JP2013072533A5

JP2013072533A5 -

Info

Publication number: JP2013072533A5
Application number: JP2011213784A
Authority: JP
Filing date: 2011-09-29
Publication date: 2014-11-06
Anticipated expiration: 2031-09-29

Description

Continuously variable transmission

この発明は、変速比を変更する為の変速機構としてトロイダル型無段変速機を組み込み、自動車用の自動変速機として使用する無段変速装置の改良に関する。具体的には、小型に構成できて限られた空間に設置し易く、しかも優れた伝達効率を有する、前置エンジン前輪駆動車（ＦＦ車）用として好適な構造を実現するものである。 The present invention relates to an improvement in a continuously variable transmission that incorporates a toroidal type continuously variable transmission as a transmission mechanism for changing a transmission ratio and is used as an automatic transmission for an automobile. Specifically, a structure suitable for a front engine front wheel drive vehicle (FF vehicle) that can be configured in a small size, can be easily installed in a limited space, and has excellent transmission efficiency is realized.

変速機構としてトロイダル型無段変速機を組み込み、比較的小型に構成できるＦＦ車用の自動変速機として、特許文献１に記載されたものが知られている。図５は、この特許文献１に記載された無段変速装置の原理を示している。この無段変速装置は、動力の伝達方向に関して上流側から順番に、入力回転軸１と、第一中間回転伝達軸２と、アイドラ軸３と、第二中間回転伝達軸４と、出力回転軸５とを互いに平行に設けている。このうちの入力回転軸１は、駆動源である図示しないエンジンにより、トルクコンバータ等の発進クラッチ６を介して一方向に回転駆動される。この様な前記入力回転軸１の周囲に、トロイダル型無段変速機７を設けている。この入力回転軸１の回転は、１対の入力ディスク８、８と図示しないパワーローラとを介して出力ディスク９に伝わり、この出力ディスク９の回転が、入力側歯車伝達機構１０を介して、前記第一中間回転伝達軸２に伝達される。次に、この第一中間回転伝達軸２の回転は、前進用クラッチ１１及び前進用歯車伝達機構１２を介して、又は、後退用クラッチ１３及び後退用歯車伝達機構１４を介して、前記第二中間回転伝達軸４に伝達される。更に、この第二中間回転伝達軸４の回転は、出力側歯車伝達機構１５を介して、デファレンシャルギヤ１６の入力部に伝達され、このデファレンシャルギヤ１６の出力部である、前記出力回転軸５が回転駆動される。車両を前進させる場合には、前記前進用クラッチ１１を接続すると共に、前記後退用クラッチ１３の接続を断つ。これに対して、車両を後退させる場合には、この後退用クラッチ１３を接続すると共に、前記前進用クラッチ１１の接続を断つ。 As an automatic transmission for an FF vehicle that incorporates a toroidal-type continuously variable transmission as a transmission mechanism and can be made relatively small, an automatic transmission described in Patent Document 1 is known. FIG. 5 shows the principle of the continuously variable transmission described in Patent Document 1. The continuously variable transmission includes an input rotation shaft 1, a first intermediate rotation transmission shaft 2, an idler shaft 3, a second intermediate rotation transmission shaft 4, and an output rotation shaft in order from the upstream side in the power transmission direction. 5 are provided in parallel with each other. Among these, the input rotating shaft 1 is rotationally driven in one direction by a starting clutch 6 such as a torque converter by an engine (not shown) as a driving source. A toroidal continuously variable transmission 7 is provided around the input rotary shaft 1. The rotation of the input rotary shaft 1 is transmitted to the output disk 9 via a pair of input disks 8 and 8 and a power roller (not shown). The rotation of the output disk 9 is transmitted via the input side gear transmission mechanism 10. It is transmitted to the first intermediate rotation transmission shaft 2. Next, the rotation of the first intermediate rotation transmission shaft 2 is performed via the forward clutch 11 and the forward gear transmission mechanism 12, or via the reverse clutch 13 and the reverse gear transmission mechanism 14. It is transmitted to the intermediate rotation transmission shaft 4. Further, the rotation of the second intermediate rotation transmission shaft 4 is transmitted to the input portion of the differential gear 16 via the output side gear transmission mechanism 15, and the output rotation shaft 5, which is the output portion of the differential gear 16, Driven by rotation. When the vehicle is advanced, the forward clutch 11 is connected and the reverse clutch 13 is disconnected. On the other hand, when the vehicle is moved backward, the reverse clutch 13 is connected and the forward clutch 11 is disconnected.

上述の図５に示した様な無段変速装置の場合、比較的小型に構成できるとは言え、互いに平行な５本の軸１〜５を備えており、未だ十分な小型・軽量化を図れるとは言えない。前記発進クラッチ６と前記トロイダル型無段変速機７との間に逆転機構を設ける事も考えられるが、この場合には前記トロイダル型無段変速機７を両方向に回転させる必要が生じ、このトロイダル型無段変速機７の制御が面倒になる。 In the case of the continuously variable transmission as shown in FIG. 5 described above, although it can be configured relatively small, it is provided with five shafts 1 to 5 parallel to each other, and can still be sufficiently reduced in size and weight. It can not be said. Although it is conceivable to provide a reverse rotation mechanism between the starting clutch 6 and the toroidal continuously variable transmission 7, in this case, it is necessary to rotate the toroidal continuously variable transmission 7 in both directions. Control of the type continuously variable transmission 7 becomes troublesome.

特開２００８−７５８６３号公報JP 2008-75863 A

本発明は、上述の様な事情に鑑み、トロイダル型無段変速機の制御を面倒にする事なく、入力部と出力部との間に配置する軸の数を少なく抑えて、より小型且つ軽量に構成できる無段変速装置の構造を実現すべく発明したものである。 In view of the circumstances as described above, the present invention reduces the number of shafts arranged between the input unit and the output unit without making troublesome control of the toroidal type continuously variable transmission, and is smaller and lighter. Invented to realize the structure of a continuously variable transmission that can be configured as follows.

