JP2012237348A - Transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission device which can be driven with excellent power transmission efficiency.SOLUTION: The transmission device has a stepless transmission 2 including: the first and the second rotary members 10, 20 capable of relatively rotating around the first central shaft A1 as a center; a sun roller 30; planet balls 50 of multiple number disposed radially on an outer circumference of the sun roller 30, and pinched between the first and the second roller members 10, 20; a support shaft 51 having the second central shaft A2 and supporting the planet ball 50 rotatably; a tilting mechanism 60 for tilting each second central shaft A2 toward the first central shaft A1 with the planet ball 50 and the support shaft 51; and a carrier 40 for supporting each planet ball 50 through each support shaft 51. When the angle made by a base line LO and a line L1 connecting the gravity center G of the planet ball 50 and a contact point P1 and the angle made by the base line LO and the gravity center G and a line L2 connecting the gravity center G and a contact point P2 are defined as a contact angle θ, and the angle made by the second central shaft A2 to a line L3 is defined as a tilting angle α, the tilting mechanism 60 controls so that the tilting angle α falls within the range of -|θ|≤α≤|θ|.

Description

本発明は、共通の回転軸を有する２つの回転要素と、その回転軸に対して放射状に複数配置した転動部材と、を備え、各回転要素の内の２つに挟持された各転動部材を傾転させることによって入出力間の変速比を無段階に変化させる変速装置に関する。   The present invention includes two rotating elements having a common rotating shaft and a plurality of rolling members arranged radially with respect to the rotating shaft, and each rolling element sandwiched between two of the rotating elements. The present invention relates to a transmission that changes a transmission ratio between input and output steplessly by tilting a member.

この種の変速装置としては、例えば、下記の特許文献１に開示されたものが知られている。この特許文献１には、回転要素としての入力ディスクと出力ディスクとで挟持された複数のボール（転動部材）を有し、そのボールの傾転角を調整して変速比を無段階に変える無段変速機構と、この無段変速機構の出力軸に回転要素の１つが連結された遊星歯車機構（差動機構）と、を備えた所謂トラクションドライブ式の無段変速機が開示されている。   As this type of transmission, for example, the one disclosed in Patent Document 1 below is known. This Patent Document 1 has a plurality of balls (rolling members) sandwiched between an input disk and an output disk as rotating elements, and changes the gear ratio steplessly by adjusting the tilt angle of the balls. A so-called traction drive type continuously variable transmission including a continuously variable transmission mechanism and a planetary gear mechanism (differential mechanism) in which one of rotating elements is connected to an output shaft of the continuously variable transmission mechanism is disclosed. .

尚、従来、無段変速機と有段変速機とを有している変速装置が知られている。例えば、下記の特許文献２には、トロイダル式の無段変速機と低速段及び高速段からなる有段変速機とを直列に繋げたものにおいて、夫々の変速比から決まる総合変速比を変化させない為に、有段変速機を低速段から高速段に切り替えると共に無段変速機を低速段側に変速させる技術が開示されている。また、下記の特許文献３には、ベルト式の無段変速機と減速機構としての遊星歯車機構からなる有段変速機とを備えた変速装置において、その有段自動変速機の変速比について、無段変速機の最大変速比より小さく、且つ、有段自動変速機の変速比と出力伝達効率との積が無段変速機の最大変速比と最大変速比における出力伝達効率との積よりも大きくなるように設定する技術が開示されている。また、下記の特許文献４には、ベルト式の無段変速機と遊星歯車機構からなる有段変速機とを備えた変速装置において、高速走行時の動力伝達効率を高めるべく、有段変速機を１よりも小さい変速比に固定すると共に、無段変速機の変速比を増大させる技術が開示されている。更に、下記の特許文献５には、入力ディスク及び出力ディスクとパワーローラとの接触点での相対滑り角速度（スピン角速度）並びに入力ディスクの角速度から決まるスピンについて、ロー側変速比からハイ側変速比までの変速比範囲で０以上になるように諸元を決めたトロイダル式の無段変速機が開示されている。その諸元とは、夫々の接触点における法線とパワーローラの回転軸とがなす角度θ、パワーローラの傾転角度φ、入出力ディスクの円弧半径をＲ０とし、円弧中心から入出力ディスク回転軸までの距離とＲ０との差をｅとしたときの比ｋ＝（ｅ／Ｒ０）である。   Conventionally, a transmission having a continuously variable transmission and a stepped transmission is known. For example, in Patent Document 2 below, a toroidal continuously variable transmission and a stepped transmission consisting of a low speed stage and a high speed stage are connected in series, and the overall speed ratio determined by each speed ratio is not changed. For this purpose, a technique for switching the stepped transmission from the low speed stage to the high speed stage and shifting the continuously variable transmission to the low speed stage side is disclosed. In addition, in Patent Document 3 below, in a transmission including a belt-type continuously variable transmission and a stepped transmission including a planetary gear mechanism as a speed reduction mechanism, the gear ratio of the stepped automatic transmission is as follows. The product of the gear ratio of the continuously variable transmission and the output transmission efficiency is smaller than the product of the maximum gear ratio of the continuously variable transmission and the output transmission efficiency at the maximum gear ratio. A technique for setting to be large is disclosed. Further, in Patent Document 4 below, in a transmission device including a belt-type continuously variable transmission and a stepped transmission including a planetary gear mechanism, a stepped transmission is provided in order to increase power transmission efficiency during high-speed traveling. Is fixed to a gear ratio smaller than 1, and a technology for increasing the gear ratio of the continuously variable transmission is disclosed. Further, Patent Document 5 below discloses a relative slip angular velocity (spin angular velocity) at a contact point between an input disk and an output disk and a power roller, and a spin determined from an angular speed of the input disk, and a low gear ratio to a high gear ratio. A toroidal continuously variable transmission has been disclosed in which specifications are determined so as to be 0 or more in the speed ratio range up to. The specifications are the angle θ between the normal line at each contact point and the rotation axis of the power roller, the tilt angle φ of the power roller, the arc radius of the input / output disk is R0, and the input / output disk is rotated from the center of the arc. The ratio k = (e / R0) where e is the difference between the distance to the axis and R0.

特表２００６−５１９３４９号公報JP-T-2006-519349 特開２００６−０２２８３９号公報JP 2006-022839 A 特開２００８−１６４１１７号公報JP 2008-164117 A 特開２００７−２１１９６２号公報JP 2007-211962 A 特開２００２−０５４７０７号公報JP 2002-054707 A

ところで、トラクションドライブ式の無段変速機は、その変速比の大きさ如何で動力伝達効率が変化する。これが為、使用される変速比によっては、動力伝達効率の悪化を招く虞がある。   By the way, the power transmission efficiency of a traction drive type continuously variable transmission changes depending on the speed ratio. For this reason, depending on the gear ratio used, there is a risk of deteriorating power transmission efficiency.

そこで、本発明は、かかる従来例の有する不都合を改善し、良好な動力伝達効率で運転可能な変速装置を提供することを、その目的とする。   Therefore, an object of the present invention is to provide a transmission that can improve the disadvantages of the conventional example and can be operated with good power transmission efficiency.

上記目的を達成する為、本発明は、共通の第１中心軸上で対向させて配置し、該第１中心軸を中心とする相対回転が可能な第１及び第２の部材と、前記第１中心軸と同心上で且つ前記第１部材と前記第２部材との間に配置した第３部材と、前記第１中心軸と平行な第２中心軸及び回転中心となる当該第２中心軸上の重心を有し、前記第３部材の外周面上で前記第１中心軸を中心として放射状に複数配置すると共に、前記第１及び第２の部材との夫々の接点が前記第１中心軸から径方向外側に向けて同じ距離で且つ前記重心からも同じ距離となるように当該第１及び第２の部材に挟持させた転動部材と、前記第２中心軸を有し、前記転動部材を回転自在に支持する支持軸と、夫々の前記第２中心軸を前記第１中心軸に対して前記転動部材及び前記支持軸と共に傾転させる傾転機構と、前記各支持軸を介して前記各転動部材を傾転動作が可能な状態で支持する第４部材と、を備えた無段変速機を有し、前記転動部材の重心から径方向に向けた基準線と当該転動部材の重心及び当該転動部材上の前記第１部材との接点を結ぶ線とが成す角度並びに前記基準線と前記転動部材の重心及び当該転動部材上の前記第２部材との接点を結ぶ線とが成す角度を接触角θとし、且つ、前記転動部材の重心を通る前記第１中心軸と平行な線に対する前記第２中心軸の成す角度を傾転角αとし、その傾転角αが「−｜θ｜≦α≦｜θ｜」の範囲内に収まるよう前記傾転機構を制御することを特徴としている。   In order to achieve the above object, the present invention provides a first member and a second member which are arranged to face each other on a common first central axis and are capable of relative rotation about the first central axis, A third member disposed concentrically with one central axis and between the first member and the second member; a second central axis parallel to the first central axis; and the second central axis serving as a rotation center A plurality of radial centers about the first central axis on the outer peripheral surface of the third member, and a plurality of contacts with the first and second members are arranged on the first central axis. A rolling member sandwiched between the first and second members so as to be the same distance from the center of gravity toward the radially outer side and the second center axis, and the rolling A support shaft for rotatably supporting the member, and the rolling member and the front of each of the second central axes with respect to the first central axis. A continuously variable transmission comprising: a tilting mechanism that tilts together with the support shaft; and a fourth member that supports each of the rolling members through the support shafts in a state in which the tilting operation is possible. The angle formed by the reference line extending in the radial direction from the center of gravity of the rolling member and the line connecting the center of gravity of the rolling member and the contact point of the first member on the rolling member, and the reference line and the rolling The angle formed by the center of gravity of the member and the line connecting the contact point with the second member on the rolling member is defined as a contact angle θ, and the line parallel to the first central axis passing through the center of gravity of the rolling member An angle formed by the second central axis is a tilt angle α, and the tilt mechanism is controlled so that the tilt angle α is within a range of “− | θ | ≦ α ≦ | θ |”. Yes.

