JP4826409B2

JP4826409B2 - Continuously variable transmission

Info

Publication number: JP4826409B2
Application number: JP2006259361A
Authority: JP
Inventors: 宏史石川
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2006-09-25
Filing date: 2006-09-25
Publication date: 2011-11-30
Anticipated expiration: 2026-09-25
Also published as: JP2008075863A

Description

この発明は、例えば自動車用自動変速装置として、或は、ポンプ等の各種産業機械の運転速度を調節する為の変速装置として利用する、無段変速装置の改良に関する。より具体的には、この無段変速装置の小型化を図るものであり、例えばＦＦ車（前置エンジン前輪駆動車）用の自動変速装置の様に、エンジンルーム等の限られた空間内に組み込む変速装置として、特に好適である。 The present invention relates to an improvement of a continuously variable transmission that is used, for example, as an automatic transmission for automobiles or as a transmission for adjusting the operating speed of various industrial machines such as pumps. More specifically, this continuously variable transmission is intended to be miniaturized. For example, in an automatic transmission for an FF vehicle (front-engine front wheel drive vehicle), the space is limited in an engine room or the like. It is particularly suitable as a built-in transmission.

例えば特許文献１、非特許文献１、２等の多くの刊行物に記載されている様に、自動車用自動変速装置を構成する変速ユニットとして、トロイダル型無段変速機を使用する事が研究され、一部で実施されている。図６は、この様なトロイダル型無段変速機のうちの、ダブルキャビティ型と呼ばれるものを示している。このトロイダル型無段変速機は、入力回転軸１の軸方向２個所位置に、１対の入力側ディスク２ａ、２ｂを支持している。これら両入力側ディスク２ａ、２ｂは、上記入力回転軸１に対し、それぞれがトロイド曲面（断面円弧形の凹面）である入力側内側面３、３同士を互いに対向させた状態で、互いに同心に、且つ、同期した回転を自在に支持している。 For example, as described in many publications such as Patent Document 1 and Non-Patent Documents 1 and 2, it has been studied to use a toroidal continuously variable transmission as a transmission unit constituting an automatic transmission for an automobile. Have been implemented in part. FIG. 6 shows a so-called double cavity type of such a toroidal type continuously variable transmission. This toroidal-type continuously variable transmission supports a pair of input-side disks 2 a and 2 b at two positions in the axial direction of the input rotary shaft 1. Both the input side disks 2a and 2b are concentric with the input rotation shaft 1 with the input side inner side surfaces 3 and 3 each having a toroidal curved surface (concave arc-shaped concave surface) facing each other. In addition, it supports the synchronized rotation freely.

又、上記入力回転軸１の中間部は、トロイダル型無段変速機を収納したケーシング４内に設置した隔壁部５に設けた通孔６を挿通している。この通孔６の内径側には、円筒状の出力筒７を、１対の転がり軸受８、８により回転自在に支持しており、この出力筒７の中間部外周面に、特許請求の範囲に記載した第一動力伝達部材を構成する出力歯車９を固設している。又、この出力筒７の両端部で上記隔壁部５の両外側面から突出した部分に、１対の出力側ディスク１０ａ、１０ｂを、スプライン係合により、上記出力筒７と同期した回転自在に支持している。この状態で、それぞれがトロイド曲面（断面円弧形の凹面）である出力側内側面１１、１１が、上記両入力側内側面３、３に対向する。尚、上記出力側ディスク１０ａ、１０ｂとして、例えば後述する特許文献３、４に記載されている構造（図８に示す構造）の様に、上記１対の出力側ディスク１０ａ、１０ｂを結合固定した如き形状の一体型の出力側ディスク１０を採用する場合もある。 Further, the intermediate portion of the input rotary shaft 1 is inserted through a through hole 6 provided in a partition wall portion 5 installed in a casing 4 housing a toroidal type continuously variable transmission. A cylindrical output tube 7 is rotatably supported by a pair of rolling bearings 8 and 8 on the inner diameter side of the through-hole 6. The output gear 9 constituting the first power transmission member described in 1 is fixed. Further, a pair of output side disks 10a and 10b are rotatably connected to both ends of the output cylinder 7 from both outer side surfaces of the partition wall section 5 in synchronization with the output cylinder 7 by spline engagement. I support it. In this state, the output side inner surfaces 11, 11, each of which is a toroidal curved surface (concave arc-shaped concave surface), face the both input side inner surfaces 3, 3. As the output side disks 10a and 10b, the pair of output side disks 10a and 10b are coupled and fixed as in the structure described in Patent Documents 3 and 4 described later (structure shown in FIG. 8), for example. The integrated output side disk 10 having such a shape may be employed.

又、上記入力回転軸１の周囲で上記入力側、出力側両内側面３、１１同士の間部分（キャビティ）に、それぞれ複数個（一般的には２個又は３個）ずつのパワーローラ１２、１２を配置している。これら各パワーローラ１２、１２はそれぞれ、上記入力側、出力側両内側面３、１１に当接（転がり接触）する周面１３、１３を球状凸面としたもので、トラニオン（支持部材）１４、１４の内側面に、回転及び若干の揺動変位自在に支持されている。又、これら各トラニオン１４、１４は、上記入力回転軸１に対し捩れの位置にある枢軸を中心とする揺動変位を自在に設けられている。 In addition, a plurality (generally two or three) of power rollers 12 are provided in a portion (cavity) between the input side and output side inner side surfaces 3 and 11 around the input rotation shaft 1. , 12 are arranged. Each of these power rollers 12 and 12 has a spherical convex surface on the peripheral surfaces 13 and 13 that are in contact (rolling contact) with the inner surfaces 3 and 11 on both the input side and the output side, and a trunnion (support member) 14 and 14 is supported on the inner surface of 14 so as to be freely rotatable and slightly swingable. Each of the trunnions 14 and 14 is provided with a swinging displacement about a pivot that is twisted with respect to the input rotary shaft 1.

上記入力側ディスク２ａ、２ｂと上記出力側ディスク１０ａ、１０ｂとの間の変速比を変える場合は、上記各トラニオン１４、１４を上記枢軸の軸方向（図６の表裏方向）に変位させる。この結果、上記各パワーローラ１２、１２の周面１３、１３と上記入力側、出力側各ディスク２ａ、２ｂ、１０ａ、１０ｂの入力側、出力側各内側面３、１１との転がり接触部（トラクション部）に作用する、接線方向の力の向きが変化（転がり接触部にサイドスリップが発生）する。そして、この力の向きの変化に伴って、上記各トラニオン１４、１４が上記枢軸を中心に揺動（傾斜）し、上記各パワーローラ１２、１２の周面１３、１３と上記入力側、出力側各ディスク２ａ、２ｂ、１０ａ、１０ｂの入力側、出力側各内側面３、５との接触位置が変化する。 When changing the gear ratio between the input side disks 2a, 2b and the output side disks 10a, 10b, the trunnions 14, 14 are displaced in the axial direction of the pivot (front and back direction in FIG. 6). As a result, rolling contact portions between the peripheral surfaces 13 and 13 of the power rollers 12 and 12 and the input and output inner surfaces 3 and 11 of the input and output disks 2a, 2b, 10a and 10b ( The direction of the tangential force acting on the traction section changes (side slip occurs in the rolling contact section). As the direction of the force changes, the trunnions 14 and 14 swing (tilt) about the pivot, and the peripheral surfaces 13 and 13 of the power rollers 12 and 12 and the input side and output The contact positions of the side disks 2a, 2b, 10a and 10b with the input side and output side inner surfaces 3 and 5 change.

例えば図６に示す様に、上記各パワーローラ１２、１２の周面１３、１３を、上記入力側ディスク２ａ、２ｂの入力側内側面３、３の径方向内寄り部分と、上記出力側ディスク１０ａ、１０ｂの出力側内側面１１、１１の径方向外寄り部分とに転がり接触させれば、上記両ディスク２ａ、２ｂ、１０ａ、１０ｂ同士の間の変速比が減速側になる。これに対して、図６とは逆に、上記各パワーローラ１２、１２の周面１３、１３を、上記入力側ディスク２ａ、２ｂの入力側内側面３、３の径方向外寄り部分と、上記出力側ディスク１０ａ、１０ｂの出力側内側面１１、１１の径方向内寄り部分とに転がり接触させれば、上記両ディスク２ａ、２ｂ、１０ａ、１０ｂ同士の間の変速比が増速側になる。 For example, as shown in FIG. 6, the peripheral surfaces 13, 13 of the power rollers 12, 12 are connected to the radially inner portions of the input side inner surfaces 3, 3 of the input side disks 2a, 2b and the output side disks. If it is brought into rolling contact with the radially outer portions of the output side inner surfaces 11, 11 of 10a, 10b, the gear ratio between the two disks 2a, 2b, 10a, 10b becomes the deceleration side. On the other hand, conversely to FIG. 6, the peripheral surfaces 13, 13 of each of the power rollers 12, 12 are arranged radially outside the input side inner surfaces 3, 3 of the input side disks 2 a, 2 b, If the rolling contact is made with the radially inner portions of the output side inner surfaces 11, 11 of the output side disks 10a, 10b, the gear ratio between the two disks 2a, 2b, 10a, 10b will be increased. Become.

上述の様なトロイダル型無段変速機の運転時には、エンジン等の駆動源（動力源）に繋がる駆動軸１５により一方（図６の左方）の入力側ディスク２ａを、ローディングカム式の押圧装置１６を介して回転駆動する。この結果、前記入力回転軸１の両端部に支持された１対の入力側ディスク２ａ、２ｂが、互いに近づく方向に押圧されつつ同期して回転する。そして、この回転が、上記各パワーローラ１２、１２を介して上記両出力側ディスク１０ａ、１０ｂに伝わり、前記出力歯車９から取り出される。 During operation of the toroidal-type continuously variable transmission as described above, one input side disk 2a (left side in FIG. 6) is connected to a loading cam type pressing device by a drive shaft 15 connected to a drive source (power source) such as an engine. 16 is driven to rotate. As a result, the pair of input-side disks 2a and 2b supported at both ends of the input rotation shaft 1 rotate synchronously while being pressed in a direction approaching each other. Then, this rotation is transmitted to both the output side disks 10a and 10b via the power rollers 12 and 12, and is taken out from the output gear 9.