本発明の無段変速装置は、入力回転軸と、トロイダル型無段変速機と、出力回転軸と、中間回転伝達軸と、前進用、後退用両遊星歯車機構と、入力側動力伝達機構と、クラッチ装置と、出力側動力伝達機構とを備える。
このうちの入力回転軸は、エンジン等の駆動源により回転駆動される。
又、前記トロイダル型無段変速機は、前記入力回転軸の周囲に、この入力回転軸と同心に設けられて、この入力回転軸をその入力部として運転される。
又、前記出力回転軸は、この入力回転軸と平行に設けられ、例えば、回転に伴って左右１対の駆動輪を回転駆動する。
又、前記中間回転伝達軸は、動力の伝達方向に関して前記入力回転軸と前記出力回転軸との間部分に、これら入力回転軸及び出力回転軸と平行に設けられている。
又、前記前進用、後退用両遊星歯車機構は、中間回転伝達軸の周囲に設けられている。
又、前記入力側動力伝達機構は、前記トロイダル型無段変速機の出力部と前記両遊星歯車機構の入力部との間に設けられている。
又、前記クラッチ装置は、その切換に伴って、前記両遊星歯車機構のうちの何れか一方の遊星歯車機構を前記トロイダル型無段変速機の出力部と前記出力回転軸との間の動力伝達経路中に組み込み、他方の遊星歯車機構をこの動力伝達経路中から切り離す機能を有する。
更に、前記出力側動力伝達機構は、前記両遊星歯車機構の出力部と前記出力回転軸との間に設けられている。
又、前記クラッチ装置は、具体的には、前進時に接続され後退時に切断される前進用クラッチと、後退時に接続され前進時に切断される後退用クラッチとにより構成する事ができる。 A continuously variable transmission according to the present invention includes an input rotation shaft, a toroidal continuously variable transmission, an output rotation shaft, an intermediate rotation transmission shaft, both forward and reverse planetary gear mechanisms, an input side power transmission mechanism, And a clutch device and an output side power transmission mechanism.
Of these, the input rotation shaft is rotationally driven by a drive source such as an engine.
The toroidal continuously variable transmission is provided around the input rotation shaft and concentric with the input rotation shaft, and is operated with the input rotation shaft as an input section.
The output rotation shaft is provided in parallel with the input rotation shaft, and for example, rotationally drives a pair of left and right drive wheels with rotation.
The intermediate rotation transmission shaft is provided in a portion between the input rotation shaft and the output rotation shaft in parallel with the input rotation shaft and the output rotation shaft in the power transmission direction.
The forward and reverse planetary gear mechanisms are provided around the intermediate rotation transmission shaft.
The input side power transmission mechanism is provided between the output part of the toroidal type continuously variable transmission and the input parts of the planetary gear mechanisms.
Further, the clutch device, when switched, transmits one of the planetary gear mechanisms to the power transmission between the output portion of the toroidal continuously variable transmission and the output rotating shaft. It is incorporated in the path and has a function of separating the other planetary gear mechanism from the power transmission path.
Furthermore, the output side power transmission mechanism is provided between the output portions of the planetary gear mechanisms and the output rotation shaft.
Specifically, the clutch device can be constituted by a forward clutch that is connected at the time of forward movement and disconnected at the time of backward movement, and a reverse clutch that is connected at the time of backward movement and disconnected at the time of forward movement.

上述の様な本発明の無段変速装置を実施する場合に、具体的には、例えば請求項２に記載した発明の様に、前記前進用、後退用両遊星歯車機構を、固定部分に支持されて回転しないキャリアを備え、これら両遊星歯車機構は何れも、前記中間回転伝達軸と共に回転する太陽歯車と、それぞれの太陽歯車の周囲に配置されたリング歯車と、それぞれの太陽歯車とリング歯車との間に設けられた複数の遊星歯車とを備えたものとする。そして、何れか一方の遊星歯車機構を、各遊星歯車を前記太陽歯車と前記リング歯車との両方の歯車に噛合させるシングルピニオン型とし、他方の遊星歯車機構を、各遊星歯車毎に１対ずつ設けた遊星歯車素子を互いに噛合させると共に、一方の遊星歯車素子を前記太陽歯車に、他方の遊星歯車素子を前記リング歯車に、それぞれ噛合させたダブルピニオン型とする。When implementing the continuously variable transmission of the present invention as described above, specifically, as in the invention described in claim 2, for example, the forward and reverse planetary gear mechanisms are supported by a fixed portion. Each of the planetary gear mechanisms includes a sun gear that rotates together with the intermediate rotation transmission shaft, a ring gear that is disposed around each sun gear, and each sun gear and ring gear. And a plurality of planetary gears provided between the two. One of the planetary gear mechanisms is a single pinion type in which each planetary gear meshes with both the sun gear and the ring gear, and the other planetary gear mechanism is paired for each planetary gear. The planetary gear elements provided are meshed with each other, and one planetary gear element is meshed with the sun gear, and the other planetary gear element is meshed with the ring gear.
この様な請求項２に記載した発明を実施する場合に好ましくは、請求項３に記載した発明の様に、前記シングルピニオン型の遊星歯車機構を構成する各遊星歯車と、前記ダブルピニオン型の遊星歯車機構を構成する各遊星歯車素子のうち、前記リング歯車と噛合している各遊星歯車素子とを同期した回転を自在に結合する事により、前記前進用、後退用両遊星歯車機構で１個のリング歯車を共用する。When implementing the invention described in claim 2, preferably, as in the invention described in claim 3, each planetary gear constituting the single-pinion type planetary gear mechanism, and the double-pinion type Of the planetary gear elements constituting the planetary gear mechanism, the planetary gear elements meshing with the ring gear are freely coupled to rotate synchronously, so that both the forward and reverse planetary gear mechanisms are 1 Shared ring gears.
又、上述の様な請求項１〜２に記載した無段変速装置を実施する場合に、例えば請求項４に記載した発明の様に、前記前進用、後退用両クラッチを、前記前進用、後退用両遊星歯車機構を構成する１対のリング歯車と、前記出力側伝達機構との間にそれぞれ設ける。Further, when the continuously variable transmission described in claims 1 and 2 as described above is implemented, for example, as in the invention described in claim 4, the forward and reverse clutches are used for the forward, Provided between a pair of ring gears constituting the reverse planetary gear mechanism and the output side transmission mechanism.

或いは、本発明の無段変速装置を実施する場合には、例えば請求項５に記載した発明の様に、前記前進用、後退用両遊星歯車機構を何れも、前記トロイダル型無段変速機の出力部の回転に伴って回転する太陽歯車と、それぞれの太陽歯車の周囲に配置されたリング歯車と、それぞれの太陽歯車とリング歯車との間に設けられ、それぞれがこれら太陽歯車とリング歯車との両方の歯車に噛合した複数の遊星歯車とを備えたシングルピニオン型とする。そして、前記両遊星歯車機構のうちの一方の遊星歯車機構を、キャリアが固定されていて前記リング歯車の回転を前記出力回転軸に伝達するものとし、他方の遊星歯車機構を、前記リング歯車が固定されていてキャリアの回転を前記出力回転軸に伝達するものとする。Alternatively, when the continuously variable transmission according to the present invention is implemented, for example, as in the invention described in claim 5, both the forward and reverse planetary gear mechanisms are provided in the toroidal continuously variable transmission. A sun gear that rotates as the output unit rotates, a ring gear that is disposed around each sun gear, and a sun gear and a ring gear that are provided between the sun gear and the ring gear. And a single pinion type having a plurality of planetary gears meshed with both gears. And one planetary gear mechanism of the two planetary gear mechanisms has a carrier fixed to transmit the rotation of the ring gear to the output rotating shaft, and the other planetary gear mechanism is connected to the ring gear. It is assumed that the rotation of the carrier is transmitted to the output rotation shaft.