ここで、前記第２部材と一体になって回転する低速用第１歯車及び当該低速用第１歯車に噛み合う低速用第２歯車を備えた低速段と、前記第２部材と一体になって回転する高速用第１歯車及び当該高速用第１歯車に噛み合う高速用第２歯車を備えた高速段と、を有する有段変速機を設け、前記有段変速機が前記低速段のときで且つ前記無段変速機の傾転角αが「α＝θ」のときの当該無段変速機における前記第１部材と前記第２部材との間の回転比をγｄ１、前記有段変速機が前記高速段のときで且つ前記無段変速機の傾転角αが「α＝−θ」のときの当該無段変速機における前記第１部材と前記第２部材との間の回転比をγｄ２、前記有段変速機の低速段の変速比をγＬｏ、前記有段変速機の高速段の変速比をγＨｉとし、これらが「（γＬｏ／γＨｉ）≦（γｄ２／γｄ１）」の関係を満たすことが望ましい。   Here, a low-speed stage including a first low-speed gear that rotates integrally with the second member, and a second low-speed gear meshing with the first low-speed gear, and the second member rotate together. And a high speed stage having a high speed second gear meshing with the high speed first gear, wherein the stepped transmission is at the low speed stage and When the tilt angle α of the continuously variable transmission is “α = θ”, the rotation ratio between the first member and the second member in the continuously variable transmission is γd1, and the stepped transmission is the high speed. The rotation ratio between the first member and the second member in the continuously variable transmission when the step and the tilt angle α of the continuously variable transmission is “α = −θ” is γd2, The speed ratio of the low speed stage of the stepped transmission is γLo, the speed ratio of the high speed stage of the stepped transmission is γHi, and these are “(γLo / γ i) ≦ (γd2 / γd1) preferably satisfies the relationship ".

本発明に係る変速装置は、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御することで、傾転角αを「α＜−｜θ｜」又は「α＞｜θ｜」の範囲内で制御した場合よりも、無段変速機の変速比が動力伝達効率の良好なものとなる。また、この変速装置は、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御することで、その傾転角αの変化率に対する無段変速機の変速比の変化率を一定に保つことができるので、変速比の制御性に優れる。従って、本発明に係る変速装置に依れば、動力伝達効率と変速制御性の良好な変速比の領域のみが使われることになり、燃費や変速品質が向上する。   The transmission according to the present invention controls the tilt angle α within the range of “− | θ | ≦ α ≦ | θ |”, so that the tilt angle α is “α <− | θ |” or “α The speed ratio of the continuously variable transmission is better in power transmission efficiency than when the control is performed within the range of> | θ |. In addition, this transmission device controls the tilt angle α within the range of “− | θ | ≦ α ≦ | θ |”, so that the speed ratio of the continuously variable transmission with respect to the rate of change of the tilt angle α can be reduced. Since the change rate can be kept constant, the controllability of the gear ratio is excellent. Therefore, according to the transmission according to the present invention, only the region of the transmission ratio with good power transmission efficiency and transmission controllability is used, and fuel consumption and transmission quality are improved.

図１は、無段変速機及び有段変速機を備える本発明に係る変速装置の全体構成を示す概略図である。FIG. 1 is a schematic diagram showing the overall configuration of a transmission according to the present invention including a continuously variable transmission and a stepped transmission. 図２は、無段変速機について説明する図である。FIG. 2 is a diagram illustrating a continuously variable transmission. 図３は、無段変速機における傾転角と夫々の接点の接点距離との関係を説明する図である。FIG. 3 is a diagram for explaining the relationship between the tilt angle and the contact distance of each contact in the continuously variable transmission. 図４は、無段変速機における変速比と夫々の接点の損失との関係を説明する図である。FIG. 4 is a diagram for explaining the relationship between the gear ratio and the loss of each contact in a continuously variable transmission. 図５は、無段変速機における変速比と動力伝達効率との関係を説明する図である。FIG. 5 is a diagram for explaining the relationship between the gear ratio and the power transmission efficiency in the continuously variable transmission. 図６は、無段変速機における傾転角と変速比との関係を説明する図である。FIG. 6 is a diagram for explaining the relationship between the tilt angle and the gear ratio in the continuously variable transmission. 図７は、変速装置における変速比と動力伝達効率との関係を説明する図である。FIG. 7 is a diagram for explaining the relationship between the gear ratio and power transmission efficiency in the transmission. 図８は、変速装置における変速比と動力伝達効率との関係を説明する図である。FIG. 8 is a diagram illustrating the relationship between the transmission ratio and the power transmission efficiency in the transmission. 図９は、変速装置のアップシフト制御時の動作について説明するタイムチャートである。FIG. 9 is a time chart for explaining the operation during upshift control of the transmission. 図１０は、変速装置のダウンシフト制御時の動作について説明するタイムチャートである。FIG. 10 is a time chart for explaining the operation during downshift control of the transmission. 図１１は、変速装置における傾転角と変速比との関係を説明する図である。FIG. 11 is a diagram illustrating the relationship between the tilt angle and the gear ratio in the transmission.

以下に、本発明に係る変速装置の実施例を図面に基づいて詳細に説明する。尚、この実施例によりこの発明が限定されるものではない。   Hereinafter, embodiments of a transmission according to the present invention will be described in detail with reference to the drawings. The present invention is not limited to the embodiments.

［実施例］
本発明に係る変速装置の実施例を図１から図１１に基づいて説明する。この例示では車両用の変速装置として説明するが、この変速装置は、入出力間の変速を要するものであれば、車両以外に適用してもよい。 [Example]
An embodiment of a transmission according to the present invention will be described with reference to FIGS. In this example, the transmission is described as a transmission for a vehicle. However, the transmission may be applied to a vehicle other than a vehicle as long as a transmission between input and output is required.

図１の符号１は、本実施例の変速装置を示す。この変速装置１は、トラクションドライブ式の無段変速機２を有している。   Reference numeral 1 in FIG. 1 indicates the transmission of this embodiment. The transmission 1 has a traction drive type continuously variable transmission 2.

この無段変速機２は、第１から第４の部材１０，２０，３０，４０と、転動部材５０と、傾転機構６０と、を備えた所謂トラクション遊星ギヤ機構と云われるものである。第１及び第２の部材１０，２０は、共通の第１中心軸Ａ１上で対向させて配置され、その相互間で第１中心軸Ａ１を中心とする相対回転を行うことができる。第３及び第４の部材３０，４０は、第１中心軸Ａ１と同心上で且つ第１部材１０と第２部材２０との間に配置される。転動部材５０は、第１中心軸Ａ１と平行な第２中心軸Ａ２及び回転中心となる当該第２中心軸Ａ２上の重心を有し、第３部材３０の外周面上で第１中心軸Ａ１を中心とする放射状に複数配置されると共に、第１及び第２の部材１０，２０との夫々の接点が第１中心軸Ａ１から径方向外側に向けて同じ距離で且つ前記重心からも同じ距離となるように当該第１及び第２の部材１０，２０に挟持されたものである。傾転機構６０は、夫々の転動部材５０の第２中心軸Ａ２を第１中心軸Ａ１に対して転動部材５０及び支持軸５１と共に傾転させるものである。ここで、この転動部材５０は、第２中心軸Ａ２を有する支持軸５１によって回転自在に支持されている。また、各転動部材５０は、その外周面が第１から第３の部材１０，２０，３０で保持されると共に、各支持軸５１を介して傾転動作が可能な状態で第４部材４０に支持されている。   The continuously variable transmission 2 is a so-called traction planetary gear mechanism including first to fourth members 10, 20, 30, 40, a rolling member 50, and a tilting mechanism 60. . The first and second members 10 and 20 are arranged to face each other on a common first central axis A1, and can perform relative rotation around the first central axis A1 between them. The third and fourth members 30 and 40 are disposed concentrically with the first central axis A <b> 1 and between the first member 10 and the second member 20. The rolling member 50 has a second central axis A2 parallel to the first central axis A1 and a center of gravity on the second central axis A2 serving as a rotation center, and the first central axis on the outer peripheral surface of the third member 30 A plurality of radial arrangements centered on A1, and the respective contacts with the first and second members 10 and 20 are the same distance from the first central axis A1 toward the radially outer side and the same from the center of gravity. It is sandwiched between the first and second members 10 and 20 so as to be a distance. The tilting mechanism 60 tilts the second central axis A2 of each rolling member 50 together with the rolling member 50 and the support shaft 51 with respect to the first central axis A1. Here, the rolling member 50 is rotatably supported by a support shaft 51 having a second central axis A2. Each rolling member 50 has its outer peripheral surface held by the first to third members 10, 20, and 30 and can be tilted via each support shaft 51. It is supported by.

以下においては、特に言及しない限り、その第１中心軸Ａ１や第２中心軸Ａ２に沿う方向を軸線方向と云い、その第１中心軸Ａ１周りの方向を周方向と云う。また、その第１中心軸Ａ１に直交する方向を径方向と云い、その中でも、内方に向けた側を径方向内側と、外方に向けた側を径方向外側と云う。   In the following, unless otherwise specified, the direction along the first central axis A1 and the second central axis A2 is referred to as the axial direction, and the direction around the first central axis A1 is referred to as the circumferential direction. Further, the direction orthogonal to the first central axis A1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

この無段変速機２においては、第１部材１０と第２部材２０と第３部材３０との間で各転動部材５０を介したトルクの伝達が行われる。そのトルクの伝達は、第１及び第２の部材１０，２０の内の少なくとも一方を転動部材５０に押し付け、これにより第１から第３の部材１０，２０，３０と各転動部材５０との間に適切な接線力（トラクション力）を発生させることによって可能にする。   In the continuously variable transmission 2, torque is transmitted through the rolling members 50 among the first member 10, the second member 20, and the third member 30. The torque is transmitted by pressing at least one of the first and second members 10, 20 against the rolling member 50, whereby the first to third members 10, 20, 30 and each rolling member 50 are It is made possible by generating an appropriate tangential force (traction force) during

また、この無段変速機２は、第２中心軸Ａ２を第１中心軸Ａ１に対して傾斜させ、支持軸５１と共に転動部材５０を傾転させることによって、入出力間の変速比γ_ＣＶＰを変える。その傾転動作は、夫々の転動部材５０を自身の第２中心軸Ａ２と第１中心軸Ａ１とを含む傾転平面上において自らの重心を中心にして動かすことによって行う。 Further, the continuously variable transmission 2 tilts the second central axis A2 with respect to the first central axis A1 and tilts the rolling member 50 together with the support shaft 51, whereby the gear ratio γ _CVP between input and output is increased. change. The tilting operation is performed by moving each rolling member 50 about its own center of gravity on the tilting plane including the second central axis A2 and the first central axis A1.

