitted to the output shaft. Since the reaction force of the driving force transmitted by the connecting rod is applied to the first and second crank members via the eccentric disk, the first and second crank members may bend. When the first and second crank members are bent, the first and second pin portions are tilted. Therefore, the sliding portion between the first and second pin portions and the first and second pin portion fitting holes of the eccentric disk. There is a problem that the friction loss of the bearing supporting the connecting rod on the eccentric disk increases.

本発明は前述の事情に鑑みてなされたもので、無段変速機の偏心ディスクを偏心量調整可能に支持する第１、第２クランク部材の撓みを抑制することを目的とする。 The present invention has been made in view of the above circumstances, and an object thereof is to suppress the bending of the first and second crank members that support the eccentric disk of the continuously variable transmission so that the eccentric amount can be adjusted.

上記目的を達成するために、請求項１に記載された発明によれば、入力軸線上に配置されて駆動源の駆動力が入力される入力軸と、出力軸線上に配置されて前記入力軸の駆動力が変速されて伝達される出力軸と、前記入力軸と一体に回転する第１クランク部材と、前記入力軸と一体に回転する第２クランク部材と、前記第１、第２クランク部材に支持されて前記入力軸線に対する偏心量が可変である複数の偏心ディスクと、前記出力軸の外周に揺動自在に支持された複数の揺動部材と、前記出力軸および前記複数の揺動部材間に配置された複数のワンウェイクラッチと、前記複数の偏心ディスクおよび前記複数の揺動部材を接続する複数のコネクティングロッドとを備え、前記第１クランク部材は、前記入力軸線に対して偏心する第１軸線上に配置された複数の第１ジャーナル部と、前記複数の第１ジャーナル部に対して偏心する複数の第１ピン部とを備え、前記第２クランク部材は、前記入力軸線に対して偏心する第２軸線上に配置された複数の第２ジャーナル部と、前記複数の第２ジャーナル部に対して偏心する複数の第２ピン部とを備え、前記複数の偏心ディスクは、前記第１ピン部が回転自在に嵌合する第１ピン部嵌合孔と、前記第２ピン部が回転自在に嵌合する第２ピン部嵌合孔とを備え、前記入力軸に対して前記第１、第２クランク部材を相対回転させることで、前記複数の偏心ディスクの偏心量をゼロおよび所定値間で変化させる無段変速機であって、前記第１クランク部材の前記第１ジャーナル部および前記第２クランク部材の前記第２ジャーナル部を支持する複数のジャーナル支持部材を備え、前記複数のジャーナル支持部材は前記複数の偏心ディスクの軸方向端面および前記複数の第１、第２ピン部の軸方向端面の少なくとも一方に相対回転自在に当接し、前記複数の偏心ディスクの軸方向厚さは前記第１、第２ピン部の軸方向厚さよりも大きく、前記複数のジャーナル支持部材は前記複数の偏心ディスクの軸方向端面に相対回転自在に当接することを特徴とする無段変速機が提案される。 In order to achieve the above object, according to the first aspect of the present invention, an input shaft that is disposed on the input axis and receives the driving force of the drive source, and an input shaft that is disposed on the output axis. An output shaft to which the driving force of the gear is transmitted and transmitted, a first crank member that rotates integrally with the input shaft, a second crank member that rotates integrally with the input shaft, and the first and second crank members A plurality of eccentric discs that are variable in eccentricity with respect to the input axis, a plurality of swing members that are swingably supported on the outer periphery of the output shaft, the output shaft, and the plurality of swing members A plurality of one-way clutches disposed therebetween, and a plurality of connecting rods connecting the plurality of eccentric disks and the plurality of swinging members, wherein the first crank member is eccentric with respect to the input axis. On one axis A plurality of first journal portions arranged; and a plurality of first pin portions that are eccentric with respect to the plurality of first journal portions; and the second crank member is a second eccentric with respect to the input axis. A plurality of second journal portions arranged on an axis; and a plurality of second pin portions that are eccentric with respect to the plurality of second journal portions, wherein the first pin portion of the plurality of eccentric disks rotates. A first pin portion fitting hole that fits freely, and a second pin portion fitting hole that fits the second pin portion rotatably, and the first and second cranks with respect to the input shaft. A continuously variable transmission that changes the eccentric amount of the plurality of eccentric disks between zero and a predetermined value by relatively rotating the members, wherein the first journal portion and the second crank member of the first crank member Of the second journal part Of comprising a journal support member, said plurality of journal support member is abutted relatively rotatably on at least one axial end face of the first, second pin portion axial end surface and of said plurality of said plurality of eccentric disks, The axial thicknesses of the plurality of eccentric disks are larger than the axial thicknesses of the first and second pin portions, and the plurality of journal support members abut against the axial end surfaces of the plurality of eccentric disks in a relatively rotatable manner. A continuously variable transmission is proposed.

また請求項２に記載された発明によれば、入力軸線上に配置されて駆動源の駆動力が入力される入力軸と、出力軸線上に配置されて前記入力軸の駆動力が変速されて伝達される出力軸と、前記入力軸と一体に回転する第１クランク部材と、前記入力軸と一体に回転する第２クランク部材と、前記第１、第２クランク部材に支持されて前記入力軸線に対する偏心量が可変である複数の偏心ディスクと、前記出力軸の外周に揺動自在に支持された複数の揺動部材と、前記出力軸および前記複数の揺動部材間に配置された複数のワンウェイクラッチと、前記複数の偏心ディスクおよび前記複数の揺動部材を接続する複数のコネクティングロッドとを備え、前記第１クランク部材は、前記入力軸線に対して偏心する第１軸線上に配置された複数の第１ジャーナル部と、前記複数の第１ジャーナル部に対して偏心する複数の第１ピン部とを備え、前記第２クランク部材は、前記入力軸線に対して偏心する第２軸線上に配置された複数の第２ジャーナル部と、前記複数の第２ジャーナル部に対して偏心する複数の第２ピン部とを備え、前記複数の偏心ディスクは、前記第１ピン部が回転自在に嵌合する第１ピン部嵌合孔と、前記第２ピン部が回転自在に嵌合する第２ピン部嵌合孔とを備え、前記入力軸に対して前記第１、第２クランク部材を相対回転させることで、前記複数の偏心ディスクの偏心量をゼロおよび所定値間で変化させる無段変速機であって、前記第１クランク部材の前記第１ジャーナル部および前記第２クランク部材の前記第２ジャーナル部を支持する複数のジャーナル支持部材を備え、前記複数のジャーナル支持部材は前記複数の偏心ディスクの軸方向端面および前記複数の第１、第２ピン部の軸方向端面の少なくとも一方に相対回転自在に当接し、前記複数の偏心ディスクの外径は前記複数のジャーナル支持部材の外径に略一致することを特徴とする無段変速機が提案される。 According to the second aspect of the present invention, the input shaft arranged on the input axis and to which the driving force of the driving source is inputted, and arranged on the output axis and the driving force of the input shaft are shifted. The output shaft to be transmitted, the first crank member that rotates integrally with the input shaft, the second crank member that rotates integrally with the input shaft, and the input axis supported by the first and second crank members A plurality of eccentric discs whose amount of eccentricity is variable, a plurality of swinging members swingably supported on the outer periphery of the output shaft, and a plurality of members disposed between the output shaft and the plurality of swinging members A one-way clutch; and a plurality of connecting rods connecting the plurality of eccentric disks and the plurality of swinging members, wherein the first crank member is disposed on a first axis that is eccentric with respect to the input axis. Multiple first A plurality of first pin portions that are eccentric with respect to the plurality of first journal portions, and the second crank member is disposed on a second axis that is eccentric with respect to the input axis. The second journal portion and a plurality of second pin portions that are eccentric with respect to the plurality of second journal portions, wherein the first pin portion is rotatably fitted to the plurality of eccentric discs. A pin portion fitting hole and a second pin portion fitting hole into which the second pin portion is rotatably fitted; and by rotating the first and second crank members relative to the input shaft. A continuously variable transmission for changing the amount of eccentricity of the plurality of eccentric disks between zero and a predetermined value, wherein the first journal portion of the first crank member and the second journal portion of the second crank member are Multiple journal support members to support Wherein the plurality of journal support member axial end surface and the plurality of first of the plurality of eccentric disks, relatively rotatably contact with at least one of the axial end surface of the second pin portion, of the plurality of eccentric disks A continuously variable transmission is proposed in which the outer diameter substantially matches the outer diameter of the plurality of journal support members.