上述の様な請求項３又は５に記載した無段変速装置を実施する場合には、例えば請求項６に記載した発明の様に、前記前進用、後退用両クラッチを、前記トロイダル型無段変速機の出力部と、前記前進用、後退用両遊星歯車機構を構成する１対の太陽歯車との間にそれぞれ設ける。When implementing the continuously variable transmission described in claim 3 or 5 as described above, for example, as in the invention described in claim 6, both the forward and reverse clutches are connected to the toroidal type continuously variable transmission. It is provided between the output portion of the transmission and a pair of sun gears constituting the forward and reverse planetary gear mechanisms.
この様な請求項６に記載した発明を実施する場合に好ましくは、請求項７に記載した発明の様に、前記中間回転伝達軸を、内径側回転伝達軸と、この内径側回転伝達軸の中間部周囲に、この内径側回転伝達軸に対する相対回転を可能に配置された、円管状の外径側回転伝達軸とから成る二重構造とする。そして、前記前進用、後退用両遊星歯車機構を構成する１対の太陽歯車を、それぞれ前記内径側回転伝達軸又は前記外径側回転伝達軸の一部に、当該回転伝達軸と同期した回転を自在に設置し、前記前進用、後退用両クラッチを、それぞれ前記内径側回転伝達軸又は前記外径側回転伝達軸と前記トロイダル型無段変速機の出力部との間に設ける。When the invention described in claim 6 is implemented, preferably, as in the invention described in claim 7, the intermediate rotation transmission shaft includes an inner diameter side rotation transmission shaft and an inner diameter side rotation transmission shaft. A double structure including a circular outer-diameter-side rotation transmission shaft disposed around the middle portion so as to be capable of relative rotation with respect to the inner-diameter-side rotation transmission shaft. Then, a pair of sun gears constituting the forward and reverse planetary gear mechanisms are respectively rotated on a part of the inner diameter side rotation transmission shaft or the outer diameter side rotation transmission shaft in synchronization with the rotation transmission shaft. The forward and reverse clutches are respectively provided between the inner diameter side rotation transmission shaft or the outer diameter side rotation transmission shaft and the output part of the toroidal continuously variable transmission.

上述の様な請求項１〜３、５〜７に記載した無段変速装置を実施する場合、例えば請求項８に記載した発明の様に、前記入力側動力伝達機構を、前記トロイダル型無段変速機の出力部に設けられた出力部材を含んで構成されるものとし、前記中間回転伝達軸の軸方向に関して、前記クラッチ装置と前記前進用、後退用両遊星歯車機構とを、互いに反対側に配置する。When implementing the continuously variable transmission according to any one of claims 1 to 3 and 5 to 7 as described above, for example, as in the invention according to claim 8, the input side power transmission mechanism is connected to the toroidal type continuously variable transmission. An output member provided at an output portion of the transmission is configured, and the clutch device and the forward and reverse planetary gear mechanisms are opposite to each other with respect to the axial direction of the intermediate rotation transmission shaft. To place.

上述の様な本発明の無段変速装置を実施する場合に好ましくは、請求項９に記載した発明の様に、出力側動力伝達機構を、デファレンシャルギヤを含んで構成されたものとし、前記クラッチ装置の切換に伴って、前記前進用、後退用両遊星歯車機構のうちの何れか一方の遊星歯車機構の出力部により前記デファレンシャルギヤの入力部を回転駆動し、このデファレンシャルギヤの出力部により、左右１対の出力回転軸を回転駆動する。Preferably, when the continuously variable transmission of the present invention as described above is implemented, the output side power transmission mechanism is configured to include a differential gear as in the invention described in claim 9, and the clutch Along with the switching of the device, the input portion of the differential gear is rotated by the output portion of one of the forward and reverse planetary gear mechanisms, and the output portion of the differential gear, A pair of left and right output rotation shafts are driven to rotate.

上述の様に構成する本発明によれば、入力回転軸を一方向に回転させた状態のまま、出力回転軸を両方向に回転させられる無段変速装置を、これら入力、出力両回転軸に加えて中間回転伝達軸を加えたのみの、３軸構造により実現できる。この為、前述の図５に示した様な５軸構造の無段変速装置に比べて、大幅な小型・軽量化が可能になる。又、トロイダル型無段変速機の回転方向を変更する必要もない為、このトロイダル型無段変速機の制御が面倒になる事もない。 According to the present invention configured as described above, a continuously variable transmission that can rotate the output rotation shaft in both directions while the input rotation shaft is rotated in one direction is added to both the input and output rotation shafts. This can be realized by a three-axis structure in which an intermediate rotation transmission shaft is added. Therefore, it is possible to significantly reduce the size and weight as compared with the continuously variable transmission having the five-shaft structure as shown in FIG. Further, since it is not necessary to change the rotation direction of the toroidal continuously variable transmission, the control of the toroidal continuously variable transmission is not troublesome.

本発明の実施の形態の第１例を示す略断面図。1 is a schematic cross-sectional view showing a first example of an embodiment of the present invention. 同第２例を示す略断面図。The schematic sectional drawing which shows the 2nd example. 同第３例を示す略断面図。Sectional drawing which shows the 3rd example. 同第４例を示す略断面図。Sectional drawing which shows the 4th example. 従来構造の１例を示す略断面図。FIG. 6 is a schematic cross-sectional view showing an example of a conventional structure.

［実施の形態の第１例］
図１は、請求項１、２、４、９に対応する、本発明の実施の形態の第１例を示している。尚、本例を含めて本発明の特徴は、入力回転軸１の周囲に設けたトロイダル型無段変速機７の出力部と、出力回転軸５を設けたデファレンシャルギヤ１６との間に設けられた、前後進切換機構を備えた動力伝達機構部分の構造にある。前記トロイダル型無段変速機７及びデファレンシャルギヤ１６を含めて、その他の部分の構造及び作用は、従来から広く知られている為、詳しい図示並びに説明は省略乃至簡略にし、以下、本例の特徴部分を中心に説明する。 [First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1, 2, 4 and 9. The features of the present invention including this example are provided between the output portion of the toroidal-type continuously variable transmission 7 provided around the input rotary shaft 1 and the differential gear 16 provided with the output rotary shaft 5. Further, the power transmission mechanism portion having a forward / reverse switching mechanism is provided. Since the structure and operation of the other parts including the toroidal-type continuously variable transmission 7 and the differential gear 16 have been widely known in the past, detailed illustration and description will be omitted or simplified. The explanation will focus on the part.