この無段変速機２においては、第１から第４の部材１０，２０，３０，４０の内の何れか１つが周方向に回転しない固定要素となり、残りが周方向に回転する回転要素になる。そして、この無段変速機２では、その回転要素の内の１つがトルク（動力）の入力部となり、残りの回転要素の内の少なくとも１つがトルクの出力部となる。これが為、この無段変速機２においては、入力部となる何れかの回転要素と出力部となる何れかの回転要素との間の回転速度（回転数）の比が変速比γ_ＣＶＰとなる。例えば、この無段変速機２は、車両の動力伝達経路上に配設される。その際には、その入力部がエンジンやモータ等の動力源側に連結され、その出力部が駆動輪側に連結される。この無段変速機２においては、入力部としての回転要素にトルクが入力された場合の各回転要素の回転動作を正駆動と云い、出力部としての回転要素に正駆動時とは逆方向のトルクが入力された場合の各回転要素の回転動作を逆駆動と云う。例えば、この無段変速機２は、先の車両の例示に従えば、加速等のように動力源側からトルクが入力部たる回転要素に入力されて当該回転要素を回転させているときが正駆動となり、減速等の様に駆動輪側から出力部たる回転中の回転要素に正駆動時とは逆方向のトルクが入力されているときが逆駆動となる。 In the continuously variable transmission 2, any one of the first to fourth members 10, 20, 30, 40 is a fixed element that does not rotate in the circumferential direction, and the rest is a rotating element that rotates in the circumferential direction. . In the continuously variable transmission 2, one of the rotating elements serves as a torque (power) input unit, and at least one of the remaining rotating elements serves as a torque output unit. For this reason, in this continuously variable transmission 2, the ratio of the rotational speed (the number of rotations) between any of the rotating elements serving as the input unit and any of the rotating elements serving as the output unit is the gear ratio γ _CVP. . For example, the continuously variable transmission 2 is disposed on the power transmission path of the vehicle. In that case, the input part is connected with the power source side, such as an engine and a motor, and the output part is connected with the drive wheel side. In this continuously variable transmission 2, the rotation operation of each rotation element when torque is input to the rotation element as the input unit is referred to as normal drive, and the rotation element as the output unit is in the direction opposite to that during normal drive. The rotating operation of each rotating element when torque is input is called reverse driving. For example, in the continuously variable transmission 2, according to the example of the preceding vehicle, when the torque is input from the power source side to the rotating element as the input unit and the rotating element is rotated as in acceleration or the like, Driving is performed, and reverse driving is performed when torque in the opposite direction to that during forward driving is input to the rotating rotating element serving as the output unit from the driving wheel side, such as deceleration.

ここで、この無段変速機２においては、第１及び第２の部材１０，２０が遊星歯車機構で云うところのリングギヤの機能を為すものとなる。また、第３部材３０は、トラクション遊星ギヤ機構のサンローラとして機能する。また、第４部材４０は、トラクション遊星ギヤ機構のキャリアとして機能する。また、転動部材５０は、トラクション遊星ギヤ機構におけるボール型ピニオンとして機能する。従って、以下においては、第３部材３０を「サンローラ３０」と云い、第４部材４０を「キャリア４０」と云う。更に、転動部材５０については、「遊星ボール５０」と云う。また、以下の例示では、キャリア４０を固定要素とする。故に、以下においては、第１及び第２の部材１０，２０のことを各々「第１及び第２の回転部材１０，２０」と云う。   Here, in the continuously variable transmission 2, the first and second members 10 and 20 perform the ring gear function as a planetary gear mechanism. The third member 30 functions as a sun roller of the traction planetary gear mechanism. The fourth member 40 functions as a carrier for the traction planetary gear mechanism. Moreover, the rolling member 50 functions as a ball-type pinion in the traction planetary gear mechanism. Therefore, in the following, the third member 30 is referred to as “sun roller 30”, and the fourth member 40 is referred to as “carrier 40”. Further, the rolling member 50 is referred to as a “planetary ball 50”. In the following example, the carrier 40 is a fixed element. Therefore, hereinafter, the first and second members 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively.

第１及び第２の回転部材１０，２０は、中心軸を第１中心軸Ａ１に一致させた円盤部材（ディスク）や円環部材（リング）であり、軸線方向で対向させて各遊星ボール５０を挟み込むように配設する。この例示においては、双方とも円環部材とする。   The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose central axes are coincident with the first central axis A1, and are opposed to each other in the axial direction so as to face each planetary ball 50. It arrange | positions so that it may be inserted | pinched. In this example, both are circular members.

この第１及び第２の回転部材１０，２０は、後で詳述する各遊星ボール５０の径方向外側の外周曲面と接触する接触面を有している。その夫々の接触面は、例えば、遊星ボール５０の外周曲面の曲率と同等の曲率の凹円弧面、その外周曲面の曲率とは異なる曲率の凹円弧面、凸円弧面又は平面等の形状を成している。ここでは、後述する基準位置の状態で第１中心軸Ａ１から各遊星ボール５０との接点Ｐ１，Ｐ２までの距離が同じ長さになるように夫々の接触面を形成して、第１及び第２の回転部材１０，２０の各遊星ボール５０に対する夫々の接触角θが同じ角度になるようにしている（図２）。その接触角θとは、基準線Ｌ０から各遊星ボール５０における第１及び第２の回転部材１０，２０との接点Ｐ１，Ｐ２までの角度のことであり、その基準線Ｌ０と遊星ボール５０の重心Ｇ及び接点Ｐ１，Ｐ２を結ぶ夫々の線Ｌ１，Ｌ２とが成す角度のことである。ここでは、遊星ボール５０の重心Ｇから径方向に向けた線を基準線Ｌ０に設定している。その夫々の接触面は、遊星ボール５０の外周曲面に対して点接触するものとして説明するが、面接触するものであってもよい。また、夫々の接触面は、第１及び第２の回転部材１０，２０から遊星ボール５０に向けて軸線方向の力（押圧力）が加わった際に、その遊星ボール５０に対して径方向内側で且つ斜め方向の力（法線力）が加わるように形成されている。   Each of the first and second rotating members 10 and 20 has a contact surface that comes into contact with a radially outer peripheral curved surface of each planetary ball 50 described in detail later. Each of the contact surfaces has, for example, a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 50, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. doing. Here, the contact surfaces are formed so that the distances from the first central axis A1 to the contact points P1 and P2 with the planetary balls 50 are the same length in the state of the reference position described later. The contact angles θ of the two rotating members 10 and 20 with respect to the planetary balls 50 are set to the same angle (FIG. 2). The contact angle θ is an angle from the reference line L0 to the contacts P1 and P2 of each planetary ball 50 with the first and second rotating members 10 and 20, and the reference line L0 and the planetary ball 50 have a contact angle θ. This is the angle formed by the center of gravity G and the lines L1 and L2 connecting the contacts P1 and P2. Here, the line from the center of gravity G of the planetary ball 50 toward the radial direction is set as the reference line L0. Each contact surface will be described as a point contact with the outer peripheral curved surface of the planetary ball 50, but may be a surface contact. Each contact surface is radially inward with respect to the planetary ball 50 when an axial force (pressing force) is applied from the first and second rotating members 10, 20 toward the planetary ball 50. And an oblique force (normal force) is applied.

その遊星ボール５０への押圧力は、例えばトルクカム（図示略）等の押圧部で第１及び第２の回転部材１０，２０の内の少なくとも一方に加えられた軸線方向の力により発生させる。そのトルクカムは、例えば第１回転部材１０と下記の入力軸１１との間、第２回転部材２０と下記の出力軸２１との間に配設する。その第１回転部材１０と入力軸１１との間のトルクカムは、その間で回転トルクを伝達させると共に軸力を発生させる。その軸力は、第１回転部材１０から遊星ボール５０への押圧力として伝わる。また、第２回転部材２０と出力軸２１との間のトルクカムは、その間で回転トルクを伝達させると共に軸力を発生させる。その軸力は、第２回転部材２０から遊星ボール５０への押圧力として伝わる。   The pressing force to the planetary ball 50 is generated by an axial force applied to at least one of the first and second rotating members 10 and 20 by a pressing portion such as a torque cam (not shown), for example. The torque cam is disposed, for example, between the first rotating member 10 and the following input shaft 11 and between the second rotating member 20 and the following output shaft 21. The torque cam between the first rotating member 10 and the input shaft 11 transmits rotational torque therebetween and generates an axial force. The axial force is transmitted as a pressing force from the first rotating member 10 to the planetary ball 50. Further, the torque cam between the second rotating member 20 and the output shaft 21 transmits the rotational torque therebetween and generates an axial force. The axial force is transmitted as a pressing force from the second rotating member 20 to the planetary ball 50.

この例示においては、第１回転部材１０を無段変速機２の正駆動時におけるトルク入力部として作用させ、第２回転部材２０を無段変速機２の正駆動時におけるトルク出力部として作用させる。従って、その第１回転部材１０には入力軸１１が連結され、第２回転部材２０には出力軸２１が連結される。その入力軸１１は、動力源側に接続されている。また、出力軸２１は、駆動輪側に接続されている。   In this illustration, the first rotating member 10 acts as a torque input portion when the continuously variable transmission 2 is positively driven, and the second rotating member 20 acts as a torque output portion when the continuously variable transmission 2 is positively driven. . Accordingly, the input shaft 11 is connected to the first rotating member 10, and the output shaft 21 is connected to the second rotating member 20. The input shaft 11 is connected to the power source side. The output shaft 21 is connected to the drive wheel side.