また請求項３に記載された発明によれば、請求項１の構成に加えて、前記複数の偏心ディスクの外径は前記複数のジャーナル支持部材の外径に略一致することを特徴とする無段変速機が提案される。According to the invention described in claim 3, in addition to the configuration of claim 1, the outer diameters of the plurality of eccentric disks substantially coincide with the outer diameters of the plurality of journal support members. A step transmission is proposed.

また請求項４に記載された発明によれば、請求項１〜請求項３の何れか１項の構成に加えて、前記複数のジャーナル支持部材は、前記入力軸線の軸方向両端部に位置する第１端部ジャーナル支持部材および第２端部ジャーナル支持部材と、前記入力軸線の軸方向中間部に位置する中間ジャーナル支持部材とからなり、前記第１、第２端部ジャーナル支持部材は変速機ケースに支持され、前記中間ジャーナル支持部材は前記変速機ケースに支持されないことを特徴とする無段変速機が提案される。According to the invention described in claim 4, in addition to the configuration of any one of claims 1 to 3, the plurality of journal support members are located at both axial ends of the input axis. The first and second end journal support members include a first end journal support member and a second end journal support member, and an intermediate journal support member positioned at an intermediate portion in the axial direction of the input axis, wherein the first and second end journal support members are transmissions. A continuously variable transmission is proposed in which the intermediate journal support member is supported by a case and is not supported by the transmission case.

尚、実施の形態の第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２は本発明のジャーナル支持部材に対応し、実施の形態の第１端部ジャーナル支持部材１２は本発明の入力軸に対応し、実施の形態のエンジンＥは本発明の駆動源に対応する。 The first end journal support member 12, the second end journal support member 13, and the intermediate journal support member 22 of the embodiment correspond to the journal support member of the present invention, and the first end journal support of the embodiment. The member 12 corresponds to the input shaft of the present invention, and the engine E of the embodiment corresponds to the drive source of the present invention.

請求項１の構成によれば、駆動源に接続された入力軸と一体に第１、第２クランク部材が回転すると、第１、第２クランク部材に支持された複数の偏心ディスクが入力軸線回りに偏心回転し、コネクティングロッドが往復運動して揺動部材が往復揺動することで、複数のワンウェイクラッチが間欠的に係合して出力軸が連続回転する。入力軸線に対する偏心ディスクの偏心量を変化させると、コネクティングロッドの往復運動のストロークおよび揺動部材の往復揺動のストロークが変化し、出力軸の１回の間欠回転角が変化することで変速比が無段階に増減する。 According to the configuration of the first aspect, when the first and second crank members rotate integrally with the input shaft connected to the drive source, the plurality of eccentric disks supported by the first and second crank members are rotated around the input axis. When the connecting rod reciprocates and the swinging member swings back and forth, the plurality of one-way clutches are intermittently engaged and the output shaft rotates continuously. When the eccentric amount of the eccentric disk with respect to the input axis is changed, the reciprocating stroke of the connecting rod and the reciprocating stroke of the swing member are changed, and the one-time intermittent rotation angle of the output shaft is changed to change the gear ratio. Increases or decreases steplessly.

第１クランク部材は、入力軸線に対して偏心する第１軸線上に配置された複数の第１ジャーナル部と、複数の第１ジャーナル部に対して偏心する複数の第１ピン部とを備え、第２クランク部材は、入力軸線に対して偏心する第２軸線上に配置された複数の第２ジャーナル部と、複数の第２ジャーナル部に対して偏心する複数の第２ピン部とを備え、複数の偏心ディスクは、第１ピン部が回転自在に嵌合する第１ピン部嵌合孔と第２ピン部が回転自在に嵌合する第２ピン部嵌合孔とを備えるので、入力軸に対して第１、第２クランク部材を相対回転させることで、複数の偏心ディスクの偏心量をゼロおよび所定値間で無段階に変化させることができる。 The first crank member includes a plurality of first journal portions disposed on a first axis that is eccentric with respect to the input axis, and a plurality of first pin portions that are eccentric with respect to the plurality of first journal portions, The second crank member includes a plurality of second journal portions disposed on a second axis that is eccentric with respect to the input axis, and a plurality of second pin portions that are eccentric with respect to the plurality of second journal portions, Since the plurality of eccentric disks include a first pin portion fitting hole in which the first pin portion is rotatably fitted and a second pin portion fitting hole in which the second pin portion is rotatably fitted, the input shaft On the other hand, by rotating the first and second crank members relative to each other, the amount of eccentricity of the plurality of eccentric disks can be changed steplessly between zero and a predetermined value.

第１クランク部材の第１ジャーナル部および第２クランク部材の第２ジャーナル部を支持する複数のジャーナル支持部材を備え、複数のジャーナル支持部材は複数の偏心ディスクの軸方向端面および第１、第２クランク部材の複数の第１、第２ピン部の軸方向端面の少なくとも一方に相対回転自在に当接するので、コネクティングロッドから伝達される駆動反力で第１、第２クランク部材が撓もうとしたとき、ジャーナル支持部材が第１、第２ピン部の傾きを防止することで第１、第２クランク部材の撓みが直接的に抑制され、あるいはジャーナル支持部材が偏心ディスクの傾きを抑制することで第１、第２クランク部材の撓みが間接的に抑制される。 A plurality of journal support members for supporting the first journal portion of the first crank member and the second journal portion of the second crank member, wherein the plurality of journal support members are axial end surfaces of the plurality of eccentric discs and the first and second journals; Since the first and second crank members are in contact with at least one of the axial end surfaces of the plurality of first and second pin portions so as to be relatively rotatable, the first and second crank members try to bend by the driving reaction force transmitted from the connecting rod. When the journal support member prevents the first and second pin portions from tilting, the deflection of the first and second crank members is directly suppressed, or the journal support member suppresses the tilt of the eccentric disk. The bending of the first and second crank members is indirectly suppressed.

また、複数の偏心ディスクの軸方向厚さは第１、第２ピン部の軸方向厚さよりも大きく、複数のジャーナル支持部材は複数の偏心ディスクの軸方向端面に相対回転自在に当接するので、当接部の面積を最小限に抑えて摩擦損失を低減しながら、第１軸線および第２軸線からできるだけ離れた位置でジャーナル支持部材に偏心ディスクを当接させることで第１、第２クランク部材の撓み防止効果を有効に発揮させることができる。Further, the axial thickness of the plurality of eccentric disks is larger than the axial thickness of the first and second pin portions, and the plurality of journal support members abut against the axial end faces of the plurality of eccentric disks in a relatively rotatable manner. The first and second crank members are brought into contact with the journal support member at a position as far as possible from the first axis and the second axis while reducing the friction loss by minimizing the area of the abutting portion. It is possible to effectively exhibit the effect of preventing bending.

また請求項２，３の構成によれば、複数の偏心ディスクの外径は複数のジャーナル支持部材の外径に略一致するので、第１、第２クランク部材の撓み防止効果を充分に発揮させながら、ジャーナル支持部材の外径を最小限に抑えて重量を削減することができる。According to the second and third aspects of the present invention, the outer diameters of the plurality of eccentric disks substantially coincide with the outer diameters of the plurality of journal support members, so that the first and second crank members can be sufficiently prevented from being bent. However, it is possible to reduce the weight by minimizing the outer diameter of the journal support member.

また請求項４の構成によれば、複数のジャーナル支持部材は、入力軸線の軸方向両端部に位置する第１端部ジャーナル支持部材および第２端部ジャーナル支持部材と、入力軸線の軸方向中間部に位置する中間ジャーナル支持部材とからなり、第１、第２端部ジャーナル支持部材は変速機ケースに支持され、中間ジャーナル支持部材は変速機ケースに支持されないので、第１、第２端部ジャーナル支持部材で第１、第２クランク部材を変速機ケースに安定的に支持しながら、中間ジャーナル支持部材を変速機ケースに支持するためのベアリングを不要にして重量の削減および摩擦損失の低減を図ることができる。 According to the fourth aspect of the present invention, the plurality of journal support members include a first end journal support member and a second end journal support member that are positioned at both ends in the axial direction of the input axis, and an axial center between the input axes. The first and second end journal support members are supported by the transmission case, and the intermediate journal support member is not supported by the transmission case. Therefore, the first and second end portions are supported by the transmission case. While the journal support member stably supports the first and second crank members on the transmission case, a bearing for supporting the intermediate journal support member on the transmission case is not required, thereby reducing weight and reducing friction loss. Can be planned .