前記トロイダル型無段変速機７と前記デファレンシャルギヤ１６との間部分に中間回転伝達軸１７を、前記入力回転軸１及び前記出力回転軸５と平行に設けている。そして、前記トロイダル型無段変速機７の出力部である、出力ディスク９の回転を、入力側歯車伝達機構１０ａにより、前記中間回転伝達軸１７に伝達自在としている。本例の場合、これら出力ディスク９と入力側歯車伝達機構１０ａとの間に設ける入力側動力伝達機構として歯車式のものを使用しているが、チェンとスプロケットとから成る構造等、歯車式以外の構造を採用する事もできる。何れにしても、前記中間回転伝達軸１７の周囲に、前進用、後退用、２組の遊星歯車機構１８、１９を設けている。 An intermediate rotation transmission shaft 17 is provided in parallel with the input rotation shaft 1 and the output rotation shaft 5 at a portion between the toroidal type continuously variable transmission 7 and the differential gear 16. The rotation of the output disk 9, which is the output portion of the toroidal-type continuously variable transmission 7, can be transmitted to the intermediate rotation transmission shaft 17 by the input side gear transmission mechanism 10a. In the case of this example, a gear type is used as the input side power transmission mechanism provided between the output disk 9 and the input side gear transmission mechanism 10a. However, other than the gear type, such as a structure comprising a chain and a sprocket, etc. The structure of can also be adopted. In any case, two sets of planetary gear mechanisms 18 and 19 for forward movement and backward movement are provided around the intermediate rotation transmission shaft 17.

これら両遊星歯車機構１８、１９は、共通のキャリア２０を備えており、このキャリア２０は、変速装置のケーシングの内部に設けた取付部等の固定部分に支持固定されて回転しない。又、前記中間伝達軸１７の中間部先端寄り部分に前進用太陽歯車２１を、同じく先端部に後退用太陽歯車２２を、それぞれ前記中間伝達軸１７と同期した回転を自在に組み付けている。又、このうちの前進用太陽歯車２１の周囲に前進用リング歯車２３を、同じく後退用太陽歯車２２の周囲に後退用リング歯車２４を、それぞれこれら両太陽歯車２１、２２と同心に、互いに独立した回転を自在に配置している。 Both the planetary gear mechanisms 18 and 19 are provided with a common carrier 20, and the carrier 20 is supported and fixed to a fixing portion such as an attachment provided inside the casing of the transmission and does not rotate. Further, the forward sun gear 21 is attached to the intermediate transmission shaft 17 near the tip of the intermediate portion, and the reverse sun gear 22 is similarly attached to the tip portion of the intermediate transmission shaft 17 so as to freely rotate in synchronization with the intermediate transmission shaft 17. Of these, the forward ring gear 23 is provided around the forward sun gear 21, and the reverse ring gear 24 is provided around the backward sun gear 22. Rotation is arranged freely.

そして、前記前進用太陽歯車２１と前記前進用リング歯車２３とに、前記キャリア２０の先端寄り（図１の左寄り）部分に回転自在に支持した、複数個（３〜４個）の前進用遊星歯車２５、２５を噛合させて、シングルピニオン型である、前記前進用遊星歯車機構１８を構成している。これに対して、前記後退用太陽歯車２２と前記後退用リング歯車２４とに、前記キャリア２０の基端寄り（図１の右寄り）部分に回転自在に支持した、複数組（３〜４組）の後退用遊星歯車２６、２６を設置している。これら各後退用遊星歯車２６、２６は、それぞれ１組ずつの遊星歯車素子２７ａ、２７ｂから成る。これら各組の遊星歯車素子２７ａ、２７ｂは、互いに噛合すると共に、一方（前記後退用遊星歯車機構１９の径方向に関して内側）の遊星歯車素子２７ａ、２７ａを前記後退用太陽歯車２２に、他方（前記後退用遊星歯車機構１９の径方向に関して外側）の遊星歯車素子２７ｂ、２７ｂを前記後退用リング歯車２４に、それぞれ噛合させて、ダブルピニオン型の、前記後退用遊星歯車機構１９を構成している。 A plurality (3 to 4) of forward planets that are rotatably supported by the forward sun gear 21 and the forward ring gear 23 at a portion near the tip (left side in FIG. 1) of the carrier 20. The forward planetary gear mechanism 18 of a single pinion type is configured by meshing the gears 25, 25. On the other hand, a plurality of sets (three to four sets) are rotatably supported by the retreating sun gear 22 and the retreating ring gear 24 at a portion near the base end (rightward in FIG. 1) of the carrier 20. The reverse planetary gears 26, 26 are installed. Each of the reverse planetary gears 26 and 26 includes a set of planetary gear elements 27a and 27b. These sets of planetary gear elements 27a and 27b mesh with each other, and one (inner side in the radial direction of the reverse planetary gear mechanism 19) one planetary gear element 27a and 27a is used as the reverse sun gear 22 and the other ( The planetary gear elements 27b and 27b on the outer side in the radial direction of the reverse planetary gear mechanism 19 are respectively meshed with the reverse ring gear 24 to constitute the double-pinion type reverse planetary gear mechanism 19. Yes.

上述の様に、前記前進用遊星歯車機構１８をシングルピニオン型とし、前記後退用遊星歯車機構１９をダブルピニオン型とすると共に、これら両遊星歯車機構１８、１９の太陽歯車２１、２２を、前記中間回転伝達軸１７と共に、互いに同方向に回転する様にしている。この為、前記前進用遊星歯車機構１８を構成する前進用リング歯車２３と、前記後退用遊星歯車機構１９を構成する後退用リング歯車２４とは、互いに逆方向に回転する。そこで、これら両リング歯車２３、２４の回転を、選択的に前記デファレンシャルギヤ１６に、出力側歯車伝達機構１５ａを通じて取り出し自在としている。この為に本例の場合には、前記前進用リング歯車２３と前記出力側歯車伝達機構１５ａとの間に前進用クラッチ２８を、前記後退用リング歯車２４とこの出力側歯車伝達機構１５ａとの間に後退用クラッチ２９を、それぞれ設けている。これら両クラッチ２８、２９は、多板クラッチ等、十分なトルク伝達容量を備えたもので、一方のクラッチ２８（２９）が接続された場合には、他方のクラッチ２９（２８）の接続が断たれる。両方のクラッチ２８、２９の接続が断たれる瞬間はあっても、両方のクラッチ２８、２９が同時に接続される事はない。 As described above, the forward planetary gear mechanism 18 is a single pinion type, the reverse planetary gear mechanism 19 is a double pinion type, and the sun gears 21 and 22 of both the planetary gear mechanisms 18 and 19 are The intermediate rotation transmission shaft 17 and the intermediate rotation transmission shaft 17 rotate in the same direction. For this reason, the forward ring gear 23 constituting the forward planetary gear mechanism 18 and the backward ring gear 24 constituting the backward planetary gear mechanism 19 rotate in opposite directions. Therefore, the rotations of both the ring gears 23 and 24 can be selectively taken out to the differential gear 16 through the output side gear transmission mechanism 15a. Therefore, in the case of this example, a forward clutch 28 is provided between the forward ring gear 23 and the output side gear transmission mechanism 15a, and the reverse ring gear 24 and the output side gear transmission mechanism 15a. A reverse clutch 29 is provided between them. These clutches 28 and 29 have a sufficient torque transmission capacity, such as a multi-plate clutch. When one clutch 28 (29) is connected, the other clutch 29 (28) is disconnected. Be drunk. Even if there is a moment when both clutches 28 and 29 are disconnected, both clutches 28 and 29 are not simultaneously connected.