サンローラ３０は、第１中心軸Ａ１と同心の円筒状又は円柱状のものである。このサンローラ３０の外周面には、複数個の遊星ボール５０が放射状に略等間隔で配置される。従って、このサンローラ３０においては、その外周面が遊星ボール５０の自転の際の転動面となる。このサンローラ３０は、自らの回転動作によって夫々の遊星ボール５０を転動（自転）させることもできれば、夫々の遊星ボール５０の転動動作（自転動作）に伴って回転することもできる。   The sun roller 30 is cylindrical or columnar concentric with the first central axis A1. A plurality of planetary balls 50 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 is a rolling surface when the planetary ball 50 rotates. The sun roller 30 can roll (rotate) each planetary ball 50 by its own rotation, or it can rotate along with the rolling operation (spinning) of each planetary ball 50.

遊星ボール５０は、サンローラ３０の外周面上を転がる転動部材である。この遊星ボール５０は、完全な球状体であることが好ましいが、少なくとも転動方向にて球形を成すもの、例えばラグビーボールの様な断面が楕円形状のものであってもよい。この遊星ボール５０は、その中心（重心Ｇ）を通って貫通させた支持軸５１によって支持する。この遊星ボール５０は、支持軸５１の外周面との間に配設した軸受（例えばニードルベアリング）によって、第２中心軸Ａ２を回転軸とした支持軸５１に対する相対回転（つまり自転）が行えるようにしている。従って、この遊星ボール５０は、支持軸５１を中心にしてサンローラ３０の外周面上を転動することができる。その支持軸５１の両端は、遊星ボール５０から突出させておく。   The planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30. The planetary ball 50 is preferably a perfect spherical body, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. The planetary ball 50 is supported by a support shaft 51 that passes through the center (center of gravity G). The planetary ball 50 can be rotated relative to the support shaft 51 with the second central axis A2 as a rotation axis (that is, rotation) by a bearing (for example, a needle bearing) disposed between the planetary ball 50 and the outer peripheral surface of the support shaft 51. I have to. Accordingly, the planetary ball 50 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 51. Both ends of the support shaft 51 are projected from the planetary ball 50.

その支持軸５１の基準となる位置は、図１に示すように、第２中心軸Ａ２が第１中心軸Ａ１と平行になる位置である。この支持軸５１は、その基準位置で形成される自身の中心軸（第２中心軸Ａ２）と第１中心軸Ａ１とを含む傾転平面内において、基準位置とそこから傾斜させた位置との間を遊星ボール５０と共に揺動（傾転）することができる。その傾転は、その傾転平面内で遊星ボール５０の重心Ｇを中心にして行われる。   The reference position of the support shaft 51 is a position where the second central axis A2 is parallel to the first central axis A1, as shown in FIG. The support shaft 51 has a reference position and a position inclined from the reference position in a tilt plane including the center axis (second center axis A2) and the first center axis A1 formed at the reference position. It can swing (tilt) with the planetary ball 50 between them. The tilt is performed around the center of gravity G of the planetary ball 50 in the tilt plane.

キャリア４０は、夫々の遊星ボール５０の傾転動作を妨げないように支持軸５１の夫々の突出部を支持する。このキャリア４０は、例えば、第１中心軸Ａ１と同心の第１及び第２の円盤部４１，４２を対向させて配置し、その第１及び第２の円盤部４１，４２を複数本の連結軸（図示略）で連結して、全体として籠状となるようにしている。これにより、このキャリア４０は、外周面に開放部分を有することになる。各遊星ボール５０は、第１及び第２の円盤部４１，４２の間に配置し、その開放部分を介して第１回転部材１０と第２回転部材２０とに接している。   The carrier 40 supports each projecting portion of the support shaft 51 so as not to prevent the tilting motion of each planetary ball 50. In this carrier 40, for example, first and second disk parts 41, 42 concentric with the first central axis A1 are arranged to face each other, and a plurality of the first and second disk parts 41, 42 are connected. They are connected by a shaft (not shown) so as to have a bowl shape as a whole. As a result, the carrier 40 has an open portion on the outer peripheral surface. Each planetary ball 50 is disposed between the first and second disk portions 41 and 42 and is in contact with the first rotating member 10 and the second rotating member 20 through an open portion thereof.

この無段変速機２には、その変速比γ_ＣＶＰを変える為の変速部が設けられている。変速比γ_ＣＶＰは遊星ボール５０の傾転角αの変化に伴い変わるので、その変速部としては、夫々の遊星ボール５０を傾転させる傾転機構６０を用いる。ここで云う傾転角αとは、遊星ボール５０の重心Ｇを通る第１中心軸Ａ１と平行な線（基準線）Ｌ３に対する第２中心軸Ａ２の成す角度のことである。ここでは、その基準線Ｌ３に対する時計回り方向を正とする。 The continuously variable transmission 2 is provided with a transmission unit for changing the transmission gear ratio γ _CVP . Since the gear ratio γ _CVP changes as the tilt angle α of the planetary ball 50 changes, a tilt mechanism 60 that tilts each planetary ball 50 is used as the speed change portion. The tilt angle α referred to here is an angle formed by the second central axis A2 with respect to a line (reference line) L3 parallel to the first central axis A1 passing through the center of gravity G of the planetary ball 50. Here, the clockwise direction with respect to the reference line L3 is positive.

この傾転機構６０には、この技術分野において周知のものを利用する。例えば、傾転機構６０としては、延設された支持軸５１の一方の端部に取り付けられた長手方向が径方向の支持部材と、この支持部材に径方向の力を加えるアクチュエータと、で構成されたものが考えられる。この傾転機構６０は、その支持部材を径方向へと動かすことにより、支持軸５１を介して遊星ボール５０を傾転させることができる。また、傾転機構６０としては、第１中心軸Ａ１と同心の円盤状のアイリスプレートを用いてもよい。そのアイリスプレートは、支持軸５１の一方の突出部が挿入される絞り孔（アイリス孔）を遊星ボール５０毎に備えたものであり、例えば第２回転部材２０と第２円盤部４２との間に配設する。その絞り孔は、径方向内側の端部を起点とし、この基点から径方向に向けた線を基準線と仮定した場合、径方向内側から径方向外側に向かうにつれて基準線から周方向に離れていく弧状になっている。この種の傾転機構６０は、アイリスプレートを周方向に回転させることによって、支持軸５１を介して遊星ボール５０を傾転させることができる。   As the tilt mechanism 60, a mechanism well known in this technical field is used. For example, the tilting mechanism 60 includes a support member having a longitudinal direction attached to one end of the extended support shaft 51 and an actuator that applies a radial force to the support member. What has been considered. The tilt mechanism 60 can tilt the planetary ball 50 via the support shaft 51 by moving the support member in the radial direction. Further, as the tilting mechanism 60, a disc-shaped iris plate concentric with the first central axis A1 may be used. The iris plate is provided with a throttle hole (iris hole) into which one protrusion of the support shaft 51 is inserted for each planetary ball 50, for example, between the second rotating member 20 and the second disk portion 42. It arranges in. Assuming that the restriction hole starts from the radially inner end and the line extending from the base point in the radial direction is the reference line, the restriction hole moves away from the reference line in the circumferential direction from the radially inner side toward the radially outer side. It is arcuate. This type of tilting mechanism 60 can tilt the planetary ball 50 via the support shaft 51 by rotating the iris plate in the circumferential direction.

この無段変速機２には、夫々の遊星ボール５０の傾転時に支持軸５１を傾転方向へと案内する為のガイド部（支持部）が設けられている。この例示では、そのガイド部をキャリア４０に設ける。ガイド部は、遊星ボール５０から突出させた支持軸５１を傾転方向に向けて案内する径方向のガイド溝４１ａ，４２ａであり、第１及び第２の円盤部４１，４２の夫々の対向する部分に遊星ボール５０毎に形成する。全てのガイド溝４１ａと全てのガイド溝４２ａは、軸線方向から観ると夫々に放射状を成している。また、ガイド溝４１ａとガイド溝４２ａは、軸線方向で対向させた位置に配置されている。   The continuously variable transmission 2 is provided with a guide portion (support portion) for guiding the support shaft 51 in the tilt direction when each planetary ball 50 tilts. In this example, the guide portion is provided on the carrier 40. The guide portions are radial guide grooves 41a and 42a for guiding the support shaft 51 protruding from the planetary ball 50 in the tilt direction, and the first and second disk portions 41 and 42 are opposed to each other. A portion is formed for each planetary ball 50. All the guide grooves 41a and all the guide grooves 42a are radial when viewed from the axial direction. The guide groove 41a and the guide groove 42a are disposed at positions facing each other in the axial direction.

この無段変速機２においては、夫々の遊星ボール５０の傾転角αが基準位置、即ち０度のときに、第１回転部材１０と第２回転部材２０とが同一回転速度（同一回転数）で回転する。つまり、このときには、第１回転部材１０と第２回転部材２０との間の回転比（回転速度又は回転数の比）γｄが１となる。その回転比γｄは、第１及び第２の回転部材１０，２０の回転数を各々Ｎ１，Ｎ２とすると、「γｄ＝Ｎ１／Ｎ２」で表される。この無段変速機２では第１回転部材１０が入力側で且つ第２回転部材２０が出力側なので、このときの変速比γ_ＣＶＰは、１になる。 In this continuously variable transmission 2, when the tilt angle α of each planetary ball 50 is the reference position, that is, 0 degrees, the first rotating member 10 and the second rotating member 20 have the same rotational speed (the same rotational speed). ) To rotate. That is, at this time, the rotation ratio (rotational speed or rotation speed ratio) γd between the first rotating member 10 and the second rotating member 20 is 1. The rotation ratio γd is expressed by “γd = N1 / N2” where the rotation speeds of the first and second rotating members 10 and 20 are N1 and N2, respectively. In this continuously variable transmission 2, since the first rotating member 10 is on the input side and the second rotating member 20 is on the output side, the gear ratio γ _{CVP at} this time is 1.