クランク式無段変速機の縦断面図。The longitudinal cross-sectional view of a crank type continuously variable transmission. 図１の２−２線断面図。FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. 第１、第２クランク部材に偏心ディスクを支持した状態を示す斜視図。The perspective view which shows the state which supported the eccentric disk in the 1st, 2nd crank member. ２種類の偏心ディスクの形状を示す図。The figure which shows the shape of two types of eccentric discs. 第１、第２クランク部材のピン部の位相および各偏心ディスクの位相を示す図。The figure which shows the phase of the pin part of a 1st, 2nd crank member, and the phase of each eccentric disk. 図１の６方向矢視図。FIG. 6 is a six-direction arrow view of FIG. 偏心ディスクの偏心量の変化を示す図。The figure which shows the change of the eccentric amount of an eccentric disk. 偏心ディスクの偏心量と揺動部材の揺動角との関係を示す図。The figure which shows the relationship between the eccentric amount of an eccentric disk, and the rocking | fluctuation angle of a rocking | swiveling member. 図１の９部拡大図。9 is an enlarged view of 9 parts in FIG.

以下、図１〜図９に基づいて本発明の実施の形態を説明する。 Hereinafter, embodiments of the present invention will be described with reference to FIGS.

図１〜図３および図９に示すように、クランク式無段変速機Ｔの変速機ケース１１の第１側壁１１ａおよび第２側壁１１ｂには、入力軸線Ｌ１上に配置された第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３がそれぞれボールベアリング１４，１５を介して回転自在に支持される。第１端部ジャーナル支持部材１２は、ボールベアリング１４を介して第１側壁１１ａに支持された円板状のディスク部１２ａと、ディスク部１２ａの一端面から入力軸線Ｌ１上に突出する円筒状のカップリング部１２ｂとを備えており、カップリング部１２ｂにエンジンＥのクランクシャフト１６が接続される。第１端部ジャーナル支持部材１２のディスク部１２ａには入力軸線Ｌ１を挟むように第１ジャーナル支持孔１２ｃおよび第２ジャーナル支持孔１２ｄが形成される。一方、ボールベアリング１５を介して第２側壁１１ｂに支持された円筒状の第２端部ジャーナル支持部材１３は、その内周面にリングギヤ１３ａが形成される。エンジンＥのクランクシャフト１６に接続されて入力軸線Ｌ１まわりに回転する第１端部ジャーナル支持部材１２はクランク式無段変速機Ｔの入力軸を構成する。 As shown in FIGS. 1 to 3 and 9, the first side wall 11 a and the second side wall 11 b of the transmission case 11 of the crank type continuously variable transmission T are provided with a first end portion disposed on the input axis L <b> 1. The journal support member 12 and the second end journal support member 13 are rotatably supported via ball bearings 14 and 15, respectively. The first end journal support member 12 includes a disk-shaped disk portion 12a supported by the first side wall 11a via a ball bearing 14, and a cylindrical shape protruding from the one end surface of the disk portion 12a onto the input axis L1. And a crankshaft 16 of the engine E is connected to the coupling portion 12b. A first journal support hole 12c and a second journal support hole 12d are formed in the disk portion 12a of the first end journal support member 12 so as to sandwich the input axis L1. On the other hand, the cylindrical second end journal support member 13 supported by the second side wall 11b via the ball bearing 15 has a ring gear 13a formed on the inner peripheral surface thereof. The first end journal support member 12 connected to the crankshaft 16 of the engine E and rotating around the input axis L1 constitutes an input shaft of the crank type continuously variable transmission T.

第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３には第１クランク部材１７および第２クランク部材１８の両端部が支持される。第１クランク部材１７は、その第１軸線Ｌ３上に配置された６個の第１ジャーナル部１７ａ〜１７ｆおよび１個の第１従動ピニオン１７ｇを備えるとともに、第１ジャーナル部１７ａ〜１７ｆおよび第１従動ピニオン１７ｇ間に挟まれるように配置された６個の第１ピン部１７ｈ〜１７ｍを備える。６個の第１ピン部１７ｈ〜１７ｍの中心は第１軸線Ｌ３に対して一定距離だけ偏心しており、かつ偏心方向が相互に６０°ずつずれている。第２軸線Ｌ４上に配置された第２クランク部材１８は第１クランク部材１７と同一形状の部材であり、６個の第２ジャーナル部１８ａ〜１８ｆ、１個の第２従動ピニオン１８ｇおよび６個の第２ピン部１８ｈ〜１８ｍを備える。 Both ends of the first crank member 17 and the second crank member 18 are supported by the first end journal support member 12 and the second end journal support member 13. The first crank member 17 includes six first journal portions 17a to 17f and one first driven pinion 17g disposed on the first axis L3, and includes the first journal portions 17a to 17f and the first journal portion 17g. Six first pin portions 17h to 17m are provided so as to be sandwiched between the driven pinions 17g. The centers of the six first pin portions 17h to 17m are eccentric by a certain distance with respect to the first axis L3, and the eccentric directions are shifted by 60 ° from each other. The second crank member 18 disposed on the second axis L4 is a member having the same shape as the first crank member 17, and includes six second journal portions 18a to 18f, one second driven pinion 18g and six pieces. Second pin portions 18h to 18m.

第１クランク部材１７および第２クランク部材１８の一端側の第１、第２ジャーナル部１７ａ，１８ａは、それぞれ第１端部ジャーナル支持部材１２の第１ジャーナル支持孔１２ｃおよび第２ジャーナル支持孔１２ｄに回転自在に嵌合する。また第１クランク部材１７および第２クランク部材１８の他端側の第１、第２従動ピニオン１７ｇ，１８ｇは、変速機ケース１１の第２側壁１１ｂに支持した電動モータよりなる変速アクチュエータ１９の出力軸に設けた駆動ピニオン２０と、第２端部ジャーナル支持部材１３のリングギヤ１３ａとに同時に噛合する。従って変速アクチュエータ１９を駆動すると、駆動ピニオン２０および第１、第２従動ピニオン１７ｇ，１８ｇを介して第１クランク部材１７および第２クランク部材１８が同方向に同角度だけ回転する。 The first and second journal portions 17a and 18a on one end side of the first crank member 17 and the second crank member 18 are respectively a first journal support hole 12c and a second journal support hole 12d of the first end journal support member 12. Fits in a freely rotatable manner. The first end side of the first crank member 17 and the second crank member 18, a second driven pinion 17 g, 18 g, the second consists of an electric motor which is supported on the side wall 11b shift actuator 19 of the transmission case 11 The drive pinion 20 provided on the output shaft and the ring gear 13a of the second end journal support member 13 are simultaneously meshed. Accordingly, when the speed change actuator 19 is driven, the first crank member 17 and the second crank member 18 rotate in the same direction by the same angle via the drive pinion 20 and the first and second driven pinions 17g and 18g.

第１クランク部材１７および第２クランク部材１８には、６個の偏心ディスク２１…が支持される。尚、６個の偏心ディスク２１…を区別して説明する必要があるときには、エンジンＥ側のものから変速アクチュエータ１９側のものに向かって順番に、偏心ディスク２１Ａ〜２１Ｆと称する場合がある。 Six eccentric disks 21 are supported by the first crank member 17 and the second crank member 18. When it is necessary to distinguish and explain the six eccentric disks 21..., The eccentric disks 21 </ b> A to 21 </ b> F may be referred to in order from the engine E side toward the speed change actuator 19 side.

６個の偏心ディスク２１Ａ〜２１Ｆの間には５個の中間ジャーナル支持部材２２…が配置される。中間ジャーナル支持部材２２は円形の第１ジャーナル支持孔２２ａおよび円形の第２ジャーナル支持孔２２ｂが形成された円板状の部材であって、第１、第２クランク部材１７，１８の第１、第２ジャーナル部１７ｂ〜１７ｆ，１８ｂ〜１８ｆが第１、第２ジャーナル支持孔２２ａ…，２２ｂ…にそれぞれ回転自在に嵌合する。第１、第２クランク部材１７，１８に対する組み付けを可能にするために、中間ジャーナル支持部材２２は第１ジャーナル支持孔２２ａおよび第２ジャーナル支持孔２２ｂを通る割り面で２分割され、図示せぬボルトで一体に締結される。中間ジャーナル支持部材２２…の直径および偏心ディスク２１Ａ〜２１Ｆの直径は略一致している。 Five intermediate journal support members 22 are arranged between the six eccentric disks 21A to 21F. The intermediate journal support member 22 is a disk-shaped member in which a circular first journal support hole 22a and a circular second journal support hole 22b are formed, and the first and second crank members 17 and 18 have a first, The second journal portions 17b to 17f and 18b to 18f are fitted into the first and second journal support holes 22a. In order to allow the first and second crank members 17 and 18 to be assembled, the intermediate journal support member 22 is divided into two by a split surface passing through the first journal support hole 22a and the second journal support hole 22b, not shown. Fastened with bolts. The diameters of the intermediate journal support members 22 and the diameters of the eccentric disks 21A to 21F are substantially the same.