ところで、上述した様なトロイダル型無段変速機を、例えば車両用（自動車用）の自動変速装置を構成する変速ユニットとして使用する場合、このトロイダル型無段変速機を、正転逆転切換機構（前後進切換機構）と組み合わせて無段変速装置を構成する必要がある。この理由は、例えば自動車であれば前進だけでなく後退させる必要もあり、駆動源であるエンジンから出力軸（車輪）に伝達される動力の回転方向を、上記正転逆転切換機構により、前進方向に対応する方向（正転方向）と、後退方向に対応する方向（逆転方向）とに、それぞれ切り換える必要がある為である。この様なトロイダル型無段変速機と正転逆転切換機構である前後進切換機構とを組み合わせて成る無段変速装置として、例えば特許文献２に記載された構造が知られている。 By the way, when the above-described toroidal continuously variable transmission is used as a transmission unit constituting an automatic transmission for a vehicle (for automobiles), for example, the toroidal continuously variable transmission is connected to a forward / reverse switching mechanism ( It is necessary to configure a continuously variable transmission in combination with a forward / reverse switching mechanism. This is because, for example, in the case of an automobile, it is necessary not only to move forward but also to move backward. The rotational direction of the power transmitted from the engine that is the drive source to the output shaft (wheel) is changed to the forward direction by the forward / reverse switching mechanism. This is because it is necessary to switch between a direction corresponding to (forward rotation direction) and a direction corresponding to the reverse direction (reverse rotation direction). For example, a structure described in Patent Document 2 is known as a continuously variable transmission that is a combination of such a toroidal type continuously variable transmission and a forward / reverse switching mechanism that is a forward / reverse switching mechanism.

図７は、上記特許文献２に記載された構造を示している。この図７に示す構造の場合は、遊星歯車式変速機１７と前進、後退各クラッチ１８、１９とから成る、前後進切換機構２０を、駆動源であるエンジンからの動力の伝達方向に関し、トロイダル型無段変速機２１よりも上流側に設けている。但し、この構造の場合、上記前後進切換機構２０と上記トロイダル型無段変速機２１とを軸方向に直列に設けている（前後進切換機構２０とトロイダル型無段変速機２１とを同心に設けている）為、無段変速装置全体の軸方向寸法が大きくなる。この為、例えばエンジンルーム等の限られた空間内に組み込む必要のある、ＦＦ車（前置エンジン前輪駆動車）用の自動変速装置として採用する事は、そのままでは難しい。 FIG. 7 shows the structure described in Patent Document 2. In the case of the structure shown in FIG. 7, the forward / reverse switching mechanism 20 including the planetary gear type transmission 17 and the forward and reverse clutches 18 and 19 is connected to the toroidal portion with respect to the direction of transmission of power from the engine as the drive source. It is provided upstream of the continuously variable transmission 21. However, in this structure, the forward / reverse switching mechanism 20 and the toroidal continuously variable transmission 21 are provided in series in the axial direction (the forward / reverse switching mechanism 20 and the toroidal continuously variable transmission 21 are concentric. Therefore, the axial dimension of the continuously variable transmission is increased. For this reason, it is difficult to adopt as an automatic transmission for an FF vehicle (front engine front wheel drive vehicle) that needs to be incorporated in a limited space such as an engine room.

これに対して、特許文献３、４には、図８に示す様に、前後進切換機構２０ａを構成する遊星歯車式変速機１７ａ（ギヤードニュートラル状態を実現する為の遊星歯車式変速機１７ａ）を、駆動源からの動力の伝達方向に関し、トロイダル型無段変速機２１よりも下流側に設けた構造が記載されている。そして、この構造の場合には、上記トロイダル型無段変速機２１の入力回転軸１と平行に設けた回転伝達軸２２の周囲に、上記遊星歯車式変速機１７ａを設けている。この為、前述の図７に示した特許文献２に記載された構造に比べ、軸方向寸法の低減を図れる。但し、上記特許文献３、４に記載された構造の場合は、上記トロイダル型無段変速機２１の入力回転軸１と上記回転伝達軸２２との距離が大きくなり易い。即ち、上記回転伝達軸２２の周囲に設けられた上記遊星歯車式変速機１７ａは、太陽歯車２３、各遊星歯車２４、２４、リング歯車２５を径方向に重畳する状態で設ける為、径方向寸法が嵩み易い。しかも、このうちの最も外径側に設けられるリング歯車２５と軸方向に対向する状態で、このリング歯車２５よりも大径の低速用クラッチ２６を設けている。この為、上記回転伝達軸２２の周囲に必要な（確保すべき）径方向寸法が嵩み、その分、上記回転伝達軸２２と上記入力回転軸１との距離が大きくなり、無段変速装置全体として大型化する。 On the other hand, in Patent Documents 3 and 4, as shown in FIG. 8, a planetary gear type transmission 17a (planetary gear type transmission 17a for realizing a geared neutral state) constituting a forward / reverse switching mechanism 20a. Is described in the downstream of the toroidal type continuously variable transmission 21 with respect to the direction of transmission of power from the drive source. In the case of this structure, the planetary gear type transmission 17a is provided around the rotation transmission shaft 22 provided in parallel with the input rotation shaft 1 of the toroidal continuously variable transmission 21. Therefore, the axial dimension can be reduced as compared with the structure described in Patent Document 2 shown in FIG. However, in the case of the structures described in Patent Documents 3 and 4, the distance between the input rotary shaft 1 of the toroidal-type continuously variable transmission 21 and the rotation transmission shaft 22 tends to be large. That is, the planetary gear type transmission 17a provided around the rotation transmission shaft 22 is provided with the sun gear 23, the planetary gears 24 and 24, and the ring gear 25 superimposed in the radial direction. Tends to be bulky. In addition, a low-speed clutch 26 having a diameter larger than that of the ring gear 25 is provided so as to face the ring gear 25 provided on the outermost diameter side in the axial direction. For this reason, a necessary radial dimension around the rotation transmission shaft 22 is increased, and accordingly, the distance between the rotation transmission shaft 22 and the input rotation shaft 1 is increased. Increases overall size.

又、図示の構造の場合は、上記遊星歯車式変速機１７ａ並びに低速用クラッチ２６を、トロイダル型無段変速機２１の両キャビティのうちの一方（図８の左方）のキャビティに対向する状態で配置している。この為、他方（図８の右方）のキャビティに対向する部分に余剰空間（無駄な空間）を生じ易くなる等、構成部材をコンパクトにまとめにくくなり、変速装置全体として大型化する事が避けられない。又、上記トロイダル型無段変速機２１と上記回転伝達軸２２との間に、このトロイダル型無段変速機２１と遊星歯車式変速機１７ａとの間で動力の伝達を行なう動力伝達機構と、この動力伝達機構と上記遊星歯車式変速機１７ａとの間の動力伝達状態を切り換える為の低速用、高速用各クラッチ２６、２７とを設けている為、上記回転伝達軸２２の周囲の構造が複雑になる。しかも、上記遊星歯車式変速機１７ａを構成する各遊星歯車２４、２４（を支持する各遊星軸２８、２８）への潤滑油供給路を設ける必要もあり、この面からも構造が複雑になる。 In the illustrated structure, the planetary gear type transmission 17a and the low speed clutch 26 are opposed to one of the cavities of the toroidal-type continuously variable transmission 21 (left side in FIG. 8). It is arranged with. For this reason, it is difficult to make the components compact in a compact manner, for example, an excess space (useless space) is likely to be formed in a portion facing the other cavity (the right side in FIG. 8). I can't. A power transmission mechanism for transmitting power between the toroidal continuously variable transmission 21 and the planetary gear type transmission 17a between the toroidal continuously variable transmission 21 and the rotation transmission shaft 22; Since the low speed and high speed clutches 26 and 27 for switching the power transmission state between the power transmission mechanism and the planetary gear type transmission 17a are provided, the structure around the rotation transmission shaft 22 is provided. It becomes complicated. In addition, it is necessary to provide a lubricating oil supply path to the planetary gears 24 and 24 (the planetary shafts 28 and 28 supporting the planetary gears 24 and 24) constituting the planetary gear type transmission 17a, and the structure is complicated also from this aspect. .

この様な不都合を防止すべく、本発明者は、回転伝達軸の周囲に設ける前後進切換機構として、遊星歯車式変速機１７、１７ａ以外の構成を採用する事を考えた。具体的には、この様な前後進切換機構として、上記回転伝達軸と同心に設けられて、正転方向（前進方向）に対応する動力の伝達を行なう為の正転用動力伝達部材（前進用動力伝達部材）と、同じく上記回転伝達軸と同心に設けられて、逆転方向（後退方向）に対応する動力の伝達を行なう為の逆転用動力伝達部材（後退用動力伝達部材）と、上記動力の伝達方向に関し、上記回転伝達軸と上記正転用動力伝達部材との間に設けられて、これら回転伝達軸と正転用動力伝達部材との間で動力の伝達を行なう状態と行なわない状態とを切り換える正転用クラッチ（前進クラッチ）と、同じく上記回転伝達軸と上記逆転用動力伝達部材との間に設けられて、これら回転伝達軸と逆転用動力伝達部材との間で動力の伝達を行なう状態と行なわない状態とを切り換える逆転用クラッチ（後退クラッチ）とを備えた構成を考えた。 In order to prevent such an inconvenience, the present inventor considered adopting a configuration other than the planetary gear type transmissions 17 and 17a as the forward / reverse switching mechanism provided around the rotation transmission shaft. Specifically, as such a forward / reverse switching mechanism, a forward drive power transmission member (forward drive member) that is provided concentrically with the rotation transmission shaft and transmits power corresponding to the forward drive direction (forward drive direction). A power transmission member), a power transmission member for reverse rotation (reverse power transmission member) which is provided concentrically with the rotation transmission shaft, and transmits power corresponding to the reverse rotation direction (reverse direction). With respect to the transmission direction of the motor, a state is provided between the rotation transmission shaft and the forward rotation power transmission member, and a state in which power is transmitted between the rotation transmission shaft and the forward rotation power transmission member and a state in which power transmission is not performed. A forward-rotating clutch (forward clutch) to be switched, and a state in which power is transmitted between the rotation transmission shaft and the reverse power transmission member, which is also provided between the rotation transmission shaft and the reverse power transmission member. And do not do Considering the configuration of a reverse clutch for switching bets (reverse clutch).