一方、夫々の遊星ボール５０を基準位置から傾転させた際には、第２中心軸Ａ２から第１回転部材１０との接点Ｐ１までの距離（第１接点距離）Ｄ１が変化すると共に、第２中心軸Ａ２から第２回転部材２０との接点Ｐ２までの距離（第２接点距離）Ｄ２が変化する。その第１接点距離Ｄ１は、第２中心軸Ａ２と接点Ｐ１との最短距離に相当し、第２接点距離Ｄ２は、第２中心軸Ａ２と接点Ｐ２との最短距離に相当する（図２）。図３には、第１から第３の接点距離Ｄ１，Ｄ２，Ｄ３と傾転角αとの対応関係を各々示している。第３接点距離Ｄ３とは、第２中心軸Ａ２と遊星ボール５０におけるサンローラ３０との接点Ｐ３との最短距離に相当するものである。また、「Ｒｂ」は、遊星ボール５０の半径である。その第１接点距離Ｄ１と第２接点距離Ｄ２は、遊星ボール５０の半径Ｒｂ、傾転角α及び接触角θを用いて下記の式１，２の如く求めることができる。   On the other hand, when each planetary ball 50 is tilted from the reference position, the distance (first contact distance) D1 from the second central axis A2 to the contact P1 with the first rotating member 10 changes, and the first 2 The distance (second contact distance) D2 from the central axis A2 to the contact P2 with the second rotating member 20 changes. The first contact distance D1 corresponds to the shortest distance between the second central axis A2 and the contact P1, and the second contact distance D2 corresponds to the shortest distance between the second central axis A2 and the contact P2 (FIG. 2). . FIG. 3 shows the correspondence between the first to third contact distances D1, D2, D3 and the tilt angle α. The third contact distance D3 corresponds to the shortest distance between the second central axis A2 and the contact point P3 of the planetary ball 50 with the sun roller 30. “Rb” is the radius of the planetary ball 50. The first contact distance D1 and the second contact distance D2 can be obtained by using the radius Rb, the tilt angle α, and the contact angle θ of the planetary ball 50 as in the following formulas 1 and 2.

Ｄ１＝Ｒｂ×ｃｏｓ（θ＋α） … （１）
Ｄ２＝Ｒｂ×ｃｏｓ（θ−α） … （２） D1 = Rb × cos (θ + α) (1)
D2 = Rb × cos (θ−α) (2)

そして、回転比γｄや変速比γ_ＣＶＰは、第１接点距離Ｄ１と第２接点距離Ｄ２とを用いて下記の式３の如く表すこともできる。 Then, the rotation ratio γd and the transmission ratio γ _CVP can be expressed as the following Expression 3 using the first contact distance D1 and the second contact distance D2.

γｄ＝γ_ＣＶＰ＝Ｄ１／Ｄ２ … （３） γd = γ _CVP = D1 / D2 (3)

その接点距離の変化により、この無段変速機２においては、第１回転部材１０又は第２回転部材２０の内の何れか一方が基準位置のときよりも高速で回転し、他方が低速で回転するようになる。例えば第２回転部材２０は、遊星ボール５０を一方へと傾転させたときに第１回転部材１０よりも低回転になり（減速）、他方へと傾転させたときに第１回転部材１０よりも高回転になる（増速）。従って、この無段変速機２においては、その傾転角αを変えることによって、第１回転部材１０と第２回転部材２０との間の回転比γｄ（＝変速比γ_ＣＶＰ）を無段階に変化させることができる。尚、ここでの増速時（γ_ＣＶＰ＜１）には、図１における上側の遊星ボール５０を紙面時計回り方向に傾転させ且つ下側の遊星ボール５０を紙面反時計回り方向に傾転させる。また、減速時（γ_ＣＶＰ＞１）には、図１における上側の遊星ボール５０を紙面反時計回り方向に傾転させ且つ下側の遊星ボール５０を紙面時計回り方向に傾転させる。 Due to the change in the contact distance, in the continuously variable transmission 2, either the first rotating member 10 or the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. To come. For example, the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 50 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed). Therefore, in this continuously variable transmission 2, the rotation ratio γd (= transmission ratio γ _CVP ) between the first rotating member 10 and the second rotating member 20 is stepless by changing the tilt angle α. Can be changed. When the speed is increased (γ _CVP <1), the upper planetary ball 50 in FIG. 1 is tilted clockwise in the plane of the drawing, and the lower planetary ball 50 is tilted counterclockwise in the plane of the drawing. Let Further, at the time of deceleration (γ _CVP > 1), the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper surface and the lower planetary ball 50 is tilted clockwise on the paper surface.

このように、この無段変速機２は、傾転角αの大きさに応じて第１回転部材１０と第２回転部材２０との間の回転比γｄ（＝変速比γ_ＣＶＰ）が変化する。 Thus, in the continuously variable transmission 2, the rotation ratio γd (= transmission ratio γ _CVP ) between the first rotating member 10 and the second rotating member 20 changes according to the magnitude of the tilt angle α. .

ここで、この無段変速機２の各接点Ｐ１，Ｐ２，Ｐ３における変速比γ_ＣＶＰとスピン損失との関係を観てみる。スピン損失は、夫々の接点Ｐ１，Ｐ２，Ｐ３におけるスピン量と接点面積と接点面圧との積に比例する。 Here, the relationship between the speed ratio γ _CVP and the spin loss at each contact P1, P2, P3 of the continuously variable transmission 2 will be examined. The spin loss is proportional to the product of the spin amount, the contact area, and the contact surface pressure at each contact P1, P2, P3.

接点Ｐ１においては、傾転角αが接触角θのときの変速比γ_ＣＶＰ（α＝θ）｛＜１｝でスピン損失が最も小さく、傾転角αが接触角θよりも大きくなるほど又は接触角θよりも小さくなるほど、つまり変速比γ_ＣＶＰが変速比γ_ＣＶＰ（α＝θ）よりも小さくなるほど又は変速比γ_ＣＶＰ（α＝θ）よりも大きくなるほどスピン損失が大きくなる。接点Ｐ２においては、傾転角αが接触角−θのときの変速比γ_ＣＶＰ（α＝−θ）｛＞１｝でスピン損失が最も小さく、傾転角αが接触角−θよりも大きくなるほど又は接触角−θよりも小さくなるほど、つまり変速比γ_ＣＶＰが変速比γ_ＣＶＰ（α＝−θ）よりも大きくなるほど又は変速比γ_ＣＶＰ（α＝−θ）よりも小さくなるほどスピン損失が大きくなる。接点Ｐ３においては、傾転角αが０のときの変速比γ_ＣＶＰ（α＝０）｛＝１｝でスピン損失が最も小さく、傾転角αが０よりも大きくなるほど又は０よりも小さくなるほど、つまり変速比γ_ＣＶＰが１よりも大きくなるほど又は１よりも小さくなるほどスピン損失が大きくなる。従って、無段変速機２においては、傾転角αが接触角θよりも大きくなるほど又は傾転角αが接触角−θよりも大きくなるほどにスピン損失が拡大していく。一方、傾転角αが接触角θよりも小さい領域又は傾転角αが接触角−θよりも小さい領域では、そのスピン損失の拡大する領域よりもスピン損失が小さくなる。 In the contact P1, the spin loss is the smallest at the gear ratio γ _CVP (α = θ) {<1} when the tilt angle α is the contact angle θ, and the contact angle P becomes larger as the tilt angle α becomes larger than the contact angle θ. more smaller than angle theta, i.e. the gear ratio gamma _CVP spin loss increases as greater than the speed ratio γ _{CVP (α} = θ) smaller than the more or gear ratio γ _{CVP (α} = θ). In the contact P2, the spin loss is the smallest at the gear ratio γ _CVP (α = −θ) {> 1} when the tilt angle α is the contact angle −θ, and the tilt angle α is larger than the contact angle −θ. more smaller than the more or contact angle - [theta], i.e. the spin loss is large enough smaller than the gear ratio gamma _CVP speed change ratio γ _{CVP (α} = -θ) greater than the more or gear ratio γ _{CVP (α} = -θ) Become. At the contact P3, the spin loss is the smallest at the gear ratio γ _CVP (α = 0) {= 1} when the tilt angle α is 0, and the tilt angle α is larger than 0 or smaller than 0. That is, the higher the gear ratio γ _CVP is, or the smaller the ratio is, the greater the spin loss. Accordingly, in the continuously variable transmission 2, the spin loss increases as the tilt angle α becomes larger than the contact angle θ or the tilt angle α becomes larger than the contact angle −θ. On the other hand, in a region where the tilt angle α is smaller than the contact angle θ or a region where the tilt angle α is smaller than the contact angle −θ, the spin loss becomes smaller than the region where the spin loss increases.

そこで、この無段変速機２においては、スピン損失を小さくして動力伝達効率を高めるべく、スピン損失の小さい傾転角αで、つまり傾転角αが「−｜θ｜≦α≦｜θ｜」の範囲内に収まるよう電子制御装置（ＥＣＵ）１００に傾転機構６０を制御させる。   Therefore, in this continuously variable transmission 2, in order to reduce the spin loss and increase the power transmission efficiency, the tilt angle α with a small spin loss, that is, the tilt angle α is “− | θ | ≦ α ≦ | θ The tilting mechanism 60 is controlled by the electronic control unit (ECU) 100 so as to be within the range of “|”.