図４に示すように、偏心ディスク２１は中心Ｏ１を有する円板状の部材であり、中心Ｏ１から偏心する中心Ｏ２および中心Ｏ３をそれぞれ有する円形の第１、第２ピン部嵌合孔２１ａ，２１ｂが、中間点Ｍにおいて相互に接するように形成される。６個の偏心ディスク２１Ａ〜２１Ｆの形状には２種類あり、２個の偏心ディスク２１Ａ，２１Ｄは、第１、第２ピン部嵌合孔２１ａ，２１ｂの中心Ｏ２および中心Ｏ３を結ぶラインと、偏心ディスク２１Ａ，２１Ｄの中心Ｏ１および中間点Ｍを結ぶラインとが相互に重なり合う。一方、残りの４個の偏心ディスク２１Ｂ，２１Ｃ，２１Ｅ，２１Ｆは、前記２本のラインが相互に６０゜の角度で交差する。 As shown in FIG. 4, the eccentric disk 21 is a disk-shaped member having a center O1, and circular first and second pin portion fitting holes 21a having a center O2 and a center O3 that are eccentric from the center O1, respectively. 21b are formed so as to contact each other at the intermediate point M. There are two types of shapes of the six eccentric disks 21A to 21F, and the two eccentric disks 21A and 21D include a line connecting the centers O2 and O3 of the first and second pin portion fitting holes 21a and 21b, The lines connecting the center O1 and the intermediate point M of the eccentric disks 21A and 21D overlap each other. On the other hand, in the remaining four eccentric disks 21B, 21C, 21E, and 21F, the two lines intersect each other at an angle of 60 °.

図５に示すように、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｈ，１８ｈが偏心ディスク２１Ａの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合し、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｉ，１８ｉが偏心ディスク２１Ｂの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合し、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｊ，１８ｊが偏心ディスク２１Ｃの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合し、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｋ，１８ｋが偏心ディスク２１Ｄの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合し、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｌ，１８ｌが偏心ディスク２１Ｅの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合し、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｍ，１８ｍが偏心ディスク２１Ｆの第１、第２ピン部嵌合孔２１ａ，２１ｂにそれぞれ嵌合する。 As shown in FIG. 5, the first and second pin portions 17h and 18h of the first and second crank members 17 and 18 are fitted in the first and second pin portion fitting holes 21a and 21b of the eccentric disc 21A, respectively. The first and second pin portions 17i and 18i of the first and second crank members 17 and 18 are fitted in the first and second pin portion fitting holes 21a and 21b of the eccentric disc 21B, respectively. The first and second pin portions 17j and 18j of the second crank members 17 and 18 are fitted in the first and second pin portion fitting holes 21a and 21b of the eccentric disc 21C, respectively. , 18 first and second pin portions 17k, 18k are respectively fitted in the first and second pin portion fitting holes 21a, 21b of the eccentric disk 21D, and the first and second crank members 17, 18 are first. The second pin portions 17l and 18l are provided on the eccentric disk 21E. The first and second pin portions 17m and 18m of the first and second crank members 17 and 18 are respectively fitted to the second pin portion fitting holes 21a and 21b, and the first and second pin portions of the eccentric disk 21F. It fits in the fitting holes 21a and 21b, respectively.

図６に示すように、第１クランク部材１７および第２クランク部材１８に組み付けた６個の偏心ディスク２１Ａ〜２１Ｆを入力軸線Ｌ１方向に見ると、それら偏心ディスク２１Ａ〜２１Ｆの中心Ｏ１は入力軸線Ｌ１に対して一定の偏心量εだけ偏心するとともに、その偏心方向は相互に６０°ずつずれている。 As shown in FIG. 6, when the six eccentric disks 21A to 21F assembled to the first crank member 17 and the second crank member 18 are viewed in the direction of the input axis L1, the center O1 of the eccentric disks 21A to 21F is the input axis. It is decentered by a certain amount of eccentricity ε with respect to L1, and its eccentric directions are shifted by 60 ° from each other.

図１において、変速アクチュエータ１９の出力軸をエンジンＥのクランクシャフト１６と同速度で回転させると、変速アクチュエータ１９に接続された駆動ピニオン２０と第２端部ジャーナル支持部材１３に設けられたリングギヤ１３ａとが同速度で回転するため、駆動ピニオン２０およびリングギヤ１３ａに同時に噛合する第１、第２従動ピニオン１７ｇ，１８ｇは回転せず、よって第１クランク部材１７および第２クランク部材１８は一定の位相を保ったまま第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３と一体に回転する。この場合、入力軸線Ｌ１に対する第１クランク部材１７の第１ピン部１７ｈ〜１７ｍおよび第２クランク部材１８の第２ピン部１８ｈ〜１８ｍの位置関係は一定に維持され、よって６個の偏心ディスク２１Ａ〜２１Ｆは一定の偏心量εを維持したまま第１クランク部材１７および第２クランク部材１８と一体に回転する。 In FIG. 1, when the output shaft of the speed change actuator 19 is rotated at the same speed as the crankshaft 16 of the engine E, a drive pinion 20 connected to the speed change actuator 19 and a ring gear 13 a provided on the second end journal support member 13. Are rotated at the same speed, the first and second driven pinions 17g and 18g simultaneously meshing with the drive pinion 20 and the ring gear 13a do not rotate, so that the first crank member 17 and the second crank member 18 have a constant phase. The first end journal support member 12 and the second end journal support member 13 are rotated together with maintaining the above. In this case, the positional relationship between the first pin portions 17h to 17m of the first crank member 17 and the second pin portions 18h to 18m of the second crank member 18 with respect to the input axis L1 is maintained constant, and thus the six eccentric disks 21A. ˜21F rotates together with the first crank member 17 and the second crank member 18 while maintaining a constant eccentricity ε.

変速アクチュエータ１９の出力軸をエンジンＥのクランクシャフト１６と異なる速度で回転させると、変速アクチュエータ１９に接続された駆動ピニオン２０と第２端部ジャーナル支持部材１３に設けられたリングギヤ１３ａとが相対回転するため、駆動ピニオン２０およびリングギヤ１３ａに同時に噛合する第１、第２従動ピニオン１７ｇ，１８ｇが同方向に所定角度だけ回転し、よって第１クランク部材１７および第２クランク部材１８は第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３に対して同方向に相対回転する。 When the output shaft of the speed change actuator 19 is rotated at a speed different from that of the crankshaft 16 of the engine E, the drive pinion 20 connected to the speed change actuator 19 and the ring gear 13a provided on the second end journal support member 13 rotate relative to each other. Therefore, the first and second driven pinions 17g and 18g simultaneously meshing with the drive pinion 20 and the ring gear 13a rotate by a predetermined angle in the same direction, so that the first crank member 17 and the second crank member 18 have the first end portion. The journal support member 12 and the second end journal support member 13 rotate relative to each other in the same direction.

図７は、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｈ，１８ｈの位相と、その第１、第２ピン部１７ｈ，１８ｈに第１、第２ピン部嵌合孔２１ａ，２１ｂを支持された偏心ディスク２１Ａの偏心量εとの関係を示している。 FIG. 7 shows the phases of the first and second pin portions 17h and 18h of the first and second crank members 17 and 18, and the fitting of the first and second pin portions to the first and second pin portions 17h and 18h. The relationship between the eccentric amount ε of the eccentric disk 21A supported by the holes 21a and 21b is shown.

図７（Ａ）に示すように、第１、第２クランク部材１７，１８の回転角θがθ＝０°のとき、第１、第２クランク部材１７，１８の第１、第２軸線Ｌ３，Ｌ４に対して第１、第２ピン部１７ｈ，１８ｈは図中下方に偏倚しており、この状態で入力軸線Ｌ１に対する偏心ディスク２１Ａの偏心量εは最小値のゼロになる。 As shown in FIG. 7A, when the rotation angle θ of the first and second crank members 17 and 18 is θ = 0 °, the first and second axes L3 of the first and second crank members 17 and 18 are used. , L4, the first and second pin portions 17h, 18h are biased downward in the figure, and in this state, the eccentric amount ε of the eccentric disk 21A with respect to the input axis L1 becomes the minimum value of zero.

図７（Ｂ）に示すように、第１、第２クランク部材１７，１８の回転角θがθ＝４５°のとき、第１、第２クランク部材１７，１８の第１、第２軸線Ｌ３，Ｌ４に対して第１、第２ピン部１７ｈ，１８ｈは図中右下方に偏倚しており、この状態で入力軸線Ｌ１に対する偏心ディスク２１Ａの偏心量εはε１になる。 As shown in FIG. 7B, when the rotation angle θ of the first and second crank members 17 and 18 is θ = 45 °, the first and second axes L3 of the first and second crank members 17 and 18 are used. , L4, the first and second pin portions 17h, 18h are offset to the lower right in the figure, and in this state, the eccentric amount ε of the eccentric disk 21A with respect to the input axis L1 becomes ε1.