この様な構成の場合、入力回転軸の軸方向に亙って正転用、逆転用各動力伝達部材が配置され、前述した遊星歯車式変速機１７、１７ａの様に、正転用、逆転用各動力伝達部材に対応する部材（図８の遊星歯車式変速機１７ａであれば、太陽歯車２３、各遊星歯車２４、２４、リング歯車２５）が径方向に重畳しない。この為、径方向寸法を抑えられる（直径を小さくできる）反面、そのままでは、回転伝達軸の軸方向寸法が徒に長くなる可能性がある。特に、トロイダル型無段変速機を構成する出力側ディスクを単一の部材により構成した場合には、このトロイダル型無段変速機の軸方向寸法を小さくできる。この為、上述の様に回転伝達軸の軸方向寸法が長いままだと、前後進切換機構の軸方向端部がトロイダル型無段変速機の軸方向端部よりも軸方向に突出する可能性があり、小型化を図る面で好ましくない。 In the case of such a configuration, forward and reverse power transmission members are arranged along the axial direction of the input rotation shaft. Like the planetary gear type transmissions 17 and 17a described above, the forward and reverse power transmission members are arranged. Members corresponding to the power transmission member (the sun gear 23, the planetary gears 24 and 24, and the ring gear 25 in the case of the planetary gear type transmission 17a in FIG. 8) do not overlap in the radial direction. For this reason, although the radial dimension can be suppressed (the diameter can be reduced), the axial dimension of the rotation transmission shaft may become longer as it is. In particular, when the output side disk constituting the toroidal type continuously variable transmission is formed of a single member, the axial dimension of the toroidal type continuously variable transmission can be reduced. Therefore, if the axial dimension of the rotation transmission shaft remains long as described above, the axial end of the forward / reverse switching mechanism may protrude more axially than the axial end of the toroidal continuously variable transmission. Therefore, it is not preferable in terms of downsizing.

特開２００１−３１７６０１号公報JP 2001-317601 A 特開２００６−４６５７３号公報JP 2006-46573 A 特開平１０−２６７１１６号公報JP-A-10-267116 特開平１１−６３１３９号公報JP 11-63139 A 青山元男著、「別冊ベストカー赤バッジシリーズ２４５／クルマの最新メカがわかる本」、株式会社三推社／株式会社講談社、平成１３年１２月２０日、ｐ．９２−９３Motoo Aoyama, “Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars”, Sangensha Co., Ltd./Kodansha Co., Ltd., December 20, 2001, p. 92-93 田中裕久著、「トロイダルＣＶＴ」、株式会社コロナ社、２０００年７月１３日Hirohisa Tanaka, “Toroidal CVT”, Corona Inc., July 13, 2000

本発明の無段変速装置は、上述の様な事情に鑑みて、小型、且つ、簡素で、しかも、回転伝達軸の軸方向寸法も低減できる構造を実現すべく発明したものである。 The continuously variable transmission of the present invention has been invented to realize a structure that is small and simple, and that can also reduce the axial dimension of the rotation transmission shaft, in view of the circumstances as described above.

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、回転伝達軸と、動力伝達機構と、出力回転軸と、正転逆転切換機構（前後進切換機構）とを備える。
このうちの入力回転軸は、駆動源（例えばエンジン等の動力源）からの動力が入力される。
又、上記トロイダル型無段変速機は、上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いる。
又、上記回転伝達軸は、上記動力の伝達方向に関し、上記入力回転軸よりも下流側に、この入力回転軸と平行に設けられている。
又、上記動力伝達機構は、上記トロイダル型無段変速機と上記回転伝達軸との間で動力の伝達を行なうものである。例えば、歯車式、或は、チェーン・スプロケット式等の動力伝達機構を採用できる。
又、上記出力回転軸は、上記動力の伝達方向に関し、上記回転伝達軸よりも下流側に、この回転伝達軸と平行に設けられている。
又、上記正転逆転切換機構（前後進切換機構）は、上記動力の伝達方向に関し、上記回転伝達軸と出力回転軸との間に設けられて、この出力回転軸から出力される上記動力の回転方向を正転、逆転（前進に対応する方向、後退に対応する方向）に切り換えるものである。 The continuously variable transmission of the present invention includes an input rotation shaft, a toroidal continuously variable transmission, a rotation transmission shaft, a power transmission mechanism, an output rotation shaft, and a forward / reverse switching mechanism (forward / reverse switching mechanism). Prepare.
Of these, the input rotary shaft receives power from a drive source (for example, a power source such as an engine).
The toroidal continuously variable transmission is provided around the input rotation shaft and concentric with the input rotation shaft.
The rotation transmission shaft is provided downstream of the input rotation shaft in parallel with the input rotation shaft in the power transmission direction.
The power transmission mechanism transmits power between the toroidal type continuously variable transmission and the rotation transmission shaft. For example, a power transmission mechanism such as a gear type or a chain / sprocket type can be employed.
The output rotation shaft is provided downstream of the rotation transmission shaft in parallel with the rotation transmission shaft with respect to the power transmission direction.
Further, the forward / reverse switching mechanism (forward / reverse switching mechanism) is provided between the rotation transmission shaft and the output rotation shaft with respect to the transmission direction of the power, and the power output from the output rotation shaft. The rotation direction is switched between forward rotation and reverse rotation (direction corresponding to forward movement, direction corresponding to backward movement).

又、上記トロイダル型無段変速機は、ダブルキャビティ型のもので、１対の入力側ディスクと、出力側ディスクと、複数個のパワーローラとを備える。
このうちの各入力側ディスクは、上記入力回転軸を介して互いに同心に、且つ、同期した回転を自在として支持されている。
又、上記出力側ディスクは、上記両入力側ディスク同士の間に、これら両入力側ディスクと同心に、且つ、これら両入力側ディスクとは独立した回転を自在として支持されている。
又、上記各パワーローラは、上記出力側ディスクの両側面と上記両入力側ディスクの側面との間にそれぞれ複数個ずつ挟持されて、これら入力側ディスクと出力側ディスクとの間で動力を伝達するものである。 The toroidal type continuously variable transmission is of a double cavity type and includes a pair of input side disks, an output side disk, and a plurality of power rollers.
Each of the input side disks is supported concentrically and freely in a synchronized manner via the input rotation shaft.
The output side disk is supported between the two input side disks so as to be concentric with the two input side disks and to rotate independently of the two input side disks.
Each of the power rollers is sandwiched between both side surfaces of the output side disk and the side surfaces of both input side disks, and transmits power between the input side disk and the output side disk. To do.

更に、上記動力伝達機構は、第一動力伝達部材（例えば、出力歯車、出力スプロケット等）と、第二動力伝達部材（例えば、伝達歯車、伝達スプロケット等）とを備える。
このうちの第一動力伝達部材は、上記出力側ディスクと同心に設けられて、この出力側ディスクと同期して回転する。
又、上記第二動力伝達部材は、上記回転伝達軸と同心に設けられて、この回転伝達軸と同期して回転する
そして、上記第一、第二両動力伝達部材を介して、上記出力側ディスクと上記回転伝達軸との間で動力の伝達を行なう。 Further, the power transmission mechanism includes a first power transmission member (for example, an output gear, an output sprocket, etc.) and a second power transmission member (for example, a transmission gear, a transmission sprocket, etc.).
Of these, the first power transmission member is provided concentrically with the output side disk, and rotates in synchronization with the output side disk.
Further, the second power transmission member is provided concentrically with the rotation transmission shaft and rotates in synchronization with the rotation transmission shaft. And, the output side via the first and second power transmission members. Power is transmitted between the disk and the rotation transmission shaft.

又、上記正転逆転切換機構（前後進切換機構）は、正転用動力伝達部材（例えば正転用歯車）と、逆転用動力伝達部材（例えば逆転用歯車）と、正転用クラッチ（前進クラッチ）と、逆転用クラッチ（後退クラッチ）とを備えたものである。
このうちの正転用動力伝達部材は、上記回転伝達軸と同心に設けられて、正転方向（前進方向）に対応する動力の伝達を行なう。
又、上記逆転用動力伝達部材は、同じく上記回転伝達軸と同心に設けられて、逆転方向（後退方向）に対応する動力の伝達を行なう。
尚、これら動力伝達部材としてスプロケットを使用する場合は、何れか一方の動力伝達部材のみとし、他方の動力伝達部材は歯車として、回転方向の変換を可能とする。
又、上記正転用クラッチは、上記動力の伝達方向に関し、上記回転伝達軸と上記正転用動力伝達部材との間に設けられて、これら回転伝達軸と正転用動力伝達部材との間で動力の伝達を行なう状態（接続した状態）と行なわない状態（接続を断った状態）とを切り換える。
又、上記逆転用クラッチは、同じく上記回転伝達軸と上記逆転用動力伝達部材との間に設けられて、これら回転伝達軸と逆転用動力伝達部材との間で動力の伝達を行なう状態（接続した状態）と行なわない状態（接続を断った状態）とを切り換える。 The forward / reverse switching mechanism (forward / reverse switching mechanism) includes a forward power transmission member (for example, a forward gear), a reverse power transmission member (for example, a reverse gear), and a forward clutch (forward clutch). And a reverse clutch (reverse clutch).
Among these, the power transmission member for normal rotation is provided concentrically with the rotation transmission shaft, and transmits power corresponding to the normal rotation direction (forward direction).
The reverse power transmission member is also provided concentrically with the rotation transmission shaft, and transmits power corresponding to the reverse direction (reverse direction).
In the case where sprockets are used as these power transmission members, only one of the power transmission members is used, and the other power transmission member is used as a gear so that the rotation direction can be changed.
The forward rotation clutch is provided between the rotation transmission shaft and the forward rotation power transmission member with respect to the power transmission direction, and power is transmitted between the rotation transmission shaft and the forward rotation power transmission member. The state of transmission (connected state) and the state of not transmitting (connected state) are switched.
The reverse clutch is also provided between the rotation transmission shaft and the reverse power transmission member, and transmits power between the rotation transmission shaft and the reverse power transmission member (connection). Switch between a state that has been disconnected) and a state that is not to be performed (the state in which the connection has been disconnected).

そして、上記正転用、逆転用各クラッチのうちの少なくとも一方のクラッチを構成するクラッチハウジングを、上記第二動力伝達部材に組み込む。
この為に例えば、請求項２に記載した様に、第二動力伝達部材の片側面部分にアウタドラムを結合固定する事により、上記一方のクラッチを構成するクラッチハウジングを上記第二動力伝達部材に組み込む。
又、好ましくは、請求項３に記載した様に、上記一方のクラッチに遠心油圧キャンセル室を設ける。 A clutch housing that constitutes at least one of the forward rotation and reverse rotation clutches is incorporated into the second power transmission member.
For this purpose, for example , as described in claim 2, an outer drum is coupled and fixed to one side surface portion of the second power transmission member, thereby incorporating the clutch housing constituting the one clutch into the second power transmission member. .
Preferably, as described in claim 3, a centrifugal hydraulic pressure canceling chamber is provided in the one clutch.