この無段変速機２においては、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御し、変速比γ_ＣＶＰを「γ_ＣＶＰ（α＝θ）≦γ_ＣＶＰ≦γ_ＣＶＰ（α＝−θ）」の範囲内に収めることで、動力伝達効率の良好な高効率領域の変速比γ_ＣＶＰで動力を伝達することができる。この無段変速機２は、その高効率領域において、変速比γ_ＣＶＰが１のとき（α＝０のとき）に最も動力伝達効率が良くなる。そして、この無段変速機２は、変速比γ_ＣＶＰが１よりも大きくなるにつれて又は小さくなるにつれて（換言するならば傾転角αが−θ又はθに近づくにつれて）、動力伝達効率が変速比γ_ＣＶＰの変化率に対して徐々に低下していく。一方、傾転角αが「α＞｜θ｜」又は「α≦−｜θ｜」の範囲内に制御され、変速比γ_ＣＶＰがγ_ＣＶＰ（α＝−θ）よりも大きくなる又はγ_ＣＶＰ（α＝θ）よりも小さくなると、その領域では、上記の高効率領域よりも、変速比γ_ＣＶＰの変化率に対する動力伝達効率の低下率が高く、僅かな変速比γ_ＣＶＰの変更で急激に動力伝達効率が悪くなる。図５には、この無段変速機２における変速比γ_ＣＶＰと動力伝達効率との対応関係を示している。 In this continuously variable transmission 2, the tilt angle α is controlled within the range of “− | θ | ≦ α ≦ | θ |”, and the gear ratio γ _{CVP is set} to “γ _CVP (α = θ) ≦ γ _CVP ≦ By being within the range of “γ _CVP (α = −θ)”, power can be transmitted with a gear ratio γ _CVP in a high efficiency region with good power transmission efficiency. This continuously variable transmission 2 has the highest power transmission efficiency in the high efficiency region when the gear ratio γ _CVP is 1 (when α = 0). The continuously variable transmission 2 has a power transmission efficiency that changes as the gear ratio γ _CVP becomes larger or smaller than 1 (in other words, as the tilt angle α approaches -θ or θ). It gradually decreases with respect to the rate of change of γ _CVP . On the other hand, the tilt angle α is controlled within the range of “α> | θ |” or “α ≦ − | θ |”, and the gear ratio γ _CVP becomes larger than γ _CVP (α = −θ) or γ _CVP. When it becomes smaller than (α = θ), the reduction rate of the power transmission efficiency with respect to the change rate of the transmission gear ratio γ _CVP is higher in that region than in the above high efficiency region, and abruptly changes with a slight change in the transmission gear ratio γ _CVP. The power transmission efficiency becomes worse. FIG. 5 shows a correspondence relationship between the speed ratio γ _CVP and the power transmission efficiency in the continuously variable transmission 2.

また、この無段変速機２は、傾転角αが−θよりも小さくなるにつれて又はθよりも大きくなるにつれて（つまり傾転角αの絶対値が｜θ｜よりも大きくなるにつれて）、その傾転角αの変化率に対する変速比γ_ＣＶＰの変化率が高くなっていく（図６）。これが為、その領域においては、傾転角αの変化に対して変速比γ_ＣＶＰが急速に変化することになり、均等に変化させることができないので、変速比γ_ＣＶＰの制御が難しい。しかしながら、この無段変速機２は、傾転角αが「−｜θ｜≦α≦｜θ｜」の範囲内であれば、その傾転角αの変化率に対する変速比γ_ＣＶＰの変化率を一定に保つことができるので、変速比γ_ＣＶＰの制御性に優れる。従って、変速比γ_ＣＶＰの制御性を向上させる上でも、この無段変速機２は、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御することが好ましい。 Further, the continuously variable transmission 2 has its tilt angle α smaller than −θ or larger than θ (that is, as the absolute value of the tilt angle α becomes larger than | θ |). The rate of change of the gear ratio γ _CVP with respect to the rate of change of the tilt angle α increases (FIG. 6). For this reason, in that region, the gear ratio γ _CVP changes rapidly with respect to the change in the tilt angle α and cannot be changed evenly, so it is difficult to control the gear ratio γ _CVP . However, in this continuously variable transmission 2, if the tilt angle α is in the range of “− | θ | ≦ α ≦ | θ |”, the rate of change of the gear ratio γ _CVP with respect to the rate of change of the tilt angle α. Can be kept constant, so that the controllability of the gear ratio γ _CVP is excellent. Therefore, in order to improve the controllability of the gear ratio γ _CVP, the continuously variable transmission 2 preferably controls the tilt angle α within the range of “− | θ | ≦ α ≦ | θ |”.

このように、この無段変速機２は、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御するように、即ち変速比γ_ＣＶＰを「γ_ＣＶＰ（α＝θ）≦γ_ＣＶＰ≦γ_ＣＶＰ（α＝−θ）」の範囲内で制御するように設定しているので、動力伝達効率と変速制御性の良好な変速比γ_ＣＶＰの領域のみが使われることになり、燃費や変速品質が向上する。 In this way, the continuously variable transmission 2 controls the tilt angle α within the range of “− | θ | ≦ α ≦ | θ |”, that is, the gear ratio γ _CVP is “γ _CVP (α = θ) ≦ γ _CVP ≦ γ _CVP (α = −θ) ”, so that only the region of the gear ratio γ _{CVP with} good power transmission efficiency and speed controllability is used. As a result, fuel economy and gear shifting quality are improved.

ところで、この変速装置１には、図１に示すように、複数の変速段を有する有段変速機３も設けている。その有段変速機３は、無段変速機２の出力側と駆動輪側との間に介在させている。ここでは、電子制御装置１００によって切り替えの制御が為される低速段７０と高速段８０の２つの変速段を備えている。   By the way, the transmission 1 is also provided with a stepped transmission 3 having a plurality of shift stages, as shown in FIG. The stepped transmission 3 is interposed between the output side of the continuously variable transmission 2 and the drive wheel side. Here, there are two shift stages, a low speed stage 70 and a high speed stage 80, which are controlled to be switched by the electronic control unit 100.

低速段７０は、出力軸２１と一体になって回転する低速用第１歯車７１と、この低速用第１歯車７１と噛み合う低速用第２歯車７２と、を有する。また、高速段８０は、出力軸２１と一体になって回転する高速用第１歯車８１と、この高速用第１歯車８１と噛み合う高速用第２歯車８２と、を有する。低速用第２歯車７２と高速用第２歯車８２は、変速装置１のケースＣＡの内側に回転自在に支持されている。   The low speed stage 70 includes a low speed first gear 71 that rotates integrally with the output shaft 21, and a low speed second gear 72 that meshes with the low speed first gear 71. The high-speed stage 80 includes a first high-speed gear 81 that rotates integrally with the output shaft 21, and a second high-speed gear 82 that meshes with the first high-speed gear 81. The low speed second gear 72 and the high speed second gear 82 are rotatably supported inside the case CA of the transmission 1.

この変速装置１においては、無段変速機２の変速比γ_ＣＶＰと有段変速機３の低速段７０の変速比γＬｏ又は高速段８０の変速比γＨｉとの積が最終的な変速比γになる（式４，５）。 In this transmission 1, the product of the speed ratio γ _CVP of the continuously variable transmission 2 and the speed ratio γLo of the low speed stage 70 or the speed ratio γHi of the high speed stage 80 of the stepped transmission 3 is the final speed ratio γ. (Equations 4 and 5).

γ＝γ_ＣＶＰ×γＬｏ … （４）
γ＝γ_ＣＶＰ×γＨｉ … （５） γ = γ _CVP × γLo (4)
γ = γ _CVP × γHi (5)

電子制御装置１００には、有段変速機３の低速段７０の使用域（以下、「有段低速域」と云う。）において、無段変速機２を上記の傾転角αの制御範囲内「−｜θ｜≦α≦｜θ｜」で制御させればよい。これにより、この変速装置１は、その有段低速域における動力伝達効率と変速制御性の良好な変速比γの領域のみが使用されることになる。これと同様に、この電子制御装置１００は、有段変速機３の高速段８０の使用域（以下、「有段高速域」と云う。）において、無段変速機２を上記の傾転角αの制御範囲内「−｜θ｜≦α≦｜θ｜」で制御すればよい。これにより、この変速装置１は、その有段高速域においても、有段高速域における動力伝達効率と変速制御性の良好な変速比γの領域のみが使用されることになる。   In the electronic control unit 100, the continuously variable transmission 2 is within the control range of the tilt angle α in the use range of the low speed stage 70 of the stepped transmission 3 (hereinafter referred to as “stepped low speed range”). Control may be performed with “− | θ | ≦ α ≦ | θ |”. As a result, the transmission 1 is used only in the region of the gear ratio γ with good power transmission efficiency and good shift controllability in the stepped low speed region. Similarly, the electronic control unit 100 causes the continuously variable transmission 2 to move at the tilt angle in the use range of the high speed stage 80 of the stepped transmission 3 (hereinafter referred to as “stepped high speed range”). Control may be performed within the range of α, “− | θ | ≦ α ≦ | θ |”. As a result, the speed change device 1 uses only the region of the gear ratio γ having good power transmission efficiency and speed controllability in the stepped high speed region even in the stepped high speed region.

有段低速域と有段高速域において最も動力伝達効率が良くなるのは、無段変速機２の変速比γ_ＣＶＰが１（α＝０）に制御されているときである（図７）。また、この変速装置１は、有段低速域と有段高速域の双方において、無段変速機２の変速比γ_ＣＶＰが１よりも大きくなるにつれて又は小さくなるにつれて（換言するならば無段変速機２の傾転角αが−θ又はθに近づくにつれて）、動力伝達効率が変速比γの変化率に対して徐々に低下していく。 The power transmission efficiency is most improved in the stepped low speed region and the stepped high speed region when the gear ratio γ _CVP of the continuously variable transmission 2 is controlled to 1 (α = 0) (FIG. 7). In addition, the speed change device 1 has a continuously variable speed change as the gear ratio γ _CVP of the continuously variable transmission 2 becomes larger or smaller than 1 in both the stepped low speed region and the stepped high speed region. As the tilt angle α of the machine 2 approaches −θ or θ), the power transmission efficiency gradually decreases with respect to the change rate of the speed ratio γ.

ここで、電子制御装置１００は、要求された変速装置１の変速比γに応じて低速段７０と高速段８０の切り替えを行う。その際、変速装置１は、変速比γを高効率領域に保持したままで低速段７０と高速段８０の切り替えを行うことが好ましい。   Here, the electronic control unit 100 switches between the low speed stage 70 and the high speed stage 80 in accordance with the requested speed ratio γ of the transmission 1. At this time, the transmission 1 preferably switches between the low speed stage 70 and the high speed stage 80 while maintaining the speed ratio γ in the high efficiency region.