図７（Ｃ）に示すように、第１、第２クランク部材１７，１８の回転角θがθ＝９０°のとき、第１、第２クランク部材１７，１８の第１、第２軸線Ｌ３，Ｌ４に対して第１、第２ピン部１７ｈ，１８ｈは図中右方に偏倚しており、この状態で入力軸線Ｌ１に対する偏心ディスク２１Ａの偏心量εはε１よりも大きいε２になる。 As shown in FIG. 7C, when the rotation angle θ of the first and second crank members 17 and 18 is θ = 90 °, the first and second axes L3 of the first and second crank members 17 and 18 are used. , L4, the first and second pin portions 17h, 18h are biased to the right in the figure, and in this state, the eccentric amount ε of the eccentric disk 21A with respect to the input axis L1 becomes ε2, which is larger than ε1.

図７（Ｄ）に示すように、第１、第２クランク部材１７，１８の回転角θがθ＝１３５°のとき、第１、第２クランク部材１７，１８の第１、第２軸線Ｌ３，Ｌ４に対して第１、第２ピン部１７ｈ，１８ｈは図中右上方に偏倚しており、この状態で入力軸線Ｌ１に対する偏心ディスク２１Ａの偏心量εはε２よりも大きいε３になる。 As shown in FIG. 7D, when the rotation angle θ of the first and second crank members 17 and 18 is θ = 135 °, the first and second axes L3 of the first and second crank members 17 and 18 are used. , L4, the first and second pin portions 17h, 18h are offset to the upper right in the figure, and in this state, the eccentric amount ε of the eccentric disk 21A with respect to the input axis L1 becomes ε3, which is larger than ε2.

図７（Ｅ）に示すように、第１、第２クランク部材１７，１８の回転角θがθ＝１８０°のとき、第１、第２クランク部材１７，１８の第１、第２軸線Ｌ３，Ｌ４に対して第１、第２ピン部１７ｈ，１８ｈは図中上方に偏倚しており、この状態で入力軸線Ｌ１に対する偏心ディスク２１Ａの偏心量εは最大値のε４になる。 As shown in FIG. 7E, when the rotation angle θ of the first and second crank members 17 and 18 is θ = 180 °, the first and second axes L3 of the first and second crank members 17 and 18 are used. , L4, the first and second pin portions 17h, 18h are offset upward in the figure, and in this state, the eccentric amount ε of the eccentric disk 21A with respect to the input axis L1 becomes the maximum value ε4.

以上のように、変速アクチュエータ１９の出力軸をエンジンＥのクランクシャフト１６と異なる速度で回転させることで、偏心ディスク２１Ａの偏心量εを最小値のゼロと最大値のε４との間で無段階に変化させることができる。残りの５個の偏心ディスク２１Ｂ〜２１Ｆの偏心量εも、上記偏心ディスク２１Ａの偏心量εと同じ大きさを維持しながら、最小値のゼロと最大値のε４との間で無段階に変化する。 As described above, by rotating the output shaft of the speed change actuator 19 at a speed different from that of the crankshaft 16 of the engine E, the eccentric amount ε of the eccentric disk 21A is stepless between the minimum value of zero and the maximum value of ε4. Can be changed. The eccentricity ε of the remaining five eccentric disks 21B to 21F also changes steplessly between the minimum value of zero and the maximum value of ε4 while maintaining the same magnitude as the eccentricity amount ε of the eccentric disk 21A. To do.

図１および図２に示すように、入力軸線Ｌ１と平行な出力軸線Ｌ２上に出力軸２３が配置されており、出力軸２３上に６個のワンウェイクラッチ２４…を介して６個の揺動部材２５…が揺動自在に支持される。各偏心ディスク２１の外周にニードルベアリング２６を介してコネクティングロッド２７の大端部２７ａが支持され、コネクティングロッド２７の小端部２７ｂが揺動部材２５にピン２８を介して接続される。 As shown in FIGS. 1 and 2, an output shaft 23 is disposed on an output axis L2 parallel to the input axis L1, and six swings are provided on the output shaft 23 via six one-way clutches 24. The members 25 are supported in a swingable manner. A large end portion 27 a of a connecting rod 27 is supported on the outer periphery of each eccentric disk 21 via a needle bearing 26, and a small end portion 27 b of the connecting rod 27 is connected to the swing member 25 via a pin 28.

ワンウェイクラッチ２４は、出力軸２３の外周面で構成されるインナー部材２３ａと、揺動部材２５の内周面で構成されるアウター部材２５ａとの間に配置された複数のローラ２９…と、これらのローラ２９…を円周方向一方に付勢する複数のエンゲージスプリング３０とを備える。 The one-way clutch 24 includes a plurality of rollers 29 disposed between an inner member 23a constituted by the outer peripheral surface of the output shaft 23 and an outer member 25a constituted by the inner peripheral surface of the swing member 25, and the like. A plurality of engagement springs 30 for urging the rollers 29...

入力軸線Ｌ１に対して偏心ディスク２１が偏心回転すると、偏心ディスク２１に大端部２７ａを接続されたコネクティングロッド２７が往復移動し、コネクティングロッド２７の小端部２７ｂが接続された揺動部材２５が出力軸２３まわりに往復揺動する。揺動部材２５が図２の反時計方向に揺動すると、エンゲージスプリング３０…で付勢されたローラ２９…がインナー部材２３ａおよびアウター部材２５ａ間に噛み込んでワンウェイクラッチ２４が係合し、出力軸２３が所定角度回転する。揺動部材２５が図２の時計方向に揺動すると、ローラ２９…がエンゲージスプリング３０…の弾発力に抗してインナー部材２３ａおよびアウター部材２５ａ間から押し出され、ワンウェイクラッチ２４が係合解除して出力軸２３の回転が停止する。 When the eccentric disk 21 rotates eccentrically with respect to the input axis L1, the connecting rod 27 having the large end 27a connected to the eccentric disk 21 reciprocates, and the swing member 25 to which the small end 27b of the connecting rod 27 is connected. Swings back and forth around the output shaft 23. When the swinging member 25 swings counterclockwise in FIG. 2, the rollers 29 urged by the engagement springs 30 ... are engaged between the inner member 23a and the outer member 25a, and the one-way clutch 24 is engaged and output. The shaft 23 rotates by a predetermined angle. When the swinging member 25 swings in the clockwise direction in FIG. 2, the rollers 29 are pushed out from between the inner member 23a and the outer member 25a against the elastic force of the engagement spring 30, and the one-way clutch 24 is disengaged. As a result, the rotation of the output shaft 23 stops.

以上のように、コネクティングロッド２７が往復運動するとワンウェイクラッチ２４が間欠的に係合して出力軸２３が間欠的に回転するが、６個のコネクティングロッド２７が異なる位相で交互に駆動力を伝達することで、出力軸２３は連続的に回転する。 As described above, when the connecting rod 27 reciprocates, the one-way clutch 24 is intermittently engaged and the output shaft 23 rotates intermittently, but the six connecting rods 27 alternately transmit driving force at different phases. As a result, the output shaft 23 rotates continuously.

図８（Ａ）に示すように、偏心ディスク２１の偏心量εが大きいときには、コネクティングロッド２７の往復運動のストロークが大きくなるために揺動部材２５の揺動角δが大きくなり、偏心ディスク２１の１回転あたりの出力軸２３の間欠回転角が大きくなる。よって、偏心ディスク２１の偏心量εが大きいときほど、出力軸回転数に対する入力軸回転数の比である変速比が小さくなる。 As shown in FIG. 8 (A), when the eccentric amount ε of the eccentric disk 21 is large, the reciprocating stroke of the connecting rod 27 increases, so that the rocking angle δ of the rocking member 25 increases, and the eccentric disk 21. The intermittent rotation angle of the output shaft 23 per one rotation increases. Therefore, the larger the eccentric amount ε of the eccentric disk 21 is, the smaller the gear ratio, which is the ratio of the input shaft speed to the output shaft speed.