上述の様な本例の無段変速装置の場合、車両を前進させる際には、前記前進用クラッチ２８を接続すると共に、前記後退用クラッチ２９の接続を断つ。この状態では、前記トロイダル型無段変速機７を構成する、前記出力ディスク９から前記中間回転伝達軸１７に伝えられた回転が、前記前進用遊星歯車機構１８と、前記前進用クラッチ２８と、前記出力側歯車伝達機構１５ａとを介して前記デファレンシャルギヤ１６に伝達され、このデファレンシャルギヤ１６の出力部に設けた左右１対の出力回転軸５、５を同方向に回転させて、図示しない駆動輪を前進方向に回転駆動する。これに対して、車両を後退させる際には、前記後退用クラッチ２９を接続すると共に、前記前進用クラッチ２８の接続を断つ。この状態では、前記中間回転伝達軸１７の回転が、前記後退用遊星歯車機構１９と、前記後退用クラッチ２９と、前記出力側歯車伝達機構１５ａとを介して前記デファレンシャルギヤ１６に伝達され、前記駆動輪を後退方向に回転駆動する。 In the case of the continuously variable transmission of this example as described above, when the vehicle is advanced, the forward clutch 28 is connected and the reverse clutch 29 is disconnected. In this state, the rotation transmitted from the output disk 9 to the intermediate rotation transmission shaft 17 constituting the toroidal-type continuously variable transmission 7 is converted into the forward planetary gear mechanism 18, the forward clutch 28, A drive (not shown) is transmitted to the differential gear 16 via the output gear transmission mechanism 15a, and a pair of left and right output rotating shafts 5 and 5 provided at the output portion of the differential gear 16 are rotated in the same direction. The wheel is driven to rotate in the forward direction. On the other hand, when the vehicle is moved backward, the reverse clutch 29 is connected and the forward clutch 28 is disconnected. In this state, the rotation of the intermediate rotation transmission shaft 17 is transmitted to the differential gear 16 via the reverse planetary gear mechanism 19, the reverse clutch 29, and the output side gear transmission mechanism 15a. The drive wheel is driven to rotate in the backward direction.

上述の様に本例の無段変速装置の場合、前記入力回転軸１と、前記中間回転伝達軸１７と、前記出力回転軸５、５との、３軸構造であり、小型且つ軽量にする為の設計が容易であるにも拘らず、前記入力回転軸１を一方向に回転させた状態のまま、前記出力回転軸５、５を両方向に回転させられる。この為、設置スペースが限られたＦＦ車用の自動変速機として、非常に有用性が高い。又、前進時と後退時とで、前記トロイダル型無段変速機７の回転方向を変更する必要もない為、このトロイダル型無段変速機７の制御が面倒になる事もない。更に、小型に構成できる事に伴い、無段変速装置全体としての摩擦損失を少なく抑えて、この無段変速装置の伝達効率の向上の図り易い。 As described above, the continuously variable transmission of this example has a three-axis structure including the input rotary shaft 1, the intermediate rotation transmission shaft 17, and the output rotary shafts 5 and 5, and is small and lightweight. Although the design for this is easy, the output rotating shafts 5 and 5 can be rotated in both directions while the input rotating shaft 1 is rotated in one direction. For this reason, it is very useful as an automatic transmission for an FF vehicle having a limited installation space. Further, since it is not necessary to change the rotational direction of the toroidal type continuously variable transmission 7 between forward and backward, control of the toroidal type continuously variable transmission 7 does not become troublesome. Furthermore, with the fact that it can be made compact, it is easy to improve the transmission efficiency of the continuously variable transmission by minimizing the friction loss of the continuously variable transmission as a whole.

［実施の形態の第２例］
図２は、請求項１〜３、６〜９に対応する、本発明の実施の形態の第２例を示している。本例の場合には、シングルピニオン型である前進用遊星歯車機構１８ａを構成する各前進用遊星歯車２５ａ、２５ａと、ダブルピニオン型の後退用遊星歯車機構１９ａを構成する各遊星歯車素子２７ａ、２７ｃのうち、径方向外側の遊星歯車素子２７ｃ、２７ｃとを互いに結合固定して（軸方向寸法が長い一体構造として）これら各遊星歯車素子２７ｃ、２７ｃと前記各前進用遊星歯車２５ａ、２５ａとが同期して回転する様にしている。そして、これら各遊星歯車素子２７ｃ、２７ｃ及び各前進用遊星歯車２５ａ、２５ａを、単一のリング歯車３０に噛合させている。又、このリング歯車３０の回転を、出力側歯車伝達機構１５ａを介して、デファレンシャルギヤ１６の入力部に伝達する様にしている。 [Second Example of Embodiment]
FIG. 2 shows a second example of an embodiment of the present invention corresponding to claims 1 to 3 and 6 to 9. In the case of this example, the forward planetary gears 25a, 25a constituting the forward planetary gear mechanism 18a of a single pinion type, and the planetary gear elements 27a constituting the double pinion type reverse planetary gear mechanism 19a, 27c, the planetary gear elements 27c, 27c on the outer side in the radial direction are coupled and fixed to each other (as an integral structure having a long axial dimension), and the planetary gear elements 27c, 27c and the forward planetary gears 25a, 25a Are rotating in synchronization. The planetary gear elements 27 c and 27 c and the forward planetary gears 25 a and 25 a are meshed with a single ring gear 30. Further, the rotation of the ring gear 30 is transmitted to the input portion of the differential gear 16 via the output side gear transmission mechanism 15a.