そこで、電子制御装置１００には、変速装置１が低速段７０でアップシフト制御されている状態（つまり有段低速域で変速比γを小さくする為の無段変速機２の制御状態）であれば、無段変速機２の変速比γ_ＣＶＰがγ_ＣＶＰ（α＝θ）になったときに、その変速比γ_ＣＶＰをγ_ＣＶＰ（α＝−θ）に切り替えさせると共に、有段変速機３を低速段７０から高速段８０に切り替えさせればよい。また、この電子制御装置１００には、変速装置１が高速段８０でダウンシフト制御されている状態（つまり有段高速域で変速比γを大きくする為の無段変速機２の制御状態）であれば、無段変速機２の変速比γ_ＣＶＰがγ_ＣＶＰ（α＝−θ）になったときに、その変速比γ_ＣＶＰをγ_ＣＶＰ（α＝θ）に切り替えさせると共に、有段変速機３を高速段８０から低速段７０に切り替えさせればよい。これが為、この変速装置１は、図７に示す如く、その低速段７０と高速段８０とを切り替える際の変速比γ、つまり有段低速域で運転中の無段変速機２が変速比γ_ＣＶＰ（α＝θ）のときの変速比γ（α＝θ）と、有段高速域で運転中の無段変速機２が変速比γ_ＣＶＰ（α＝−θ）のときの変速比γ（α＝−θ）と、が同じ大きさになるように、無段変速機２の諸元（傾転角α、接触角θ、変速比γ_ＣＶＰ等）と有段変速機３の諸元（低速段７０と高速段８０の変速比γＬｏ、γＨｉ）を設定すればよい。 Therefore, the electronic control unit 100 may be in a state where the transmission 1 is upshift controlled at the low speed stage 70 (that is, the control state of the continuously variable transmission 2 for reducing the speed ratio γ in the stepped low speed range). For example, when the gear ratio γ _CVP of the continuously variable transmission 2 becomes γ _CVP (α = θ), the gear ratio γ _CVP is switched to γ _CVP (α = −θ) and the stepped transmission 3 May be switched from the low speed stage 70 to the high speed stage 80. Further, the electronic control unit 100 is in a state in which the transmission 1 is downshift controlled at the high speed stage 80 (that is, the control state of the continuously variable transmission 2 for increasing the speed ratio γ in the stepped high speed range). If present, when the gear ratio γ _CVP of the continuously variable transmission 2 becomes γ _CVP (α = −θ), the gear ratio γ _CVP is switched to γ _CVP (α = θ) and the stepped transmission 3 may be switched from the high speed stage 80 to the low speed stage 70. For this reason, as shown in FIG. 7, the transmission 1 has a transmission ratio γ when switching between the low speed stage 70 and the high speed stage 80, that is, the continuously variable transmission 2 operating in the stepped low speed range is changed to the transmission ratio γ. The transmission ratio γ (α = θ) when _CVP (α = θ) and the transmission ratio γ (when the continuously variable transmission 2 operating in the stepped high speed range is the transmission ratio γ _CVP (α = −θ). (α = −θ) and the specifications of the continuously variable transmission 2 (tilt angle α, contact angle θ, gear ratio γ _CVP, etc.) and the specifications of the stepped transmission 3 ( The speed ratio γLo, γHi) between the low speed stage 70 and the high speed stage 80 may be set.

更に、この変速装置１は、変速装置１が低速段７０でアップシフト制御されている状態において、無段変速機２の変速比γ_ＣＶＰがγ_ＣＶＰ（α＝θ）になる前に、その変速比γ_ＣＶＰを切り替え、且つ、有段変速機３を低速段７０から高速段８０に切り替えたとしても、変速比γを高効率領域に保持し続けることができる（図８）。また、この変速装置１は、変速装置１が高速段８０でダウンシフト制御されている状態において、変速比γ_ＣＶＰがγ_ＣＶＰ（α＝−θ）になる前に、その変速比γ_ＣＶＰを切り替え、且つ、有段変速機３を高速段８０から低速段７０に切り替えたとしても、変速比γを高効率領域に保持し続けることができる（図８）。この場合には、その低速段７０から切り替えるときの変速比γと高速段８０から切り替えるときの変速比γとが同じ大きさになるように、無段変速機２の諸元と有段変速機３の諸元を設定すればよい。 Further, the transmission 1 is shifted before the transmission ratio γ _CVP of the continuously variable transmission 2 becomes γ _CVP (α = θ) in a state where the transmission 1 is upshift controlled at the low speed stage 70. Even if the ratio γ _CVP is switched and the stepped transmission 3 is switched from the low speed stage 70 to the high speed stage 80, the speed ratio γ can be kept in the high efficiency region (FIG. 8). Further, the transmission 1 switches the transmission ratio γ _CVP before the transmission ratio γ _CVP becomes γ _CVP (α = −θ) in a state where the transmission 1 is downshift controlled at the high speed stage 80. Even if the stepped transmission 3 is switched from the high speed stage 80 to the low speed stage 70, the speed ratio γ can be kept in the high efficiency region (FIG. 8). In this case, the specifications of the continuously variable transmission 2 and the stepped transmission are set so that the speed ratio γ when switching from the low speed stage 70 and the speed ratio γ when switching from the high speed stage 80 are the same. It is only necessary to set 3 specifications.

従って、この変速装置１においては、変速比γを高効率領域のみで使う為、低速段７０及び高速段８０の変速比γＬｏ、γＨｉ、有段低速域で運転中の無段変速機２の変速比γ_ＣＶＰ（α＝θ）及び有段高速域で運転中の無段変速機２の変速比γ_ＣＶＰ（α＝−θ）が下記の式６の関係を満たすように、無段変速機２の諸元と有段変速機３の諸元を設定すればよい。つまり、この変速装置１は、有段低速域における変速比γ_ＣＶＰ（α＝θ）のときの変速比γ（α＝θ）｛＝γ_ＣＶＰ（α＝θ）×γＬｏ｝が有段高速域における変速比γ_ＣＶＰ（α＝−θ）のときの変速比γ（α＝−θ）｛＝γ_ＣＶＰ（α＝−θ）×γＨｉ｝以下になるように設定すればよい。尚、低速段７０と高速段８０の変速比γＬｏ、γＨｉは、「１＜（γＬｏ／γＨｉ）」の関係を有している。 Therefore, in this transmission 1, since the gear ratio γ is used only in the high efficiency region, the gear ratios γLo and γHi of the low speed stage 70 and the high speed stage 80, and the speed change of the continuously variable transmission 2 operating in the stepped low speed region. The continuously variable transmission 2 so that the ratio γ _CVP (α = θ) and the transmission ratio γ _CVP (α = −θ) of the continuously variable transmission 2 operating in the stepped high speed range satisfy the relationship of the following Expression 6. And the specifications of the stepped transmission 3 may be set. In other words, the transmission 1 has a gear ratio γ (α = θ) {= γ _CVP (α = θ) × γLo} at a gear ratio γ _CVP (α = θ) in a stepped low speed region. speed ratio γ (α = -θ) {= γ CVP (α = -θ) × γHi} may be set to be less than when the speed ratio γ _CVP (α = -θ) in. The gear ratios γLo and γHi between the low speed stage 70 and the high speed stage 80 have a relationship of “1 <(γLo / γHi)”.

（γＬｏ／γＨｉ）≦｛γ_ＣＶＰ（α＝−θ）／γ_ＣＶＰ（α＝θ）｝ … （６） (ΓLo / γHi) ≦ {γ _CVP (α = −θ) / γ _CVP (α = θ)} (6)

この式６においては、その変速比γ_ＣＶＰ（α＝θ）を有段低速域における「α＝θ」のときの無段変速機２の回転比γｄ１に置き換え、且つ、その変速比γ_ＣＶＰ（α＝−θ）を有段高速域における「α＝−θ」のときの無段変速機２の回転比γｄ２に置き換えてもよい。 In this equation 6, the gear ratio γ _CVP (α = θ) is replaced with the rotation ratio γd1 of the continuously variable transmission 2 when “α = θ” in the stepped low speed region, and the gear ratio γ _CVP ( α = −θ) may be replaced with the rotation ratio γd2 of the continuously variable transmission 2 when “α = −θ” in the stepped high speed range.

低速段７０と高速段８０とを切り替える際、無段変速機２は、傾転角αを傾転角α１（０＜α１≦θ）と傾転角α２（−θ≦α２＜０）との間で切り替える。その傾転角α１，α２は、「｜α１｜＝｜α２｜」の関係を有していることが望ましい。   When switching between the low speed stage 70 and the high speed stage 80, the continuously variable transmission 2 changes the tilt angle α between the tilt angle α1 (0 <α1 ≦ θ) and the tilt angle α2 (−θ ≦ α2 <0). Switch between. It is desirable that the tilt angles α1 and α2 have a relationship of “| α1 | = | α2 |”.

この変速装置１をアップシフトさせるとき及びダウンシフトさせるときの動作について、各々図９及び図１０のタイムチャートに基づき説明する。   Operations when the transmission 1 is upshifted and downshifted will be described based on the time charts of FIGS. 9 and 10, respectively.

アップシフト制御時には、低速段７０で運転しているときに、無段変速機２の傾転角αが負の値、０、正の値へと順に移り変わる。電子制御装置１００は、傾転角αがα１になったときに、傾転角αをα２に制御すると共に、有段変速機３を低速段７０から高速段８０に切り替える。そして、この電子制御装置１００は、アップシフト制御が続くのであれば、傾転角αをα２から０に近づけていき、接触角θと同一角度になるまで制御する。従って、この変速装置１は、図９の下図や図１１に示すように、単位時間当りの変速比変化率を一定に保ちながら、変速比γをγ（α＝−θ）からγ（α＝θ）の間でアップシフトできる。また、この変速装置１は、「（γＬｏ／γＨｉ）≦｛γ_ＣＶＰ（α＝−θ）／γ_ＣＶＰ（α＝θ）｝」の関係を満たすように設定しているので、低速段７０から高速段８０へと切り替えるときに、その切り替え前後で連続的な変速比γの変化、つまり段付きを抑えた無段階の変速比γの変化が可能になる。故に、この変速装置１は、アップシフト制御時の変速比γの制御性に優れる。 During upshift control, when the vehicle is operating at the low speed stage 70, the tilt angle α of the continuously variable transmission 2 changes in order from a negative value, 0, and a positive value. When the tilt angle α becomes α1, the electronic control unit 100 controls the tilt angle α to α2, and switches the stepped transmission 3 from the low speed stage 70 to the high speed stage 80. Then, if the upshift control continues, the electronic control unit 100 controls the tilt angle α from α2 to 0 and until it reaches the same angle as the contact angle θ. Therefore, as shown in the lower diagram of FIG. 9 and FIG. 11, the transmission 1 changes the transmission ratio γ from γ (α = −θ) to γ (α = α = −θ) while keeping the transmission ratio change rate per unit time constant. upshift between θ). The transmission 1 is set so as to satisfy the relationship of “(γLo / γHi) ≦ {γ _CVP (α = −θ) / γ _CVP (α = θ)}”. When switching to the high speed stage 80, it is possible to continuously change the speed ratio γ before and after the switching, that is, to change the stepless speed ratio γ while suppressing stepping. Therefore, the transmission 1 is excellent in controllability of the speed ratio γ during upshift control.