図８（Ｂ）に示すように、偏心ディスク２１の偏心量εが減少すると、コネクティングロッド２７の往復運動のストロークが小さくなって揺動部材２５の揺動角δが小さくなり、偏心ディスク２１の１回転あたりの出力軸２３の間欠回転角が小さくなる。よって、偏心ディスク２１の偏心量εが小さくなるのに伴って変速比が大きくなる。図８（Ｃ）に示すように、偏心ディスク２１の偏心量εがゼロになると、コネクティングロッド２７が往復運動を停止して揺動部材２５が往復揺動を停止するため、出力軸２３は回転を停止して変速比が無限大になる。 As shown in FIG. 8B, when the eccentric amount ε of the eccentric disk 21 decreases, the stroke of the reciprocating motion of the connecting rod 27 decreases, and the swing angle δ of the swing member 25 decreases. The intermittent rotation angle of the output shaft 23 per rotation is reduced. Therefore, the gear ratio increases as the eccentric amount ε of the eccentric disk 21 decreases. As shown in FIG. 8C, when the eccentric amount ε of the eccentric disk 21 becomes zero, the connecting rod 27 stops the reciprocating motion and the swinging member 25 stops the reciprocating swinging, so that the output shaft 23 rotates. And the gear ratio becomes infinite.

以上のように、偏心ディスク２１…の偏心量εを最大偏心量とゼロとの間で変化させることで、クランク式無段変速機Ｔの変速比を最小のＯＤ状態（オーバードライブ状態）と無限大のＧＮ状態（ギヤドニュートラル状態）との間で無段階に変化させることができる。 As described above, by changing the eccentricity ε of the eccentric disks 21 between the maximum eccentricity and zero, the transmission ratio of the crank type continuously variable transmission T can be reduced to the minimum OD state (overdrive state) and infinite. It can be changed steplessly between a large GN state (geared neutral state).

図９に示すように、偏心ディスク２１…の軸方向厚さＷ１は、第１、第２クランク部材１７，１８の第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向厚さＷ２より大きく設定されている。６個の偏心ディスク２１…の間に挟まれた５個の中間ジャーナル支持部材２２…の軸方向端面は、偏心ディスク２１…の軸方向端面に摺動自在に当接し、第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向端面との間に僅かな隙間αを有している。また第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３の軸方向端面も、それらに対向する偏心ディスク２１Ａ，２１Ｆの軸方向端面に摺動自在に当接し、第１、第２ピン部１７ｈ，１８ｈ，１７ｍ，１８ｍの軸方向端面との間に僅かな隙間αを有している。 As shown in FIG. 9, the axial thickness W1 of the eccentric discs 21 ... is the axial thickness W2 of the first and second pin portions 17h-17m, 18h-18m of the first and second crank members 17, 18. It is set larger. The axial end surfaces of the five intermediate journal support members 22 sandwiched between the six eccentric discs 21 are slidably abutted with the axial end surfaces of the eccentric discs 21. There is a slight gap α between the axial end surfaces of the portions 17h to 17m and 18h to 18m. Further, the axial end surfaces of the first end journal support member 12 and the second end journal support member 13 are also slidably brought into contact with the axial end surfaces of the eccentric disks 21A and 21F opposed to the first end journal support member 13 and the first end journal support member 13, respectively. A slight gap α is provided between the axial ends of the pin portions 17h, 18h, 17m, and 18m.

次に、図９に基づいて第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…の作用を説明する。 Next, the operation of the first end journal support member 12, the second end journal support member 13, and the intermediate journal support members 22 ... will be described with reference to FIG.

図２に示すように、本実施の形態のクランク式無段変速機Ｔは、コネクティングロッド２７が矢印Ａ１方向に移動して揺動部材２５が矢印Ａ２方向に揺動するとき、つまりコネクティングロッド２７に引張荷重が作用するときにワンウェイクラッチ２４が係合して駆動力を伝達する。 As shown in FIG. 2, the crank type continuously variable transmission T according to the present embodiment is configured such that the connecting rod 27 moves in the arrow A1 direction and the swing member 25 swings in the arrow A2 direction, that is, the connecting rod 27. When a tensile load acts on the one-way clutch 24, the one-way clutch 24 is engaged to transmit the driving force.

図９において、６本のコネクティングロッド２７…に引張荷重が作用するとき、コネクティングロッド２７…に偏心ディスク２１Ａ〜２１Ｆを介して接続された第１、第２クランク部材１７，１８は軸方向両端の第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３を支点として出力軸２３に向けて図中下向きに引っ張られ、太い鎖線で示すように弧状に湾曲しようとする。このようにして第１、第２クランク部材１７，１８が湾曲すると第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍが傾くため、変速比を変化させるべく第１、第２クランク部材１７，１８を回転させたときに、第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの外周面と各偏心ディスク２１の第１、第２ピン部嵌合孔２１ａ，２１ｂの内周面との摺動部の摩擦損失が増加するだけでなく、偏心ディスク２１…も第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍに引きずられて傾くため、コネクティングロッド２７…の大端部２７ａ…を支持するニードルベアリング２６…の摩擦損失も増加する可能性がある。 In FIG. 9, when a tensile load acts on the six connecting rods 27, the first and second crank members 17, 18 connected to the connecting rods 27 via eccentric disks 21A to 21F are provided at both ends in the axial direction. The first end journal support member 12 and the second end journal support member 13 are pulled downward in the figure toward the output shaft 23 with the fulcrum as a fulcrum, and try to bend in an arc shape as indicated by a thick chain line. When the first and second crank members 17 and 18 are bent in this way, the first and second pin portions 17h to 17m and 18h to 18m are inclined, so that the first and second crank members 17 and 17 are changed to change the gear ratio. When the 18 is rotated, the outer peripheral surfaces of the first and second pin portions 17h to 17m and 18h to 18m and the inner peripheral surfaces of the first and second pin portion fitting holes 21a and 21b of the eccentric disks 21 Not only does the friction loss of the sliding part increase, but also the eccentric disk 21... Is tilted by being dragged by the first and second pin parts 17 h to 17 m and 18 h to 18 m, so that the large end part 27 a of the connecting rod 27. The friction loss of the supporting needle bearings 26 may also increase.

しかしながら、本実施の形態によれば、偏心ディスク２１…を挟むように配置された第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…が、偏心ディスク２１…の軸方向端面に相対回転自在に当接するため、当接部に発生する面圧で第１、第２クランク部材１７，１８の撓みが抑制され、第１、第２クランク部材１７，１８の撓みによる摩擦損失の増加が最小限に抑えられる。 However, according to the present embodiment, the first end journal support member 12, the second end journal support member 13, and the intermediate journal support member 22 arranged so as to sandwich the eccentric disks 21. Since the first and second crank members 17 and 18 are bent by the surface pressure generated at the contact portion, the first and second crank members 17 and 18 are prevented from being bent. Increase in friction loss due to bending is minimized.

このとき、第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３は変速機ケース１１にボールベアリング１４，１５を介して支持されているため、第１端部ジャーナル支持部材１２および第２端部ジャーナル支持部材１３で第１、第２クランク部材１７，１８を安定的に支持することができ、しかも５個の中間ジャーナル支持部材２２…は変速機ケース１１に支持されずにフローティング状態にあるため、中間ジャーナル支持部材２２…を変速機ケース１１に支持するためのベアリングを不要にして重量の削減および摩擦損失の更なる低減を図ることができる。 At this time, since the first end journal support member 12 and the second end journal support member 13 are supported by the transmission case 11 via the ball bearings 14 and 15, the first end journal support member 12 and the second end journal support member 12 The two end journal support members 13 can stably support the first and second crank members 17, 18, and the five intermediate journal support members 22... Are not supported by the transmission case 11 and are in a floating state. Therefore, it is possible to reduce the weight and further reduce the friction loss by eliminating the need for bearings for supporting the intermediate journal support members 22 to the transmission case 11.

また偏心ディスク２１…の軸方向厚さＷ１を、第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向厚さＷ２よりも大きくし、第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向端面が第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…の軸方向端面に当接しないようにしたので、変速比変更時に当接部の面積を最小限に抑えて摩擦損失を低減することができる。 Further, the axial thickness W1 of the eccentric disk 21 is made larger than the axial thickness W2 of the first and second pin portions 17h to 17m and 18h to 18m, and the first and second pin portions 17h to 17m and 18h. axial end faces the first end journal support member 12 of ～18M, since not to contact the second end journal support member 13 and the intermediate journal support member 22 ... axial end faces of those at the time of speed ratio change Friction loss can be reduced by minimizing the contact area.

しかも偏心ディスク２１…に対する第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…の当接部は、第１、第２クランク部材１７，１８の第１軸線Ｌ３および第２軸線Ｌ４から大きく離れているため、第１、第２クランク部材１７，１８の撓み防止効果を有効に発揮させることができる。 Moreover, the abutting portions of the first end journal support member 12, the second end journal support member 13, and the intermediate journal support member 22 with respect to the eccentric disks 21 are the first axes of the first and second crank members 17, 18. Since it is far away from L3 and the second axis L4, the effect of preventing the deflection of the first and second crank members 17, 18 can be effectively exhibited.