又、上述の様な無段変速装置を実施する場合に好ましくは、請求項４に記載した様に、正転逆転切換機構（前後進切換機構）を、（例えばはす歯歯車等の）歯車機構により構成する。そして、上記正転用動力伝達部材を構成する正転用歯車（例えば前進用歯車）を、上記出力回転軸に設けた第一出力用歯車に直接噛合させると共に、上記逆転用動力伝達部材を構成する逆転用歯車（例えば後退用歯車）を、上記出力回転軸に設けた第二出力用歯車に、アイドル歯車を介して噛合させる。 In the case of implementing the continuously variable transmission as described above, preferably, the forward / reverse switching mechanism (forward / reverse switching mechanism) is replaced with a gear (such as a helical gear) as described in claim 4. Configure by mechanism. Then, the forward rotation gear (for example, the forward gear) constituting the forward rotation power transmission member is directly meshed with the first output gear provided on the output rotation shaft, and the reverse rotation constituting the reverse rotation power transmission member. A gear (for example, a reverse gear) is engaged with a second output gear provided on the output rotation shaft via an idle gear.

又、好ましくは、請求項５に記載した様に、出力側ディスクを単一の部材により構成する（一体型の出力側ディスクとする）。又、これと共に、この出力側ディスクの軸方向中間部外周面に第一動力伝達部材（例えば出力歯車）を設ける。そして、この第一動力伝達部材から第二動力伝達部材（例えば伝達歯車）に動力を、増速した状態で伝達自在とする。尚、上記第一動力伝達部材は、例えば前述の特許文献３、４に記載された構造（図８に示した構造）の様に、上記出力側ディスクと別体の部材とし、この出力側ディスクに結合固定（同期した回転を自在に結合）する事により構成する他、一体型の出力側ディスクに直接固設する（出力側ディスクに第一動力伝達部材も一体に設ける）事により構成する事もできる。
又、好ましくは、請求項６に記載した様に、回転伝達軸の軸方向に関し、第二動力伝達部材を、正転用動力伝達部材と逆転用動力伝達部材との間に設ける。 Preferably, as described in claim 5, the output side disk is constituted by a single member (set as an integrated output side disk). Along with this, a first power transmission member (for example, an output gear) is provided on the outer peripheral surface of the axially intermediate portion of the output side disk. Then, power can be transmitted from the first power transmission member to a second power transmission member (for example, a transmission gear) in an accelerated state. The first power transmission member is a separate member from the output side disk as in the structure described in Patent Documents 3 and 4 described above (the structure shown in FIG. 8). In addition to being configured to be coupled and fixed (synchronized rotation is freely coupled), it is also configured to be directly fixed to an integrated output side disk (the first power transmission member is also provided integrally with the output side disk). You can also.
Preferably, as described in claim 6, with respect to the axial direction of the rotation transmission shaft, the second power transmission member is provided between the forward rotation power transmission member and the reverse rotation power transmission member.

上述の様な本発明によれば、無段変速装置を、小型、且つ、簡素に構成でき、しかも、回転伝達軸の軸方向寸法の短縮も図れる。
即ち、前後進切換機構として、例えば前述の図８に示した様な遊星歯車式変速機１７ａを組み込まない為、この正転逆転切換機構を簡素に構成できる。又、これと共に、この様な遊星歯車式変速機１７ａを組み込んだ構造に比べ、回転伝達軸の周囲に配置される部材の径方向寸法を小さくできる。この為、トロイダル型無段変速機（の中心軸である入力回転軸）と正転逆転切換機構（の中心軸である回転伝達軸）とを近接させる事ができ、無段変速装置全体として小型に構成できる。しかも、正転用、逆転用各クラッチのうちの少なくとも一方のクラッチを構成するクラッチハウジングを、第二動力伝達部材に組み込んでいる為、上記回転伝達軸の軸方向寸法が徒に大きくなる事も防止できる。この為、この面からも無段変速装置全体として小型化を図れる。 According to the present invention as described above, the continuously variable transmission can be configured to be small and simple, and the axial dimension of the rotation transmission shaft can be shortened.
That is, since the planetary gear type transmission 17a as shown in FIG. 8 is not incorporated as the forward / reverse switching mechanism, for example, the forward / reverse switching mechanism can be simply configured. At the same time, the radial dimension of the members arranged around the rotation transmission shaft can be reduced as compared with the structure incorporating such a planetary gear type transmission 17a. For this reason, the toroidal continuously variable transmission (the input rotation shaft that is the central axis) and the forward / reverse switching mechanism (the rotation transmission shaft that is the central axis) can be brought close to each other, and the entire continuously variable transmission is small Can be configured. In addition, since the clutch housing that constitutes at least one of the forward and reverse clutches is incorporated in the second power transmission member , the axial dimension of the rotation transmission shaft is prevented from becoming too large. it can. For this reason, the size of the continuously variable transmission as a whole can be reduced also from this aspect.

更に、上記第二動力伝達部材により、油圧室に導入される油圧を受ける事ができる為、上記クラッチハウジングの剛性を確保し易い。この為、上記一方のクラッチの応答性の向上を図れ、クラッチ制御の安定化を図れる。又、請求項３に記載した様に、上記一方のクラッチに遠心油圧キャンセル室を設ければ、この遠心油圧キャンセル室の存在に拘わらず、上記一方のクラッチ、延いては、回転伝達軸の軸方向寸法が徒に大きくなる事を防止できる（遠心油圧キャンセル室を設ける事に伴う軸方向寸法の増大の程度を、小さく抑えられる）。 Furthermore, since the hydraulic pressure introduced into the hydraulic chamber can be received by the second power transmission member, it is easy to ensure the rigidity of the clutch housing. Therefore, the response of the one clutch can be improved, and the clutch control can be stabilized. Further, as described in claim 3, if the one clutch is provided with a centrifugal oil pressure canceling chamber, the one clutch, and further the shaft of the rotation transmission shaft, regardless of the existence of the centrifugal oil pressure canceling chamber. It is possible to prevent the dimensional dimension from becoming too large (the degree of increase in the axial dimension associated with the provision of the centrifugal hydraulic pressure canceling chamber can be kept small).

又、請求項４に記載した様に、正転逆転切換機構（前後進切換機構）を歯車機構とすれば、（例えばスプロケットとチェンとにより構成する場合等に比べて）より簡素に構成できる。しかも、例えば自動車の変速装置等で一般的に使用されているはす歯歯車により構成すれば、上記正転逆転切換機構を簡素、且つ、廉価に構成できる。
又、請求項５に記載した構成を採用した場合には、出力側ディスクの一体化によりトロイダル型無段変速機の軸方向寸法を低減できると共に、増速した状態で動力を伝達する為、クラッチ容量の低減を図れる。この為、このクラッチの軸方向、径方向寸法の低減を図れ（小型のものにでき）、更なる無段変速装置の小型化を図れる。
又、請求項６に記載した構成を採用した場合には、トロイダル型無段変速機の出力側ディスクを中心として、この出力側ディスクの軸方向両側に存在する各キャビティに、正転用、逆転用各動力伝達部材をそれぞれ対向させられる。言い換えれば、これら正転用、逆転用各動力伝達部材並びにこれら各部材に近接した状態で設ける部材を、空間に余裕のある各キャビティに対向させる事ができる。この為、上記トロイダル型無段変速機（入力回転軸）と上記正転逆転切換機構（回転伝達軸）とを更に近接させる事ができ、無駄な空間の低減、延いては、無段変速装置全体の更なる小型化を図れる。 Further, as described in claim 4, if the forward / reverse switching mechanism (forward / reverse switching mechanism) is a gear mechanism, it can be configured more simply (compared to, for example, a sprocket and chain). Moreover, for example, if it is constituted by a helical gear generally used in an automobile transmission or the like, the forward / reverse switching mechanism can be constructed simply and inexpensively.
Further, when the configuration described in claim 5 is adopted, the axial dimension of the toroidal-type continuously variable transmission can be reduced by integrating the output side disk, and the power is transmitted in an accelerated state. Capacity can be reduced. For this reason, the axial and radial dimensions of the clutch can be reduced (can be reduced in size), and the further continuously variable transmission can be further reduced in size.
Further, when the configuration described in claim 6 is adopted, the output side disc of the toroidal type continuously variable transmission is centered on each cavity on both sides in the axial direction of the output side disc for forward rotation and reverse rotation. Each power transmission member can be made to oppose. In other words, the power transmission members for normal rotation and reverse rotation and the members provided close to these members can be opposed to the cavities with sufficient space. For this reason, the toroidal type continuously variable transmission (input rotation shaft) and the forward / reverse switching mechanism (rotation transmission shaft) can be brought closer to each other, thereby reducing useless space, and thus the continuously variable transmission. The overall size can be further reduced.

図１〜５は、本発明の実施の形態の１例を示している。本例の無段変速装置は、入力回転軸１ａと、トロイダル型無段変速機２１ａと、回転伝達軸２２ａと、動力伝達機構２９と、出力回転軸３０と、特許請求の範囲に記載した正転逆転切換機構に相当する前後進切換機構３１とを備える。
このうちの入力回転軸１ａは、トルクコンバータ３２並びに駆動軸１５ａを介して、エンジン等の駆動源（動力源）からの動力が入力される。この様な入力回転軸１ａは、ケーシング等の固定の部分に対し、回転自在に設けられている。又、上記トロイダル型無段変速機２１ａは、上記入力回転軸１ａと同心に設けられている。又、上記回転伝達軸２２ａは、上記動力の伝達方向に関し、上記入力回転軸１ａよりも下流側に、その両端部に設けた１対の円すいころ軸受３３、３３により上記ケーシング等の固定の部分に対し回転自在に支持された状態で、上記入力回転軸１ａと平行に設けられている。 1 to 5 show an example of an embodiment of the present invention. The continuously variable transmission of this example includes an input rotary shaft 1a, a toroidal continuously variable transmission 21a, a rotation transmission shaft 22a, a power transmission mechanism 29, an output rotary shaft 30, and the positive rotation speed described in the claims. A forward / reverse switching mechanism 31 corresponding to a rotation / reverse switching mechanism is provided.
Of these, the input rotary shaft 1a receives power from a drive source (power source) such as an engine via the torque converter 32 and the drive shaft 15a. Such an input rotating shaft 1a is rotatably provided to a fixed part such as a casing. The toroidal continuously variable transmission 21a is provided concentrically with the input rotary shaft 1a. The rotation transmission shaft 22a is fixed to the casing or the like by a pair of tapered roller bearings 33, 33 provided at both ends thereof on the downstream side of the input rotation shaft 1a in the power transmission direction. Is provided in parallel with the input rotation shaft 1a in a state of being rotatably supported.