一方、ダウンシフト制御時には、高速段８０で運転しているときに、無段変速機２の傾転角αが正の値、０、負の値へと順に移り変わる。電子制御装置１００は、傾転角αがα２になったときに、傾転角αをα１に制御すると共に、有段変速機３を高速段８０から低速段７０に切り替える。そして、この電子制御装置１００は、ダウンシフト制御が続くのであれば、傾転角αをα１から０に近づけていき、−θになるまで制御する。従って、この変速装置１は、図１０の下図や図１１に示すように、単位時間当りの変速比変化率を一定に保ちながら、変速比γをγ（α＝θ）からγ（α＝−θ）の間でダウンシフトできる。また、この変速装置１は、「（γＬｏ／γＨｉ）≦｛γ_ＣＶＰ（α＝−θ）／γ_ＣＶＰ（α＝θ）｝」の関係を満たすように設定しているので、高速段８０から低速段７０へと切り替えるときに、その切り替え前後で連続的な変速比γの変化、つまり段付きを抑えた無段階の変速比γの変化が可能になる。故に、この変速装置１は、ダウンシフト制御時の変速比γの制御性に優れる。 On the other hand, during downshift control, when the vehicle is operating at the high speed stage 80, the tilt angle α of the continuously variable transmission 2 changes in order from a positive value, 0, and a negative value. When the tilt angle α becomes α2, the electronic control unit 100 controls the tilt angle α to α1 and switches the stepped transmission 3 from the high speed stage 80 to the low speed stage 70. Then, if the downshift control continues, the electronic control device 100 controls the tilt angle α from α1 to 0 until it reaches −θ. Therefore, as shown in the lower diagram of FIG. 10 and FIG. 11, the transmission 1 changes the gear ratio γ from γ (α = θ) to γ (α = −) while keeping the speed ratio change rate per unit time constant. downshift between (θ). The transmission 1 is set so as to satisfy the relationship of “(γLo / γHi) ≦ {γ _CVP (α = −θ) / γ _CVP (α = θ)}”. When switching to the low speed stage 70, it is possible to continuously change the speed ratio γ before and after the switching, that is, to change the stepless speed ratio γ while suppressing stepping. Therefore, the transmission 1 is excellent in controllability of the speed ratio γ during downshift control.

このように、この変速装置１は、傾転角αを「−｜θ｜≦α≦｜θ｜」の範囲内で制御するように設定し、且つ、「（γＬｏ／γＨｉ）≦｛γ_ＣＶＰ（α＝−θ）／γ_ＣＶＰ（α＝θ）｝」の関係を満たすように設定しているので、動力伝達効率と変速制御性の良好な変速比γの領域のみが使われることになり、燃費や変速品質が向上する。 Thus, the transmission 1 is set so that the tilt angle α is controlled within the range of “− | θ | ≦ α ≦ | θ |”, and “(γLo / γHi) ≦ {γ _CVP. (Α = −θ) / γ _CVP (α = θ)} ”is set so as to satisfy the relationship of“ α = −θ) / γ _CVP (α = θ)} ”. , Improve fuel economy and shift quality.

１ 変速装置
２ 無段変速機
３ 有段変速機
１０ 第１回転部材（第１部材）
１１ 入力軸
２０ 第２回転部材（第２部材）
２１ 出力軸
３０ サンローラ（第３部材）
４０ キャリア（第４部材）
５０ 遊星ボール（転動部材）
５１ 支持軸
６０ 傾転機構
７０ 低速段
７１ 低速用第１歯車
７２ 低速用第２歯車
８０ 高速段
８１ 高速用第１歯車
８２ 高速用第２歯車
１００ 電子制御装置
Ａ１ 第１中心軸
Ａ２ 第２中心軸
Ｇ 重心
Ｌ０ 基準線
Ｌ１，Ｌ２ 線
Ｌ３ 基準線
Ｐ１，Ｐ２，Ｐ３ 接点
α 傾転角
θ 接触角 DESCRIPTION OF SYMBOLS 1 Transmission device 2 Continuously variable transmission 3 Stepped transmission 10 First rotating member (first member)
11 Input shaft 20 Second rotating member (second member)
21 Output shaft 30 Sun roller (third member)
40 Carrier (4th member)
50 Planetary ball (rolling member)
51 Support shaft 60 Tilt mechanism 70 Low speed stage 71 Low speed first gear 72 Low speed second gear 80 High speed stage 81 High speed first gear 82 High speed second gear 100 Electronic control unit A1 First central axis A2 Second center Axis G Center of gravity L0 Reference line L1, L2 line L3 Reference line P1, P2, P3 Contact α Tilt angle θ Contact angle

Claims (2)

共通の第１中心軸上で対向させて配置し、該第１中心軸を中心とする相対回転が可能な第１及び第２の部材と、
前記第１中心軸と同心上で且つ前記第１部材と前記第２部材との間に配置した第３部材と、
前記第１中心軸と平行な第２中心軸及び回転中心となる当該第２中心軸上の重心を有し、前記第３部材の外周面上で前記第１中心軸を中心として放射状に複数配置すると共に、前記第１及び第２の部材との夫々の接点が前記第１中心軸から径方向外側に向けて同じ距離で且つ前記重心からも同じ距離となるように当該第１及び第２の部材に挟持させた転動部材と、
前記第２中心軸を有し、前記転動部材を回転自在に支持する支持軸と、
夫々の前記第２中心軸を前記第１中心軸に対して前記転動部材及び前記支持軸と共に傾転させる傾転機構と、
前記各支持軸を介して前記各転動部材を傾転動作が可能な状態で支持する第４部材と、
を備えた無段変速機を有し、
前記転動部材の重心から径方向に向けた基準線と当該転動部材の重心及び当該転動部材上の前記第１部材との接点を結ぶ線とが成す角度並びに前記基準線と前記転動部材の重心及び当該転動部材上の前記第２部材との接点を結ぶ線とが成す角度を接触角θとし、且つ、前記転動部材の重心を通る前記第１中心軸と平行な線に対する前記第２中心軸の成す角度を傾転角αとし、その傾転角αが「−｜θ｜≦α≦｜θ｜」の範囲内に収まるよう前記傾転機構を制御することを特徴とした変速装置。 A first member and a second member disposed opposite to each other on a common first central axis and capable of relative rotation about the first central axis;
A third member disposed concentrically with the first central axis and between the first member and the second member;
A second central axis parallel to the first central axis and a center of gravity on the second central axis serving as a rotation center, and a plurality of radial arrangements about the first central axis on the outer peripheral surface of the third member In addition, the first and second members are arranged such that the respective contacts with the first and second members have the same distance from the first central axis outward in the radial direction and the same distance from the center of gravity. A rolling member sandwiched between members;
A support shaft having the second central axis and rotatably supporting the rolling member;
A tilt mechanism that tilts each of the second central axes with the rolling member and the support shaft with respect to the first central axis;
A fourth member that supports each rolling member in a state capable of tilting operation via each support shaft;
Having a continuously variable transmission with
The angle formed by the reference line extending in the radial direction from the center of gravity of the rolling member and the line connecting the center of gravity of the rolling member and the contact point of the first member on the rolling member, and the reference line and the rolling The angle formed by the center of gravity of the member and the line connecting the contact point with the second member on the rolling member is defined as a contact angle θ, and the line parallel to the first central axis passing through the center of gravity of the rolling member An angle formed by the second central axis is defined as a tilt angle α, and the tilt mechanism is controlled so that the tilt angle α is within a range of “− | θ | ≦ α ≦ | θ |”. Gearbox. 前記第２部材と一体になって回転する低速用第１歯車及び当該低速用第１歯車に噛み合う低速用第２歯車を備えた低速段と、前記第２部材と一体になって回転する高速用第１歯車及び当該高速用第１歯車に噛み合う高速用第２歯車を備えた高速段と、を有する有段変速機を設け、
前記有段変速機が前記低速段のときで且つ前記無段変速機の傾転角αが「α＝θ」のときの当該無段変速機における前記第１部材と前記第２部材との間の回転比をγｄ１、前記有段変速機が前記高速段のときで且つ前記無段変速機の傾転角αが「α＝−θ」のときの当該無段変速機における前記第１部材と前記第２部材との間の回転比をγｄ２、前記有段変速機の低速段の変速比をγＬｏ、前記有段変速機の高速段の変速比をγＨｉとし、これらが「（γＬｏ／γＨｉ）≦（γｄ２／γｄ１）」の関係を満たすことを特徴とした請求項１記載の変速装置。 A low-speed stage including a first low-speed gear that rotates integrally with the second member and a second low-speed gear that meshes with the first low-speed gear; and a high-speed rotation that rotates integrally with the second member A stepped transmission having a first gear and a high-speed stage provided with a second high-speed gear meshing with the first high-speed gear;
Between the first member and the second member in the continuously variable transmission when the stepped transmission is at the low speed and the tilt angle α of the continuously variable transmission is “α = θ”. The first member in the continuously variable transmission when the stepped transmission is at the high speed and the tilt angle α of the continuously variable transmission is “α = −θ”. The rotation ratio between the second member and the second member is γd2, the low speed gear ratio of the stepped transmission is γLo, and the high speed gear ratio of the stepped transmission is γHi. These are “(γLo / γHi)”. 2. The transmission according to claim 1, wherein a relationship of ≦ (γd2 / γd1) ”is satisfied.

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