本例の場合には、前進用遊星歯車機構１８ａを構成する前進用太陽歯車２１ａと、前記後退用遊星歯車機構１９ａを構成する後退用太陽歯車２２ａとを、トロイダル型無段変速機７の出力ディスク９の回転に基づき、選択的に回転駆動する様に構成している。即ち、本例の場合には、動力の伝達方向に関して、前記出力ディスク９の回転を取り出す為の入力側歯車伝達機構１０ｂの下流側端部に、クラッチ装置を構成する、前進用、後退用両クラッチ２８ａ、２９ａを設けている。これら両クラッチ２８ａ、２９ａにより、前記前進用、後退用両太陽歯車２１ａ、２２ａを選択的に回転駆動させる為、本例の場合には、中間回転伝達軸１７ａを、円管状の外径側回転伝達軸３１の内側に円杆状の内径側回転伝達軸３２を挿通した、二重構造としている。言い換えれば、この内径側回転伝達軸３２の中間部周囲に前記外径側回転伝達軸３１を、この内径側回転伝達軸３２に対する相対回転を可能に配置している。 In this example, the forward sun gear 21a constituting the forward planetary gear mechanism 18a and the backward sun gear 22a constituting the backward planetary gear mechanism 19a are output from the toroidal-type continuously variable transmission 7. Based on the rotation of the disk 9, it is configured to selectively rotate. That is, in the case of this example, both the forward and reverse directions that constitute the clutch device at the downstream end of the input side gear transmission mechanism 10b for taking out the rotation of the output disk 9 in the power transmission direction. Clutches 28a and 29a are provided. In order to selectively rotate and drive the forward and reverse sun gears 21a and 22a by both the clutches 28a and 29a, in the case of this example, the intermediate rotation transmission shaft 17a is rotated on the outer side of the circular tube. A double structure is formed in which a conical inner diameter side rotation transmission shaft 32 is inserted inside the transmission shaft 31. In other words, the outer diameter side rotation transmission shaft 31 is arranged around the intermediate portion of the inner diameter side rotation transmission shaft 32 so as to be able to rotate relative to the inner diameter side rotation transmission shaft 32.

そして、前記前進用太陽歯車２１ａを前記外径側回転伝達軸３１の先端部に、前記後退用太陽歯車２２ａを前記内径側回転伝達軸３２の先端部に、それぞれこれら外径側回転伝達軸３１又は内径側回転伝達軸３２と同期した回転を自在に設置している。前記前進用クラッチ２８ａは、前記外径側回転軸３１の基端部と前記入力側歯車伝達機構１０ｂとの間に、前記後退用クラッチ２９ａは、前記内径側回転伝達軸３２の基端部とこの入力側歯車伝達機構１０ｂとの間に、それぞれ設置している。本例の場合には、この入力側歯車伝達機構１０ｂを挟んで、前記前進用、後退用両クラッチ２８ａ、２９ａと、前記前進用、後退用両遊星歯車機構１８ａ、１９ａとを、軸方向に関して互いに反対側に配置している。 The forward sun gear 21a is at the tip of the outer diameter side rotation transmission shaft 31, and the backward sun gear 22a is at the tip of the inner diameter side rotation transmission shaft 32. Alternatively, the rotation synchronized with the inner diameter side rotation transmission shaft 32 is freely installed. The forward clutch 28a is disposed between the proximal end portion of the outer diameter side rotation shaft 31 and the input side gear transmission mechanism 10b, and the backward clutch 29a is coupled to the proximal end portion of the inner diameter side rotation transmission shaft 32. They are respectively installed between the input side gear transmission mechanism 10b. In the case of this example, the forward and reverse clutches 28a and 29a and the forward and reverse planetary gear mechanisms 18a and 19a are connected in the axial direction with the input side gear transmission mechanism 10b interposed therebetween. They are arranged on opposite sides.

上述の様に構成する本例の構造の場合も、３軸構造で小型・軽量化を図り易い構造であるにも拘らず、前記前進用、後退用両クラッチ２８ａ、２９ａを選択的に接続する事により、入力回転軸１を一方向に回転させたまま、出力回転軸５、５を両方向に回転させられる。しかも本例の構造の場合には、次の(1)〜(3)の効果を、合わせて得られる。
(1) 前記前進用、後退用両クラッチ２８ａ、２９ａと、前記前進用、後退用両遊星歯車機構１８ａ、１９ａとをバランス良く配置できて、小型・軽量化を図る面から有利である。
(2) これら前進用、後退用両遊星歯車機構１８ａ、１９ａで、単一のリング歯車３０を共用している為、径が大きく、従って重量が嵩むリング歯車の数を減らす事で、より小型・軽量化を図れる。
(3) 前記前進用、後退用両クラッチ２８ａ、２９ａを、動力の伝達方向に関して、減速機として機能する、前記前進用、後退用両遊星歯車機構１８ａ、１９ａよりも上流側に配置するので、前記前進用、後退用両クラッチ２８ａ、２９ａを通過するトルクを低く抑えられる。この結果、これら両クラッチ２８ａ、２９ａのトルク伝達容量を低く抑え、これら両クラッチ２８ａ、２９ａを小型化する事ができて、無段変速装置全体としての小型・軽量化も図り易い。
その他の部分の構成及び作用は、前述した実施の形態の第１例とほぼ同様であるから、重複する説明は省略する。 In the case of the structure of the present example configured as described above, both the forward and reverse clutches 28a and 29a are selectively connected even though the three-axis structure is easy to reduce in size and weight. Thus, the output rotary shafts 5 and 5 can be rotated in both directions while the input rotary shaft 1 is rotated in one direction. Moreover, in the case of the structure of this example, the following effects (1) to (3) can be obtained together.
(1) The forward and reverse clutches 28a and 29a and the forward and reverse planetary gear mechanisms 18a and 19a can be arranged in a well-balanced manner, which is advantageous in terms of reducing the size and weight.
(2) Since both the forward and reverse planetary gear mechanisms 18a, 19a share a single ring gear 30, the number of ring gears that are large in diameter and therefore heavy is reduced, thereby reducing the size. -Reduces weight.
(3) Since both the forward and reverse clutches 28a and 29a are arranged on the upstream side of the forward and reverse planetary gear mechanisms 18a and 19a, which function as a speed reducer, in the power transmission direction. The torque passing through both the forward and reverse clutches 28a and 29a can be kept low. As a result, the torque transmission capacity of both the clutches 28a, 29a can be kept low, and both the clutches 28a, 29a can be miniaturized, and the overall continuously variable transmission can be easily reduced in size and weight.
Since the configuration and operation of the other parts are almost the same as those of the first example of the above-described embodiment, redundant description is omitted.