又、上記動力伝達機構２９は、上記トロイダル型無段変速機２１ａと上記回転伝達軸２２ａとの間で動力の伝達を行なうものである。又、上記出力回転軸３０は、上記動力の伝達方向に関し、上記回転伝達軸２２ａよりも下流側に、その両端部に設けた別の１対の円すいころ軸受３４、３４により上記ケーシング等の固定の部分に対し回転自在に支持された状態で、上記回転伝達軸２２ａと平行に設けられている。又、上記前後進切換機構３１は、上記動力の伝達方向に関し、上記回転伝達軸２２ａと出力回転軸３０との間に設けられて、この出力回転軸３０から出力される動力の回転方向を正転、逆転（前進方向に対応する方向、後退方向に対応する方向）に切り換えるものである。 The power transmission mechanism 29 transmits power between the toroidal type continuously variable transmission 21a and the rotation transmission shaft 22a. The output rotating shaft 30 is fixed to the casing or the like by another pair of tapered roller bearings 34, 34 provided at both ends thereof on the downstream side of the rotation transmitting shaft 22a in the power transmission direction. And is provided in parallel with the rotation transmission shaft 22a in a state of being rotatably supported with respect to this portion. Further, the forward / reverse switching mechanism 31 is provided between the rotation transmission shaft 22a and the output rotation shaft 30 with respect to the power transmission direction, and the rotation direction of the power output from the output rotation shaft 30 is set to be normal. The rotation is switched to reverse rotation (direction corresponding to the forward direction, direction corresponding to the backward direction).

又、上記トロイダル型無段変速機２１ａは、ダブルキャビティ型のもので、１対の入力側ディスク２ａ、２ｂと、出力側ディスク１０と、複数個のパワーローラ１２、１２（図６〜８参照）とを備える。このうちの各入力側ディスク２ａ、２ｂは、上記入力回転軸１ａを介して互いに同心に、且つ、同期した回転を自在として支持されている。又、上記出力側ディスク１０は、上記両入力側ディスク２ａ、２ｂ同士の間に、これら両入力側ディスク２ａ、２ｂと同心に、且つ、これら両入力側ディスク２ａ、２ｂとは独立した回転を自在として支持されている。本例の場合、それぞれのキャビティに１対の支柱３６、３６を、ケーシング等の固定の部分にアクチュエータボディ３５を介して支持した状態で設けている。そして、上記各支柱３６、３６の中間部に設けた支持環３７、３７に、上記出力側ディスク１０の軸方向両端部を、スラスト玉軸受３８、３８を介して回転自在に支持している。上記入力回転軸１ａは、上述の様に支持された出力側ディスク１０の中心部に設けた貫通孔３９に、ラジアルニードル軸受４０、４０を介して回転自在に、且つ、軸方向の変位を自在に支持されている。この様な入力回転軸１ａは、油圧式の押圧装置１６ａが発生する押圧力に応じて（押圧装置１６ａを構成する油圧室４１の拡縮に応じて）、一方（図１の左方）の入力側ディスク２ａに対し、他方（図１の右方）の入力側ディスク２ｂと共に、軸方向に変位する。 The toroidal type continuously variable transmission 21a is of a double cavity type, and includes a pair of input side disks 2a, 2b, an output side disk 10, and a plurality of power rollers 12, 12 (see FIGS. 6 to 8). ). Each of the input side disks 2a and 2b is supported concentrically and freely in a synchronized manner via the input rotation shaft 1a. The output side disk 10 rotates between the input side disks 2a and 2b concentrically with the input side disks 2a and 2b and independently of the input side disks 2a and 2b. It is supported as free. In the case of this example, a pair of support columns 36 are provided in each cavity in a state of being supported via a actuator body 35 on a fixed part such as a casing. The axial ends of the output-side disk 10 are rotatably supported via thrust ball bearings 38 and 38 on support rings 37 and 37 provided at intermediate portions of the columns 36 and 36. The input rotary shaft 1a can be freely rotated through the through hole 39 provided in the central portion of the output side disk 10 supported as described above via the radial needle bearings 40 and 40 and can be displaced in the axial direction. It is supported by. Such an input rotating shaft 1a has one input (left side in FIG. 1) according to the pressing force generated by the hydraulic pressing device 16a (according to expansion / contraction of the hydraulic chamber 41 constituting the pressing device 16a). Along with the other input side disk 2b (to the right in FIG. 1), the side disk 2a is displaced in the axial direction.

又、上記各パワーローラ１２、１２は、前述の図６に示した構造と同様に、上記出力側ディスク１０の両側面と上記両入力側ディスク２ａ、２ｂの側面との間にそれぞれ複数個ずつ挟持されて、これら入力側ディスク２ａ、２ｂと出力側ディスク１０との間で動力を伝達する。又、上記各パワーローラ１２、１２はそれぞれ、上記入力回転軸１ａに対し捩れの位置にある枢軸を中心とする揺動変位を自在に設けられたトラニオン（支持部材）１４、１４（図６、８参照）の内側面に、回転及び若干の揺動変位自在に支持されている。これら各トラニオン１４、１４を傾斜させる（トロイダル型無段変速機２１ａの変速比を変更する）動作は、アクチュエータボディ３５内に設けた図示しない油圧式のアクチュエータにより、上記各トラニオン１４、１４を上記枢軸の軸方向に変位させる事により行なう。 Each of the power rollers 12 and 12 has a plurality of each between the both side surfaces of the output side disk 10 and the side surfaces of the both input side disks 2a and 2b, similarly to the structure shown in FIG. The power is transmitted between the input side disks 2a and 2b and the output side disk 10 by being sandwiched. The power rollers 12 and 12 are trunnions (support members) 14 and 14 (FIG. 6, FIG. 6), each of which is provided with a swinging displacement about a pivot that is twisted with respect to the input rotary shaft 1a. 8) is supported so as to be freely rotatable and slightly swingable. The operation of inclining each of the trunnions 14 and 14 (changing the transmission ratio of the toroidal type continuously variable transmission 21a) is performed by using the hydraulic actuator (not shown) provided in the actuator body 35 to cause the trunnions 14 and 14 to This is done by displacing in the axial direction of the pivot axis.

更に、上記動力伝達機構２９は、上記出力側ディスク１０の軸方向中間部外周面に設けた、特許請求の範囲に記載した第一動力伝達部材に相当する出力歯車９ａと、上記回転伝達軸２２ａと同心に設けた、特許請求の範囲に記載した第二動力伝達部材に相当する伝達歯車４２とを備える。そして、これら出力歯車９ａと伝達歯車４２とを直接噛合させ、これら出力歯車９ａと伝達歯車４２との間（出力側ディスク１０と回転伝達軸２２ａとの間）で動力の伝達を自在としている。本例の場合は、上記出力側ディスク１０を単一の部材により構成している。そして、この出力側ディスク１０の軸方向中間部外周面に上記出力歯車９ａを、直接形成（固設）している。又、本例の場合は、この様な出力歯車９ａから伝達歯車４２に上記動力を、増速した状態で伝達自在としている。即ち、上記出力歯車９ａに比べて伝達歯車４２の歯数を少なく（外径を小さく）している。 Further, the power transmission mechanism 29 includes an output gear 9a corresponding to the first power transmission member described in the claims provided on the outer peripheral surface of the output side disk 10 in the axial direction, and the rotation transmission shaft 22a. And a transmission gear 42 corresponding to the second power transmission member described in the claims. The output gear 9a and the transmission gear 42 are directly meshed with each other so that power can be freely transmitted between the output gear 9a and the transmission gear 42 (between the output side disk 10 and the rotation transmission shaft 22a). In the case of this example, the output side disk 10 is constituted by a single member. The output gear 9 a is directly formed (fixed) on the outer circumferential surface of the intermediate portion in the axial direction of the output side disk 10. In this example, the power can be transmitted from the output gear 9a to the transmission gear 42 in an accelerated state. That is, the number of teeth of the transmission gear 42 is smaller (outer diameter is smaller) than that of the output gear 9a .

又、前記前後進切換機構３１は、歯車機構（本例の場合ははすば歯車）により構成したもので、特許請求の範囲に記載した正転用動力伝達部材並びに正転用歯車に相当する前進用歯車４３と、同じく逆転用動力伝達部材並びに逆転用歯車に相当する後退用歯車４４と、第一、第二各出力用歯車４５、４６と、アイドル歯車４７とを備える。又、これと共に、それぞれが特許請求の範囲に記載したクラッチを構成し、この特許請求の範囲に記載した正転用クラッチに相当する前進クラッチ４８と、同じく逆転用クラッチに相当する後退クラッチ４９とを備える。これらのうちの上記前進用歯車４３は、上記回転伝達軸２２ａの中間部で、上記伝達歯車４２と軸方向に隣り合う位置に、ラジアルニードル軸受５０を介して回転自在に支持されている。又、上記後退用歯車４４は、上記回転伝達軸２２ａの他端寄り部分（図１、３、４の右端寄り部分）に、別のラジアルニードル軸受５１を介して回転自在に支持されている。尚、上記伝達歯車４２は、上記回転伝達軸２２ａの中間部で、上記前進用、後退用各歯車４３、４４の間部分に、この回転伝達軸２２ａと同期した回転を自在に（例えばスプライン係合、キー係合等により）支持されている。 The forward / reverse switching mechanism 31 is constituted by a gear mechanism (helical gear in the case of this example), and the forward rotation power transmission member and the forward rotation gear corresponding to the forward rotation gear described in the claims. The gear 43 includes a reverse gear 44 corresponding to the reverse power transmission member and the reverse gear, first and second output gears 45 and 46, and an idle gear 47. Along with this, each of the clutches described in the claims constitutes a forward clutch 48 corresponding to the forward rotation clutch described in the claims, and a reverse clutch 49 also corresponding to the reverse rotation clutch. Prepare. Of these, the forward gear 43 is rotatably supported via a radial needle bearing 50 at a position adjacent to the transmission gear 42 in the axial direction at an intermediate portion of the rotation transmission shaft 22a. The reverse gear 44 is rotatably supported via another radial needle bearing 51 at a portion near the other end of the rotation transmission shaft 22a (a portion near the right end in FIGS. 1, 3 and 4). The transmission gear 42 can freely rotate in the middle of the rotation transmission shaft 22a between the forward and reverse gears 43, 44 in synchronization with the rotation transmission shaft 22a (for example, a spline engagement). (For example, by key engagement).