更に、偏心ディスク２１…の外径は第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…の外径に略一致するので、第１、第２クランク部材１７，１８の撓み防止効果を充分に発揮させながら、第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…の外径を最小限に抑えて重量を削減することができる。 Further, since the outer diameters of the eccentric disks 21 are substantially the same as the outer diameters of the first end journal support member 12, the second end journal support member 13, and the intermediate journal support members 22 ..., the first and second crank members. while sufficiently be exhibited only prevention effect wrinkles 17, the weight is suppressed first end journal support member 12, a second end journal support member 13 and the intermediate journal support member 22 ... the outer diameter of a minimum Can be reduced.

以上、本発明の実施の形態を説明したが、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、実施の形態では第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…が偏心ディスク２１…の軸方向端面だけに当接するが、それらを第１、第２クランク部材１７，１８の第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向端面だけに当接させても良い。 For example, in the embodiment, the first end journal support member 12, the second end journal support member 13, and the intermediate journal support member 22 contact only the axial end surface of the eccentric disk 21 ... You may make it contact | abut only to the axial direction end surface of the 1st, 2nd pin parts 17h-17m of the 2nd crank members 17 and 18, 18h-18m.

このようにすれば、第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…で第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの傾きを抑制して第１、第２クランク部材１７，１８の撓みを抑制することができ、ひいては偏心ディスク２１…の傾きを抑制することができる。 In this way, the first end journal support member 12, the second end journal support member 13, the intermediate journal support member 22 ... suppress the inclination of the first and second pin portions 17h to 17m, 18h to 18m. Thus, the bending of the first and second crank members 17 and 18 can be suppressed, and as a result, the inclination of the eccentric disks 21 can be suppressed.

勿論、第１端部ジャーナル支持部材１２、第２端部ジャーナル支持部材１３および中間ジャーナル支持部材２２…を、偏心ディスク２１…の軸方向端面および第１、第２クランク部材１７，１８の第１、第２ピン部１７ｈ〜１７ｍ，１８ｈ〜１８ｍの軸方向端面の両方に当接させても良い。 Of course, the first end journal support member 12, the second end journal support member 13, and the intermediate journal support member 22 are connected to the axial end surface of the eccentric disk 21 and the first of the first and second crank members 17 and 18, respectively. The second pin portions 17h to 17m and 18h to 18m may be in contact with both axial end surfaces.

また実施の形態ではコネクティングロッド２７が引張荷重により駆動力を伝達するようになっているが、圧縮荷重により駆動力を伝達するようにしても良い。 In the embodiment, the connecting rod 27 transmits the driving force by a tensile load, but the driving force may be transmitted by a compressive load.

また本発明の駆動源は実施の形態のエンジンＥに限定されず、電動モータのような他種の駆動源であっても良い。 The drive source of the present invention is not limited to the engine E of the embodiment, and may be another type of drive source such as an electric motor.

また実施の形態ではクランク式無段変速機Ｔが６個の偏心ディスク２１Ａ〜２１Ｆを備えているが、偏心ディスクの数は６個に限定されるものではない。 In the embodiment, the crank type continuously variable transmission T includes the six eccentric disks 21A to 21F, but the number of the eccentric disks is not limited to six.

１１変速機ケース
１２第１端部ジャーナル支持部材（入力軸、ジャーナル支持部材）
１３第２端部ジャーナル支持部材（ジャーナル支持部材）
１７第１クランク部材
１７ａ〜１７ｆ第１ジャーナル部
１７ｈ〜１７ｍ第１ピン部
１８第２クランク部材
１８ａ〜１８ｆ第２ジャーナル部
１８ｈ〜１８ｍ第２ピン部
２１偏心ディスク
２１ａ第１ピン部嵌合孔
２１ｂ第２ピン部嵌合孔
２２中間ジャーナル支持部材（ジャーナル支持部材）
２３出力軸
２４ワンウェイクラッチ
２５揺動部材
２７コネクティングロッド
Ｅエンジン（駆動源）
Ｌ１入力軸線
Ｌ２出力軸線
Ｌ３第１軸線
Ｌ４第２軸線
Ｗ１偏心ディスクの軸方向厚さ
Ｗ２第１、第２ピン部の軸方向厚さ
ε 偏心ディスクの偏心量
11 Transmission case 12 First end journal support member (input shaft, journal support member)
13 Second end journal support member (journal support member)
17 1st crank member 17a-17f 1st journal part 17h-17m 1st pin part 18 2nd crank member 18a-18f 2nd journal part 18h-18m 2nd pin part 21 Eccentric disk 21a 1st pin part fitting hole 21b Second pin portion fitting hole 22 Intermediate journal support member (journal support member)
23 Output shaft 24 One-way clutch 25 Swing member 27 Connecting rod E Engine (drive source)
L1 input axis L2 output axis L3 first axis L4 second axis W1 axial thickness W2 of the eccentric disk axial thickness ε of the first and second pin portions ε eccentricity of the eccentric disk

Claims

入力軸線（Ｌ１）上に配置されて駆動源（Ｅ）の駆動力が入力される入力軸（１２）と、出力軸線（Ｌ２）上に配置されて前記入力軸（１２）の駆動力が変速されて伝達される出力軸（２３）と、前記入力軸（１２）と一体に回転する第１クランク部材（１７）と、前記入力軸（１２）と一体に回転する第２クランク部材（１８）と、前記第１、第２クランク部材（１７，１８）に支持されて前記入力軸線（Ｌ１）に対する偏心量（ε）が可変である複数の偏心ディスク（２１）と、前記出力軸（２３）の外周に揺動自在に支持された複数の揺動部材（２５）と、前記出力軸（２３）および前記複数の揺動部材（２５）間に配置された複数のワンウェイクラッチ（２４）と、前記複数の偏心ディスク（２１）および前記複数の揺動部材（２５）を接続する複数のコネクティングロッド（２７）とを備え、
前記第１クランク部材（１７）は、前記入力軸線（Ｌ１）に対して偏心する第１軸線上（Ｌ３）に配置された複数の第１ジャーナル部（１７ａ〜１７ｆ）と、前記複数の第１ジャーナル部（１７ａ〜１７ｆ）に対して偏心する複数の第１ピン部（１７ｈ〜１７ｍ）とを備え、
前記第２クランク部材（１８）は、前記入力軸線（Ｌ１）に対して偏心する第２軸線（Ｌ４）上に配置された複数の第２ジャーナル部（１８ａ〜１８ｆ）と、前記複数の第２ジャーナル部（１８ａ〜１８ｆ）に対して偏心する複数の第２ピン部（１８ｈ〜１８ｍ）とを備え、
前記複数の偏心ディスク（２１）は、前記第１ピン部（１７ｈ〜１７ｍ）が回転自在に嵌合する第１ピン部嵌合孔（２１ａ）と、前記第２ピン部（１８ｈ〜１８ｍ）が回転自在に嵌合する第２ピン部嵌合孔（２１ｂ）とを備え、
前記入力軸（１２）に対して前記第１、第２クランク部材（１７，１８）を相対回転させることで、前記複数の偏心ディスク（２１）の偏心量（ε）をゼロおよび所定値間で変化させる無段変速機であって、
前記第１クランク部材（１７）の前記第１ジャーナル部（１７ａ〜１７ｆ）および前記第２クランク部材（１８）の前記第２ジャーナル部（１８ａ〜１８ｆ）を支持する複数のジャーナル支持部材（１２，１３，２２）を備え、前記複数のジャーナル支持部材（１２，１３，２２）は前記複数の偏心ディスク（２１）の軸方向端面および前記複数の第１、第２ピン部（１７ｈ〜１７ｍ，１８ｈ〜１８ｍ）の軸方向端面の少なくとも一方に相対回転自在に当接し、
前記複数の偏心ディスク（２１）の軸方向厚さ（Ｗ１）は前記第１、第２ピン部（１７ｈ〜１７ｍ，１８ｈ〜１８ｍ）の軸方向厚さ（Ｗ２）よりも大きく、前記複数のジャーナル支持部材（１２，１３，２２）は前記複数の偏心ディスク（２１）の軸方向端面に相対回転自在に当接することを特徴とする無段変速機。 An input shaft (12) that is arranged on the input axis (L1) and receives the driving force of the drive source (E), and a driving force of the input shaft (12) that is arranged on the output axis (L2) and changes the speed. Output shaft (23) transmitted, the first crank member (17) rotating integrally with the input shaft (12), and the second crank member (18) rotating integrally with the input shaft (12). A plurality of eccentric disks (21) supported by the first and second crank members (17, 18) and having a variable eccentricity (ε) with respect to the input axis (L1), and the output shaft (23). A plurality of swinging members (25) supported swingably on the outer periphery of the output shaft, a plurality of one-way clutches (24) disposed between the output shaft (23) and the plurality of swinging members (25), The plurality of eccentric disks (21) and the plurality of swing members (25 And a plurality of connecting rods connecting the (27),
The first crank member (17) includes a plurality of first journal portions (17a to 17f) disposed on a first axis (L3) eccentric with respect to the input axis (L1), and the plurality of first A plurality of first pin portions (17h to 17m) eccentric with respect to the journal portions (17a to 17f),
The second crank member (18) includes a plurality of second journal portions (18a to 18f) disposed on a second axis (L4) eccentric with respect to the input axis (L1), and the plurality of second crank members (18). A plurality of second pin portions (18h to 18m) eccentric with respect to the journal portion (18a to 18f),
The plurality of eccentric disks (21) have a first pin portion fitting hole (21a) into which the first pin portions (17h to 17m) are rotatably fitted, and the second pin portions (18h to 18m). A second pin portion fitting hole (21b) that fits rotatably,
By rotating the first and second crank members (17, 18) relative to the input shaft (12), the eccentric amount (ε) of the plurality of eccentric disks (21) is between zero and a predetermined value. A continuously variable transmission,
A plurality of journal support members (12, 12) for supporting the first journal portion (17a-17f) of the first crank member (17) and the second journal portion (18a-18f) of the second crank member (18). 13 and 22), and the plurality of journal support members (12, 13, 22) include axial end surfaces of the plurality of eccentric disks (21) and the plurality of first and second pin portions (17h to 17m, 18h). relatively rotatably contact the at least one axial end face of the ~18m),
An axial thickness (W1) of the plurality of eccentric disks (21) is larger than an axial thickness (W2) of the first and second pin portions (17h to 17m, 18h to 18m), and the plurality of journals The continuously variable transmission, wherein the support members (12, 13, 22) abut against the axial end surfaces of the plurality of eccentric disks (21) in a relatively rotatable manner.