［実施の形態の第３例］
図３は、請求項１、５〜９に対応する、本発明の実施の形態の第３例を示している。本例の場合、前進用、後退用両遊星歯車機構１８ｂ、１９ｂは何れも、シングルピニオン型である。即ち、このうちの前進用遊星歯車機構１８ｂは、中間伝達軸１７ａを構成する内径側回転伝達軸３２の先端部に設けた前進用太陽歯車２１ａと、この前進用太陽歯車２１ａの周囲に設けた前進用リング歯車２３ａとの間に複数個の前進用遊星歯車２５、２５を設け、これら各前進用遊星歯車２５、２５を、前記前進用太陽歯車２１ａ及び前記前進用リング歯車２３ａに噛合させて成る。又、前記各前進用遊星歯車２５、２５を回転自在に支持したキャリア２０ａを、ケーシングの内部に設けた取付部等の固定部分に支持固定して、回転を阻止している。更に、前記前進用リング歯車２３ａの回転を、前記後退用遊星歯車機構１９ｂを構成するキャリア２０ｂと出力側歯車伝達機構１５ａとを通じて、デファレンシャルギヤ１６に取り出す様にしている。 [Third example of embodiment]
FIG. 3 shows a third example of an embodiment of the present invention corresponding to claims 1 and 5 to 9. In the case of this example, both the forward and reverse planetary gear mechanisms 18b and 19b are of single pinion type. That is, among these, the forward planetary gear mechanism 18b is provided around the forward sun gear 21a provided at the tip of the inner diameter side rotational transmission shaft 32 constituting the intermediate transmission shaft 17a and the forward sun gear 21a. A plurality of forward planetary gears 25, 25 are provided between the forward ring gear 23a and the forward planetary gears 25, 25 are meshed with the forward sun gear 21a and the forward ring gear 23a. Become. Further, the carrier 20a that rotatably supports the forward planetary gears 25, 25 is supported and fixed to a fixing portion such as a mounting portion provided inside the casing to prevent rotation. Further, the rotation of the forward ring gear 23a is taken out to the differential gear 16 through the carrier 20b and the output side gear transmission mechanism 15a constituting the reverse planetary gear mechanism 19b.

これに対して、前記後退用遊星歯車機構１９ｂは、前記中間伝達軸１７ａを構成する外径側回転伝達軸３１の先端部に設けた後退用太陽歯車２２ａと、この後退用太陽歯車２２ａの周囲に設けた後退用リング歯車２４ａとの間に複数個の後退用遊星歯車２６ａ、２６ａを設け、これら各後退用遊星歯車２６ａ、２６ａを、前記後退用太陽歯車２２ａ及び前記後退用リング歯車２４ａに噛合させて成る。又、この後退用リング歯車２４ａを、固定の部分に支持固定し、回転を阻止している。更に、前記各後退用遊星歯車２６ａ、２６ａを回転自在に支持した、前記キャリア２０ｂの回転（これら各後退用遊星歯車２６ａ、２６ａの公転運動）を、前記出力側歯車伝達機構１５ａを通じて、前記デファレンシャルギヤ１６に取り出す様にしている。 On the other hand, the reverse planetary gear mechanism 19b includes a reverse sun gear 22a provided at the tip of the outer diameter side rotation transmission shaft 31 constituting the intermediate transmission shaft 17a, and the periphery of the reverse sun gear 22a. A plurality of reverse planetary gears 26a, 26a are provided between the reverse ring gear 24a and the reverse ring gear 24a. The reverse planetary gears 26a, 26a are connected to the reverse sun gear 22a and the reverse ring gear 24a. It is made to mesh. The reverse ring gear 24a is supported and fixed to a fixed portion to prevent rotation. Further, the rotation of the carrier 20b, which rotatably supports the retreating planetary gears 26a, 26a (revolving motion of the retreating planetary gears 26a, 26a), is transmitted through the output side gear transmission mechanism 15a to the differential. The gear 16 is taken out.

上述の様に構成する本例の場合も、３軸構造で小型・軽量化を図り易い構造であるにも拘らず、前進用、後退用両クラッチ２８ａ、２９ａを選択的に接続する事により、入力回転軸１を一方向に回転させたまま、出力回転軸５、５を両方向に回転させられる。又、本例の構造の場合には、上述した実施の形態の第２例の場合に得られる、前記(1)(3)の効果に加えて、前記前進用、後退用両遊星歯車機構１８ｂ、１９ｂを、何れもシングルピニオン型とする事による、構造の簡略化も図れる。
その他の部分の構成及び作用は、前述した実施の形態の第２例とほぼ同様であるから、重複する説明は省略する。 In the case of this example configured as described above, the forward and backward clutches 28a and 29a are selectively connected in spite of the triaxial structure that is easy to reduce in size and weight. The output rotation shafts 5 and 5 can be rotated in both directions while the input rotation shaft 1 is rotated in one direction. In the case of the structure of this example, in addition to the effects (1) and (3) obtained in the case of the second example of the above-described embodiment, the forward and reverse planetary gear mechanisms 18b. , 19b can be of a single pinion type, thereby simplifying the structure.
Since the configuration and operation of the other parts are almost the same as those of the second example of the above-described embodiment, a duplicate description is omitted.

［実施の形態の第４例］
図４も、請求項１、５〜９に対応する、本発明の実施の形態の第４例を示している。本例の場合には、前進用、後退用両遊星歯車機構１８ｃ、１９ｃの配置を、上述した実施の形態の第３例の場合とは逆にしている。これに合わせて、前進用、後退用両クラッチ２８ａ、２９ａの配置、並びに、回転を阻止する部材を、中間回転伝達軸１７ａの軸方向に関して、上述の実施の形態の第３例とは逆にしている。配置が逆になった点以外の基本的な構造及び作用は、上述した実施の形態の第３例と同様であるから、重複する説明は省略する。 [Fourth Example of Embodiment]
FIG. 4 also shows a fourth example of the embodiment of the invention corresponding to claims 1 and 5 to 9. In the case of this example, the arrangement of both forward and reverse planetary gear mechanisms 18c and 19c is reversed from that in the third example of the above-described embodiment. In accordance with this, the arrangement of the forward and reverse clutches 28a and 29a and the member that prevents the rotation are reversed with respect to the axial direction of the intermediate rotation transmission shaft 17a from the third example of the above-described embodiment. ing. Since the basic structure and operation other than the reverse arrangement are the same as in the third example of the above-described embodiment, redundant description is omitted.

本発明を構成するトロイダル型無段変速機は、図示の様なハーフトロイダル型に限らず、フルトロイダル型であっても良い。 The toroidal type continuously variable transmission constituting the present invention is not limited to the half toroidal type as shown, but may be a full toroidal type.