又、上記第一出力用歯車４５は、上記出力回転軸３０の一端寄り部分（図１、３、５の左端寄り部分）に、上記前進用歯車４３と直接噛合した状態で、上記出力回転軸３０と同期した回転を自在に（例えばスプライン係合、キー係合等により）支持している。又、上記第二出力用歯車４６は、上記出力回転軸３０の他端寄り部分（図１、３、５の右端寄り部分）に、上記アイドル歯車４７を介して上記後退用歯車４４と噛合した状態で、上記出力回転軸３０と同期した回転を自在に（例えばスプライン係合、キー係合等により）支持されている。上記第一出力用歯車４５は、上記回転伝達軸２２ａと逆方向（前進方向に対応する方向）に回転するのに対して、上記第二出力用歯車４６は、上記回転伝達軸２２ａと同方向（後退方向に対応する方向）に回転する。又、この出力回転軸３０の他端寄り部分で、上記第二出力用歯車４６と軸方向に隣り合う位置に、第三出力用歯車５２を直接形成している。そして、この第三出力用歯車５２をデファレンシャルギヤの入力歯車５３に噛合させ、１対の車輪駆動軸５４を回転駆動自在としている。 Further, the first output gear 45 is in a state in which the first output gear 45 is directly meshed with the forward gear 43 at a portion near one end of the output rotary shaft 30 (portion near the left end in FIGS. 1, 3 and 5). Rotation synchronized with 30 is supported freely (for example, by spline engagement, key engagement, etc.). The second output gear 46 meshes with the reverse gear 44 via the idle gear 47 at the other end portion (the right end portion in FIGS. 1, 3, and 5) of the output rotating shaft 30. In this state, the rotation synchronized with the output rotation shaft 30 is supported freely (for example, by spline engagement, key engagement, etc.). The first output gear 45 rotates in the direction opposite to the rotation transmission shaft 22a (the direction corresponding to the forward direction), whereas the second output gear 46 has the same direction as the rotation transmission shaft 22a. Rotate in the direction corresponding to the backward direction. A third output gear 52 is formed directly at a position near the other end of the output rotating shaft 30 at a position adjacent to the second output gear 46 in the axial direction. The third output gear 52 is meshed with an input gear 53 of a differential gear so that the pair of wheel drive shafts 54 can be driven to rotate.

又、前記前進、後退各クラッチ４８、４９は、駆動源からの動力の伝達方向に関し、前記トロイダル型無段変速機２１ａよりも下流側、即ち、本例の場合は、前記回転伝達軸２２ａの周囲に設けている。このうちの前進クラッチ４８は、動力の伝達方向に関し、上記回転伝達軸２２ａと上記前進用歯車４３との間に設けられ、これら回転伝達軸２２ａと前進用歯車４３との間で動力の伝達を行なう状態（接続した状態）と行なわない状態（接続を断った状態）とを切り換える。又、上記後退クラッチ４９は、動力の伝達方向に関し、上記回転伝達軸２２ａと上記後退用歯車４４との間に設けられ、これら回転伝達軸２２ａと後退用歯車４４との間で動力の伝達を行なう状態（接続した状態）と行なわない状態（接続を断った状態）とを切り換える。これら前進、後退各クラッチ４８、４９は、運転者のシフトレバー（操作レバー）の操作に応じて、進行方向に対応する何れか一方のクラッチ４８（４９）が接続される。 Further, the forward and reverse clutches 48 and 49 are downstream of the toroidal-type continuously variable transmission 21a with respect to the direction of transmission of power from the drive source, that is, in this example, the rotation transmission shaft 22a. It is provided around. Of these, the forward clutch 48 is provided between the rotation transmission shaft 22a and the forward gear 43 with respect to the direction of power transmission, and transmits power between the rotation transmission shaft 22a and the forward gear 43. Switching between a state to be performed (connected state) and a state not to be performed (state disconnected). The reverse clutch 49 is provided between the rotation transmission shaft 22a and the reverse gear 44 in the power transmission direction, and transmits power between the rotation transmission shaft 22a and the reverse gear 44. Switching between a state to be performed (connected state) and a state not to be performed (state disconnected). Each of the forward and reverse clutches 48 and 49 is connected to one of the clutches 48 (49) corresponding to the traveling direction in accordance with the operation of the shift lever (operating lever) by the driver.

この様な前進、後退各クラッチ４８、４９は、それぞれ湿式多板クラッチとしている。このうちの前進クラッチ４８は、クラッチハウジング５５ａと、ピストン５６ａと、アウタドラム５７ａと、複数枚のプレッシャプレート５８ａ、５８ａと、インナドラム５９ａと、複数枚のクラッチディスク６０ａ、６０ａと、圧縮コイルばね６１ａと、止め輪６７ａとを備える。このうちのクラッチハウジング５５ａは、上記回転伝達軸２２ａと同期した回転を自在に、この回転伝達軸２２ａに支持されている。又、上記ピストン５６ａは、上記クラッチハウジング５５ａの内側に油密に嵌装されている。そして、上記回転伝達軸２２ａの軸方向に関して互いに対向する、上記ピストン５６ａの側面と上記クラッチハウジング５５ａの内面との間部分を、油圧室６２ａとしている。 Each of the forward and reverse clutches 48 and 49 is a wet multi-plate clutch. The forward clutch 48 includes a clutch housing 55a, a piston 56a, an outer drum 57a, a plurality of pressure plates 58a and 58a, an inner drum 59a, a plurality of clutch disks 60a and 60a, and a compression coil spring 61a. And a retaining ring 67a. Of these, the clutch housing 55a is supported by the rotation transmission shaft 22a so as to freely rotate in synchronization with the rotation transmission shaft 22a. The piston 56a is oil-tightly fitted inside the clutch housing 55a. A portion between the side surface of the piston 56a and the inner surface of the clutch housing 55a that are opposed to each other in the axial direction of the rotation transmission shaft 22a is a hydraulic chamber 62a.

又、上記アウタドラム５７ａは、上記クラッチハウジング５５ａと一体に設けられており、内周面に上記各プレッシャプレート５８ａ、５８ａを、軸方向の相対変位を可能に、且つ、回転方向の変位を不能（アウタドラム５７ａと同期した回転を自在に）に支持している。又、上記アウタドラム５７ａの内周面の開口寄り部分に上記止め輪６７ａを係止し、上記ピストン５６ａから最も遠いプレッシャプレート５８ａが上記アウタドラム５７ａから抜け出るのを阻止している。又、上記インナドラム５９ａは、前記前進用歯車４３の側面に固設されており、外周面に上記各クラッチディスク６０ａ、６０ａを、軸方向の相対変位を可能に、且つ、回転方向の変位を不能（インナドラム５９ａと同期した回転を自在）に支持している。 The outer drum 57a is provided integrally with the clutch housing 55a. The pressure plates 58a and 58a can be displaced relative to each other in the axial direction on the inner peripheral surface, and cannot be displaced in the rotational direction ( The rotation synchronized with the outer drum 57a is freely supported. Further, the retaining ring 67a is locked to a portion near the opening of the inner peripheral surface of the outer drum 57a to prevent the pressure plate 58a farthest from the piston 56a from coming out of the outer drum 57a. The inner drum 59a is fixed to the side surface of the forward gear 43, and the clutch disks 60a, 60a can be axially displaced on the outer peripheral surface and can be displaced in the rotational direction. It is impossible (rotation synchronized with the inner drum 59a is freely supported).

又、上記圧縮コイルばね６１ａは、上記インナドラム５９ａの内側に設けられて、上記クラッチハウジング５５ａとピストン５６ａとの間に、互いに軸方向に対向する側面同士が近付く方向（油圧室６２ａが狭まる方向）の弾力を付与している。上記油圧室６２ａに、上記回転伝達軸２２ａに設けた給油通路６３ａを通じて圧油が導入されると、上記圧縮コイルばね６１ａの弾力に抗して、上記ピストン５６ａが軸方向に変位する。この結果、このピストン５６ａと上記止め輪６７ａとの間で、上記各プレッシャプレート５８ａ、５８ａと各クラッチディスク６０ａ、６０ａとが挟持されて、上記回転伝達軸２２ａと前進用歯車４３との間で動力の伝達が可能になる（回転伝達軸２２ａと前進用歯車４３とが同期して回転する）。又、上記油圧室６２ａへの上記圧油の導入が断たれると（油溜に開放されると）、上記各プレッシャプレート５８ａ、５８ａと各クラッチディスク６０ａ、６０ａとの側面同士が近接対向乃至は滑り合い、上記回転伝達軸２２ａと前進用歯車４３との間で動力の伝達が行なわれなくなる。 The compression coil spring 61a is provided on the inner side of the inner drum 59a, and a direction in which side surfaces facing each other in the axial direction approach each other between the clutch housing 55a and the piston 56a (direction in which the hydraulic chamber 62a narrows). ) Elasticity. When pressure oil is introduced into the hydraulic chamber 62a through an oil supply passage 63a provided in the rotation transmission shaft 22a, the piston 56a is displaced in the axial direction against the elasticity of the compression coil spring 61a. As a result, the pressure plates 58a and 58a and the clutch disks 60a and 60a are sandwiched between the piston 56a and the retaining ring 67a, and the rotation transmission shaft 22a and the forward gear 43 are interposed. Power can be transmitted (the rotation transmission shaft 22a and the forward gear 43 rotate in synchronization). Further, when the introduction of the pressure oil into the hydraulic chamber 62a is cut off (when released to the oil reservoir), the side surfaces of the pressure plates 58a and 58a and the clutch disks 60a and 60a face each other. And the transmission of power is not performed between the rotation transmission shaft 22a and the forward gear 43.

又、上記後退クラッチ４９に就いても、上記前進クラッチ４８と同様に、クラッチハウジング５５ｂと、ピストン５６ｂと、アウタドラム５７ｂと、複数枚のプレッシャプレート５８ｂ、５８ｂと、インナドラム５９ｂと、複数枚のクラッチディスク６０ｂ、６０ｂと、圧縮コイルばね６１ｂと、止め輪６７ｂとを備える。この様な後退クラッチ４９を構成するこれら各部材５５ｂ、５６ｂ、５７ｂ、５８ｂ、５９ｂ、６０ｂ、６１ｂ、６７ｂは、上記前進クラッチ４８を構成する各部材５５ａ、５６ａ、５７ａ、５８ａ、５９ａ、６０ａ、６１ａ、６７ｂと同様の構成を有する。尚、上記後退クラッチ４９の油圧室６２ｂには、上記前進クラッチ４８の油圧室６２ａに圧油を導入する為の給油通路６３ａとは別の給油通路６３ｂを通じて、圧油が導入される。 Similarly to the forward clutch 48, the reverse clutch 49 also includes a clutch housing 55b, a piston 56b, an outer drum 57b, a plurality of pressure plates 58b and 58b, an inner drum 59b, and a plurality of sheets. Clutch disks 60b and 60b, a compression coil spring 61b, and a retaining ring 67b are provided. These members 55b, 56b, 57b, 58b, 59b, 60b, 61b, 67b constituting such a reverse clutch 49 are members 55a, 56a, 57a, 58a, 59a, 60a, constituting the forward clutch 48, respectively. It has the same configuration as 61a and 67b. The hydraulic oil is introduced into the hydraulic chamber 62b of the reverse clutch 49 through an oil supply passage 63b different from the oil supply passage 63a for introducing the pressure oil into the hydraulic chamber 62a of the forward clutch 48.