入力軸線（Ｌ１）上に配置されて駆動源（Ｅ）の駆動力が入力される入力軸（１２）と、出力軸線（Ｌ２）上に配置されて前記入力軸（１２）の駆動力が変速されて伝達される出力軸（２３）と、前記入力軸（１２）と一体に回転する第１クランク部材（１７）と、前記入力軸（１２）と一体に回転する第２クランク部材（１８）と、前記第１、第２クランク部材（１７，１８）に支持されて前記入力軸線（Ｌ１）に対する偏心量（ε）が可変である複数の偏心ディスク（２１）と、前記出力軸（２３）の外周に揺動自在に支持された複数の揺動部材（２５）と、前記出力軸（２３）および前記複数の揺動部材（２５）間に配置された複数のワンウェイクラッチ（２４）と、前記複数の偏心ディスク（２１）および前記複数の揺動部材（２５）を接続する複数のコネクティングロッド（２７）とを備え、
前記第１クランク部材（１７）は、前記入力軸線（Ｌ１）に対して偏心する第１軸線上（Ｌ３）に配置された複数の第１ジャーナル部（１７ａ〜１７ｆ）と、前記複数の第１ジャーナル部（１７ａ〜１７ｆ）に対して偏心する複数の第１ピン部（１７ｈ〜１７ｍ）とを備え、
前記第２クランク部材（１８）は、前記入力軸線（Ｌ１）に対して偏心する第２軸線（Ｌ４）上に配置された複数の第２ジャーナル部（１８ａ〜１８ｆ）と、前記複数の第２ジャーナル部（１８ａ〜１８ｆ）に対して偏心する複数の第２ピン部（１８ｈ〜１８ｍ）とを備え、
前記複数の偏心ディスク（２１）は、前記第１ピン部（１７ｈ〜１７ｍ）が回転自在に嵌合する第１ピン部嵌合孔（２１ａ）と、前記第２ピン部（１８ｈ〜１８ｍ）が回転自在に嵌合する第２ピン部嵌合孔（２１ｂ）とを備え、
前記入力軸（１２）に対して前記第１、第２クランク部材（１７，１８）を相対回転させることで、前記複数の偏心ディスク（２１）の偏心量（ε）をゼロおよび所定値間で変化させる無段変速機であって、
前記第１クランク部材（１７）の前記第１ジャーナル部（１７ａ〜１７ｆ）および前記第２クランク部材（１８）の前記第２ジャーナル部（１８ａ〜１８ｆ）を支持する複数のジャーナル支持部材（１２，１３，２２）を備え、前記複数のジャーナル支持部材（１２，１３，２２）は前記複数の偏心ディスク（２１）の軸方向端面および前記複数の第１、第２ピン部（１７ｈ〜１７ｍ，１８ｈ〜１８ｍ）の軸方向端面の少なくとも一方に相対回転自在に当接し、
前記複数の偏心ディスク（２１）の外径は前記複数のジャーナル支持部材（１２，１３，２２）の外径に略一致することを特徴とする無段変速機。 An input shaft (12) that is arranged on the input axis (L1) and receives the driving force of the drive source (E), and a driving force of the input shaft (12) that is arranged on the output axis (L2) and changes the speed. Output shaft (23) transmitted, the first crank member (17) rotating integrally with the input shaft (12), and the second crank member (18) rotating integrally with the input shaft (12). A plurality of eccentric disks (21) supported by the first and second crank members (17, 18) and having a variable eccentricity (ε) with respect to the input axis (L1), and the output shaft (23). A plurality of swinging members (25) supported swingably on the outer periphery of the output shaft, a plurality of one-way clutches (24) disposed between the output shaft (23) and the plurality of swinging members (25), The plurality of eccentric disks (21) and the plurality of swing members (25 And a plurality of connecting rods connecting the (27),
The first crank member (17) includes a plurality of first journal portions (17a to 17f) disposed on a first axis (L3) eccentric with respect to the input axis (L1), and the plurality of first A plurality of first pin portions (17h to 17m) eccentric with respect to the journal portions (17a to 17f),
The second crank member (18) includes a plurality of second journal portions (18a to 18f) disposed on a second axis (L4) eccentric with respect to the input axis (L1), and the plurality of second crank members (18). A plurality of second pin portions (18h to 18m) eccentric with respect to the journal portion (18a to 18f),
The plurality of eccentric disks (21) have a first pin portion fitting hole (21a) into which the first pin portions (17h to 17m) are rotatably fitted, and the second pin portions (18h to 18m). A second pin portion fitting hole (21b) that fits rotatably,
By rotating the first and second crank members (17, 18) relative to the input shaft (12), the eccentric amount (ε) of the plurality of eccentric disks (21) is between zero and a predetermined value. A continuously variable transmission,
A plurality of journal support members (12, 12) for supporting the first journal portion (17a-17f) of the first crank member (17) and the second journal portion (18a-18f) of the second crank member (18). 13 and 22), and the plurality of journal support members (12, 13, 22) include axial end surfaces of the plurality of eccentric disks (21) and the plurality of first and second pin portions (17h to 17m, 18h). ~ 18m) at least one of the axial end faces in a relatively rotatable manner,
Substantially continuously variable transmission you characterized in that matches the outer diameter of the plurality of journal support member (12,13,22) of said plurality of eccentric disks (21).

前記複数の偏心ディスク（２１）の外径は前記複数のジャーナル支持部材（１２，１３，２２）の外径に略一致することを特徴とする、請求項１に記載の無段変速機。The continuously variable transmission according to claim 1, wherein the outer diameters of the plurality of eccentric disks (21) substantially coincide with the outer diameters of the plurality of journal support members (12, 13, 22).

前記複数のジャーナル支持部材（１２，１３，２２）は、前記入力軸線（Ｌ１）の軸方向両端部に位置する第１端部ジャーナル支持部材（１２）および第２端部ジャーナル支持部材（１３）と、前記入力軸線（Ｌ１）の軸方向中間部に位置する中間ジャーナル支持部材（２２）とからなり、前記第１、第２端部ジャーナル支持部材（１２，１３）は変速機ケース（１１）に支持され、前記中間ジャーナル支持部材（２２）は前記変速機ケース（１１）に支持されないことを特徴とする、請求項１〜請求項３の何れか１項に記載の無段変速機。 The plurality of journal support members (12, 13, 22) are a first end journal support member (12) and a second end journal support member (13) located at both axial ends of the input axis (L1). And an intermediate journal support member (22) positioned at an intermediate portion in the axial direction of the input axis (L1). The first and second end journal support members (12, 13) serve as a transmission case (11). The continuously variable transmission according to any one of claims 1 to 3 , wherein the intermediate journal support member (22) is not supported by the transmission case (11).