１入力回転軸
２第一中間回転伝達軸
３アイドラ軸
４第二中間回転伝達軸
５出力回転軸
６発進クラッチ
７トロイダル型無段変速機
８入力ディスク
９出力ディスク
１０、１０ａ、１０ｂ入力側歯車伝達機構
１１前進用クラッチ
１２前進用歯車伝達機構
１３後退用クラッチ
１４後退用歯車伝達機構
１５、１５ａ出力側歯車伝達機構
１６デファレンシャルギヤ
１７、１７ａ中間回転伝達軸
１８、１８ａ、１８ｂ、１８ｃ前進用遊星歯車機構
１９、１９ａ、１９ｂ、１９ｃ後退用遊星歯車機構
２０、２０ａ、２０ｂキャリア
２１、２１ａ前進用太陽歯車
２２、２２ａ後退用太陽歯車
２３、２３ａ前進用リング歯車
２４、２４ａ後退用リング歯車
２５、２５ａ前進用遊星歯車
２６、２６ａ後退用遊星歯車
２７ａ、２７ｂ、２７ｃ遊星歯車素子
２８、２８ａ前進用クラッチ
２９、２９ａ後退用クラッチ
３０リング歯車
３１外径側回転伝達軸
３２内径側回転伝達軸 DESCRIPTION OF SYMBOLS 1 Input rotation shaft 2 1st intermediate rotation transmission shaft 3 Idler shaft 4 Second intermediate rotation transmission shaft 5 Output rotation shaft 6 Starting clutch 7 Toroidal continuously variable transmission 8 Input disk 9 Output disk 10, 10a, 10b Input side gear transmission Mechanism 11 Forward clutch 12 Forward gear transmission mechanism 13 Reverse clutch 14 Reverse gear transmission mechanism 15, 15a Output side gear transmission mechanism 16 Differential gear 17, 17a Intermediate rotation transmission shaft 18, 18a, 18b, 18c Forward planetary gear Mechanism 19, 19a, 19b, 19c Reverse planetary gear mechanism 20, 20a, 20b Carrier 21, 21a Forward sun gear 22, 22a Reverse sun gear 23, 23a Forward ring gear 24, 24a Reverse ring gear 25, 25a Forward planetary gear 26, 26a Reverse planetary gear 27a, 27 b, 27c Planetary gear elements 28, 28a Forward clutch 29, 29a Reverse clutch 30 Ring gear 31 Outer diameter side rotation transmission shaft 32 Inner diameter side rotation transmission shaft

Claims

An input rotary shaft that is rotationally driven by a drive source, and a toroidal continuously variable transmission that is provided around the input rotary shaft and concentrically with the input rotary shaft and is operated using the input rotary shaft as an input unit thereof. An output rotation shaft provided in parallel with the input rotation shaft, and an intermediate portion provided in parallel with the input rotation shaft and the output rotation shaft at a portion between the input rotation shaft and the output rotation shaft in the power transmission direction. Between the rotation transmission shaft, the forward and reverse planetary gear mechanisms provided around the intermediate rotation transmission shaft, the output portion of the toroidal continuously variable transmission, and the input portions of these planetary gear mechanisms. An input-side power transmission mechanism, a clutch device, and an output-side power transmission mechanism provided between the output portions of these planetary gear mechanisms and the output rotation shaft, the clutch device switching Accompanying One of the planetary gear mechanisms is incorporated into a power transmission path between the output portion of the toroidal-type continuously variable transmission and the output rotation shaft, and the other planetary gear mechanism is incorporated in the power transmission path. A continuously variable transmission that has a function of disconnecting from a forward clutch that is connected during forward travel and disconnected during backward travel, and a reverse clutch that is connected during backward travel and disconnected during forward travel.

The forward and reverse planetary gear mechanisms each include a carrier that is supported by a fixed portion and does not rotate. Both of these planetary gear mechanisms are a sun gear that rotates together with the intermediate rotation transmission shaft, and each sun gear. A ring gear disposed in the periphery, and a plurality of planetary gears provided between the sun gear and the ring gear, and one of the planetary gear mechanisms is configured to connect each planetary gear to the sun gear. A single-pinion type that meshes with both the gear and the ring gear, and the other planetary gear mechanism meshes one planetary gear element provided for each planetary gear with each other, and one planetary gear element 2. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is a double pinion type in which a sun gear is engaged with the other planetary gear element and the ring gear.

Each planetary gear constituting the single pinion type planetary gear mechanism is synchronized with each planetary gear element meshing with the ring gear among the planetary gear elements constituting the double pinion type planetary gear mechanism. The continuously variable transmission according to claim 2, wherein one ring gear is shared by both the forward and reverse planetary gear mechanisms by freely coupling the rotation.

2. The forward and reverse clutches are respectively provided between a pair of ring gears constituting the forward and reverse planetary gear mechanisms and the output transmission mechanism. The continuously variable transmission as described in any one of -2.

Both the forward and reverse planetary gear mechanisms are each a sun gear that rotates as the output portion of the toroidal continuously variable transmission rotates, and a ring gear that is arranged around each sun gear, A single pinion type provided with a plurality of planetary gears meshed with both the sun gear and the ring gear, and the two planetary gear mechanisms, One planetary gear mechanism has a carrier fixed and transmits the rotation of the ring gear to the output rotation shaft, and the other planetary gear mechanism has the ring gear fixed and the carrier rotates. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is transmitted to the output rotation shaft.

The forward and reverse clutches are provided between the output portion of the toroidal-type continuously variable transmission and a pair of sun gears constituting the forward and reverse planetary gear mechanisms, respectively. there, continuously variable transmission according to claim 3 or claim 5.

The intermediate rotation transmission shaft has a circular outer diameter rotation transmission shaft disposed around the inner diameter side rotation transmission shaft and an intermediate portion of the inner diameter side rotation transmission shaft so as to be able to rotate relative to the inner diameter side rotation transmission shaft. A pair of sun gears constituting the forward and reverse planetary gear mechanisms, respectively, on a part of the inner diameter side rotation transmission shaft or the outer diameter side rotation transmission shaft, The forward and reverse clutches are installed freely in synchronization with the rotation transmission shaft. The inner and outer rotation transmission shafts and the outer diameter side rotation transmission shaft and the toroidal continuously variable transmission are respectively provided. The continuously variable transmission according to claim 6, provided between the output section and the output section.

The input-side power transmission mechanism includes an output member provided at an output portion of the toroidal-type continuously variable transmission, and the clutch device and the forward drive in the axial direction of the intermediate rotation transmission shaft The continuously variable transmission according to any one of claims 1 to 3, and 5 to 7, wherein the primary and reverse planetary gear mechanisms are disposed on opposite sides of each other.

The output-side power transmission mechanism is configured to include a differential gear, and the output of either one of the forward and reverse planetary gear mechanisms according to the switching of the clutch device. 9. The continuously variable drive according to any one of claims 1 to 8, wherein an input portion of the differential gear is rotationally driven by a portion, and a pair of left and right output rotation shafts are rotationally driven by an output portion of the differential gear. Transmission device.