又、上記後退クラッチ４９の場合は、上記クラッチハウジング５５ｂを、前記伝達歯車４２の一部を利用して構成している。即ち、この伝達歯車４２の軸方向片側面に、この側面から凹入する状態で（油圧室６２ｂを構成する為の）環状の凹部６４を、全周に亙って設けている。そして、この凹部６４の開口縁（内周面）に上記アウタドラム５７ｂを、締り嵌め等により油密に嵌合固定（結合固定）する事により、上記クラッチハウジング５５ｂを上記伝達歯車４２の片側部分に、一体的に組み込んでいる。従って、上記回転伝達軸２２ａの軸方向に関して互いに対向する、上記ピストン５６ｂの側面と上記凹部６４の底面との間部分が、上記油圧室６２ｂとなる。又、上記後退クラッチ４９は、上記ピストン５６ｂを挟んでこの油圧室６２ｂと反対側に、遠心油圧キャンセル室６５を設けている。この遠心油圧キャンセル室６５を設ける為に、上記ピストン５６ｂにその外周縁部を、油密に、且つ、軸方向の相対変位を可能に内嵌した仕切板６９の内周縁部を、上記伝達歯車４２の内周縁部に形成した円筒部７１に、止め輪７０により係止している。前記圧縮コイルバネ６１ｂは、上記ピストン５６ｂと上記仕切板６９との間に設けている。又、上記遠心油圧キャンセル室６５には、上記油圧室６２ｂに圧油を導入する上記給油通路６３ｂとは別系統の潤滑油供給路６６を通じて、低圧の油を導入する。上記後退クラッチ４９の接続を断った状態（油圧室６２ｂに圧油を導入してない状態）で、遠心力に基づき上記油圧室６２ｂから油圧が抜けず、上記ピストン５６ｂに上記後退クラッチ４９を接続する方向の力が加わる傾向となっても、上記遠心油圧室キャンセル室６５内に存在する油にも同様に遠心力が加わる事で、上記力を相殺できる。即ち、上記ピストン５６ｂを挟んで軸方向両側に位置する両油圧室６２ｂ、６５から遠心力に基づく油圧の力がこのピストン５６ｂに、互いに相殺する方向に加わる。この為、運転時（特に前進時）の回転伝達軸２２ａの回転に拘わらず、上記後退クラッチ４９の接続を確実に断つ事ができ、この後退クラッチ４９の応答性の向上を図れる。 In the case of the reverse clutch 49, the clutch housing 55b is configured by using a part of the transmission gear 42. That is, an annular recess 64 (for constituting the hydraulic chamber 62b) is provided over the entire circumference on one side surface in the axial direction of the transmission gear 42 so as to be recessed from the side surface. The clutch housing 55b is fixed to one side portion of the transmission gear 42 by fitting and fixing the outer drum 57b to the opening edge (inner peripheral surface) of the recess 64 in an oil-tight manner by means of an interference fit or the like. , Integrated into one. Therefore, the portion between the side surface of the piston 56b and the bottom surface of the recess 64, which are opposed to each other in the axial direction of the rotation transmission shaft 22a, is the hydraulic chamber 62b. The reverse clutch 49 is provided with a centrifugal hydraulic pressure cancel chamber 65 on the opposite side of the hydraulic chamber 62b with the piston 56b interposed therebetween. In order to provide the centrifugal hydraulic pressure canceling chamber 65, the outer peripheral edge of the piston 56b, the inner peripheral edge of the partition plate 69 fitted in an oil-tight manner and capable of relative displacement in the axial direction, and the transmission gear are provided. A retaining ring 70 is engaged with a cylindrical portion 71 formed on the inner peripheral edge of 42. The compression coil spring 61b is provided between the piston 56b and the partition plate 69. Low pressure oil is introduced into the centrifugal oil pressure cancellation chamber 65 through a lubricating oil supply passage 66 that is a separate system from the oil supply passage 63b that introduces pressure oil into the hydraulic chamber 62b. In a state where the connection of the reverse clutch 49 is cut off (pressure oil is not introduced into the hydraulic chamber 62b), the hydraulic pressure is not released from the hydraulic chamber 62b based on centrifugal force, and the reverse clutch 49 is connected to the piston 56b. Even if the force in the direction to be applied tends to be applied, the force can be offset by applying the centrifugal force to the oil existing in the centrifugal hydraulic chamber cancel chamber 65 in the same manner. That is, the hydraulic force based on the centrifugal force is applied to the piston 56b in a direction that cancels each other out from both the hydraulic chambers 62b and 65 located on both sides in the axial direction across the piston 56b. For this reason, regardless of the rotation of the rotation transmission shaft 22a during operation (particularly during forward movement), the reverse clutch 49 can be reliably disconnected, and the response of the reverse clutch 49 can be improved.

上述の様な本例の構造によれば、無段変速装置を、小型、且つ、簡素に構成でき、しかも、回転伝達軸２２ａの軸方向寸法も低減できる。
即ち、前後進切換機構３１として、例えば前述の図８に示した様な遊星歯車式変速機１７ａ（図８）を組み込まない為、この前後進切換機構３１を簡素に構成できる。又、これと共に、この様な遊星歯車式変速機１７ａ（図８）を組み込んだ構造に比べ、回転伝達軸２２ａの周囲に配置される部材の径方向寸法を小さくできる。この為、この回転伝達軸２２ａと入力回転軸１ａとを近接させる事ができ、無段変速装置全体として小型に構成できる。しかも、前進、後退各クラッチ４８、４９のうちの少なくとも一方のクラッチである後退クラッチ４９を、伝達歯車４２の一部を利用して構成している。この為、これら後退クラッチ４９の一部と伝達歯車４２の一部とが、径方向に関して互いに重畳し、これら後退クラッチ４９の軸方向寸法と伝達歯車４２の軸方向寸法とが、そのまま足し合わされる事がなくなる。この結果、上記回転伝達軸２２ａの軸方向寸法が徒に大きくなる事も防止できて、この面からも無段変速装置全体として小型化を図れる。 According to the structure of this example as described above, the continuously variable transmission can be configured to be small and simple, and the axial dimension of the rotation transmission shaft 22a can also be reduced.
That is, since the planetary gear type transmission 17a (FIG. 8) as shown in FIG. 8 is not incorporated as the forward / reverse switching mechanism 31, for example, the forward / backward switching mechanism 31 can be simply configured. In addition, the radial dimension of the member disposed around the rotation transmission shaft 22a can be reduced as compared with the structure incorporating such a planetary gear type transmission 17a (FIG. 8). For this reason, the rotation transmission shaft 22a and the input rotation shaft 1a can be brought close to each other, and the entire continuously variable transmission can be made compact. In addition, the reverse clutch 49 which is at least one of the forward and reverse clutches 48 and 49 is configured by using a part of the transmission gear 42. Therefore, a part of the reverse clutch 49 and a part of the transmission gear 42 are overlapped with each other in the radial direction, and the axial dimension of the reverse clutch 49 and the axial dimension of the transmission gear 42 are added together. Things disappear. As a result, the axial dimension of the rotation transmission shaft 22a can be prevented from becoming too large, and the entire continuously variable transmission can be reduced in size from this aspect.

又、上記後退クラッチ４９を構成するクラッチハウジング５５ｂを上記伝達歯車４２に組み込んでいる為、この伝達歯車４２により油圧室６２ｂに導入される油圧を受ける事ができ、上記クラッチハウジング５５ｂの剛性を確保し易くできる。この為、上記後退クラッチ４９の応答性の向上を図れ、クラッチ制御の安定化を図れる。又、この様な後退クラッチ４９に遠心油圧キャンセル室６５を、径方向に重畳する状態で設けている為、この遠心油圧キャンセル室の存在に拘わらず、上記後退クラッチ４９、延いては、上記回転伝達軸２２ａの軸方向寸法が徒に大きくなる事を防止できる（軸方向寸法の増大の程度を小さく抑えられる）。 Further, since the clutch housing 55b constituting the reverse clutch 49 is incorporated in the transmission gear 42, the transmission gear 42 can receive the hydraulic pressure introduced into the hydraulic chamber 62b, and the rigidity of the clutch housing 55b is ensured. Easy to do. Therefore, the response of the reverse clutch 49 can be improved and the clutch control can be stabilized. In addition, since the centrifugal hydraulic pressure canceling chamber 65 is provided in such a reverse clutch 49 in a state of being superimposed in the radial direction, the reverse clutch 49 and the rotation of the rotational clutch canceling regardless of the existence of the centrifugal hydraulic pressure canceling chamber. It is possible to prevent the axial dimension of the transmission shaft 22a from becoming large (the degree of increase in the axial dimension can be kept small).

又、上記前後進切換機構３１を歯車機構とすると共に、自動車の変速装置等で一般的に使用されているはす歯歯車により構成している為、例えばスプロケットとチェンとにより構成する場合等に比べて、より簡素に、且つ、廉価に構成できる。又、出力側ディスク１０を単一の部材により構成している為、トロイダル型無段変速機２１ａの軸方向寸法を低減できる。又、これと共に、上記前進、後退各クラッチ４８、４９に増速した状態で動力を伝達する為、これら各クラッチ４８、４９のクラッチ容量の低減を図れる。この為、これら前進、後退各クラッチ４８、４９の軸方向、径方向寸法の低減を図れ（小型のものにでき）、更なる無段変速装置の小型化を図れる。 Further, since the forward / reverse switching mechanism 31 is a gear mechanism and is constituted by a helical gear generally used in an automobile transmission or the like, for example, when it is constituted by a sprocket and a chain, etc. Compared to this, it can be configured more simply and inexpensively. Moreover, since the output side disk 10 is comprised by the single member, the axial direction dimension of the toroidal type continuously variable transmission 21a can be reduced. At the same time, since the power is transmitted to the forward and reverse clutches 48 and 49 in an accelerated state, the clutch capacity of each of the clutches 48 and 49 can be reduced. For this reason, the axial and radial dimensions of the forward and reverse clutches 48 and 49 can be reduced (can be made smaller), and the continuously variable transmission can be further reduced in size.

又、本例の場合は、上記伝達歯車４２を、上記回転伝達軸２２ａの軸方向に関し、前進用、後退用各歯車４３、４４の間部分に設けている。この為、上記トロイダル型無段変速機２１ａの出力側ディスク１０を中心として、この出力側ディスク１０の軸方向両側に存在する各キャビティに、上記前進用、後退用各歯車４３、４４をそれぞれ対向させられる。言い換えれば、これら前進用、後退用各歯車４３、４４並びに前進、後退各クラッチ４８、４９を、空間に余裕のある各キャビティに対向させる事ができる。この為、上記トロイダル型無段変速機２１ａ（入力回転軸１ａ）と上記前後進切換機構３１（回転伝達軸２２ａ）とを更に近接させる事ができ、無駄な空間の低減、延いては、無段変速装置全体の更なる小型化を図れる。 In the case of this example, the transmission gear 42 is provided between the forward and reverse gears 43 and 44 in the axial direction of the rotation transmission shaft 22a. Therefore, the forward and reverse gears 43 and 44 are opposed to the cavities existing on both sides in the axial direction of the output side disk 10 around the output side disk 10 of the toroidal-type continuously variable transmission 21a. Be made. In other words, the forward and reverse gears 43 and 44 and the forward and backward clutches 48 and 49 can be opposed to the cavities with sufficient space. For this reason, the toroidal continuously variable transmission 21a (input rotation shaft 1a) and the forward / reverse switching mechanism 31 (rotation transmission shaft 22a) can be further brought closer to each other. Further downsizing of the entire step transmission can be achieved.

又、上記前進、後退各クラッチ４８、４９を上記回転伝達軸２２ａに設けている為、出力回転軸３０に設けた場合に比べて、これら各クラッチ４８、４９として小型のものを採用できる。即ち、例えば自動車の変速装置を構成する場合には、駆動源であるエンジンからファイナルギヤ（第三出力用歯車５２）までの間に大きく減速させる必要がある。そして、この様に減速され、トルクが増大した動力が入力される上記出力回転軸３０に、上記前進、後退各クラッチ４８、４９を設けると、これら各クラッチ４８、４９のクラッチ容量を確保すべく、大型化のもの（プレッシャプレート５８ａ、５８ｂ、クラッチディスク６０ａ、６０ｂの径が大きく、枚数の多いもの）にする必要がある。これに対して本例の場合には、上記回転伝達軸２２ａに上記前進、後退各クラッチ４８、４９を設けている為、クラッチ容量を小さくでき、その分、小型に構成できる。又、上記出力回転軸３０の構造が簡素に成り、その分この出力回転軸３０の加工が容易になって、コスト低減を図れる。 Further, since the forward and reverse clutches 48 and 49 are provided on the rotation transmission shaft 22a, smaller clutches 48 and 49 can be employed as compared with the case where they are provided on the output rotation shaft 30. That is, for example, in the case of configuring a transmission of an automobile, it is necessary to greatly reduce the speed between the engine that is a driving source and the final gear (the third output gear 52). When the forward and backward clutches 48 and 49 are provided on the output rotating shaft 30 to which the power with increased torque is input as described above, the clutch capacity of the clutches 48 and 49 should be secured. It is necessary to increase the size (the pressure plates 58a and 58b and the clutch disks 60a and 60b have a large diameter and a large number). On the other hand, in the case of this example, since the forward and reverse clutches 48 and 49 are provided on the rotation transmission shaft 22a, the clutch capacity can be reduced, and the size can be reduced accordingly. Further, the structure of the output rotary shaft 30 is simplified, and the machining of the output rotary shaft 30 is facilitated accordingly, and the cost can be reduced.

尚、本例の場合は、エンジンからの動力の伝達方向に関し、トロイダル型無段変速機２１ａの入力回転軸１ａよりも上流側に、発進装置を構成するトルクコンバータ３２を設けている。但し、前述した前進、後退各クラッチ４８、４９に発進クラッチとしての機能（例えば半クラッチ機能等）を持たせれば、上記トルクコンバータ３２を省略する事ができて、前記駆動軸１５ａ部分の軸方向に関する小型化を図れる。尚、上記前進、後退各クラッチ４８、４９や前述した押圧装置１６ａ等、圧油を必要とする分に導入する油圧を発生させる為のオイルポンプ６８（図２）は、上記駆動軸１５ａの回転に基づいて駆動される。 In the case of this example, a torque converter 32 constituting a starting device is provided upstream of the input rotary shaft 1a of the toroidal-type continuously variable transmission 21a with respect to the direction of transmission of power from the engine. However, if each of the forward and reverse clutches 48 and 49 has a function as a starting clutch (for example, a half clutch function), the torque converter 32 can be omitted, and the axial direction of the drive shaft 15a portion can be omitted. Can be miniaturized. Note that the oil pump 68 (FIG. 2) for generating hydraulic pressure to be introduced as much pressure oil as necessary, such as the forward and reverse clutches 48 and 49 and the pressing device 16a described above, rotates the drive shaft 15a. It is driven based on.

本発明の無段変速装置に組み込むトロイダル型無段変速機の構造に関しては、ハーフトロイダル型、フルトロイダル型の何れでも良い。 The structure of the toroidal type continuously variable transmission incorporated in the continuously variable transmission of the present invention may be either a half toroidal type or a full toroidal type.

本発明の実施の形態の１例を示す断面図。Sectional drawing which shows one example of embodiment of this invention. 図１の左方から見た図。The figure seen from the left side of FIG. アイドル歯車が噛合する面で切断した、図１と同様の断面図。Sectional drawing similar to FIG. 1 cut | disconnected in the surface which an idle gear meshes | engages. 回転伝達軸並びにこれに組み付けられた部材を取り出して示す断面図。Sectional drawing which takes out and shows the rotation transmission shaft and the member assembled | attached to this. 出力回転軸並びにこれに組み付けられた部材を取り出して示す断面図。Sectional drawing which takes out and shows the output rotating shaft and the member assembled | attached to this. トロイダル型無段変速機の１例を示す断面図。Sectional drawing which shows one example of a toroidal type continuously variable transmission. 従来構造の１例を示す断面図。Sectional drawing which shows an example of a conventional structure. 従来構造の別例を示す断面図。Sectional drawing which shows another example of a conventional structure.

Explanation of symbols

１、１ａ入力回転軸
２ａ、２ｂ入力側ディスク
３入力側内側面
４ケーシング
５隔壁部
６通孔
７出力筒
８転がり軸受
９、９ａ出力歯車
１０、１０ａ、１０ｂ出力側ディスク
１１出力側内側面
１２パワーローラ
１３周面
１４トラニオン
１５、１５ａ駆動軸
１６、１６ａ押圧装置
１７、１７ａ遊星歯車式変速機
１８前進クラッチ
１９後退クラッチ
２０、２０ａ前後進切換機構
２１、２１ａトロイダル型無段変速機
２２、２２ａ回転伝達軸
２３太陽歯車
２４遊星歯車
２５リング歯車
２６低速用クラッチ
２７高速用クラッチ
２８遊星軸
２９動力伝達機構
３０出力回転軸
３１前後進切換機構
３２トルクコンバータ
３３円すいころ軸受
３４円すいころ軸受
３５アクチュエータボディ
３６支柱
３７支持環
３８スラスト玉軸受
３９貫通孔
４０ラジアルニードル軸受
４１油圧室
４２伝達歯車
４３前進用歯車
４４後退用歯車
４５第一出力用歯車
４６第二出力用歯車
４７アイドル歯車
４８前進クラッチ
４９後退クラッチ
５０ラジアルニードル軸受
５１ラジアルニードル軸受
５２第三出力用歯車
５３入力歯車
５４車輪駆動軸
５５ａ、５５ｂクラッチハウジング
５６ａ、５６ｂピストン
５７ａ、５７ｂアウタドラム
５８ａ、５８ｂプレッシャプレート
５９ａ、５９ｂインナドラム
６０ａ、６０ｂクラッチディスク
６１ａ、６１ｂ圧縮コイルバネ
６２ａ、６２ｂ油圧室
６３ａ、６３ｂ給油通路
６４凹部
６５遠心油圧キャンセル室
６６潤滑油供給路
６７ａ、６７ｂ止め輪
６８オイルポンプ
６９仕切板
７０止め輪
７１円筒部 DESCRIPTION OF SYMBOLS 1, 1a Input rotating shaft 2a, 2b Input side disk 3 Input side inner surface 4 Casing 5 Partition part 6 Through-hole 7 Output cylinder 8 Rolling bearing 9, 9a Output gear 10, 10a, 10b Output side disk 11 Output side inner surface 12 Power roller 13 Peripheral surface 14 Trunnion 15, 15a Drive shaft 16, 16a Press device 17, 17a Planetary gear type transmission 18 Forward clutch 19 Reverse clutch 20, 20a Forward / reverse switching mechanism 21, 21a Toroidal type continuously variable transmission 22, 22a Rotation transmission shaft 23 Sun gear 24 Planetary gear 25 Ring gear 26 Low speed clutch 27 High speed clutch 28 Planetary shaft 29 Power transmission mechanism 30 Output rotation shaft 31 Forward / reverse switching mechanism 32 Torque converter 33 Tapered roller bearing 34 Tapered roller bearing 35 Actuator body 36 support 37 support ring 8 Thrust Ball Bearing 39 Through Hole 40 Radial Needle Bearing 41 Hydraulic Chamber 42 Transmission Gear 43 Forward Gear 44 Reverse Gear 45 First Output Gear 46 Second Output Gear 47 Idle Gear 48 Forward Clutch 49 Reverse Clutch 50 Radial Needle Bearing 51 radial needle bearing 52 third output gear 53 input gear 54 wheel drive shaft 55a, 55b clutch housing 56a, 56b piston 57a, 57b outer drum 58a, 58b pressure plate 59a, 59b inner drum 60a, 60b clutch disc 61a, 61b compression coil spring 62a, 62b Hydraulic chamber 63a, 63b Oil supply passage 64 Recessed portion 65 Centrifugal hydraulic cancel chamber 66 Lubricating oil supply passage 67a, 67b Retaining ring 68 Oil pump 69 Partition plate 70 Retaining ring 71 The cylindrical portion

Claims

An input rotary shaft to which power from the drive source is input;
Around the input rotation shaft, a toroidal continuously variable transmission provided concentrically with the input rotation shaft;
A rotation transmission shaft provided in parallel to the input rotation shaft on the downstream side of the input rotation shaft with respect to the transmission direction of the power,
A power transmission mechanism for transmitting power between the toroidal continuously variable transmission and the rotation transmission shaft;
With respect to the transmission direction of the power, an output rotation shaft provided in parallel to the rotation transmission shaft on the downstream side of the rotation transmission shaft,
A forward / reverse switching mechanism that is provided between the rotation transmission shaft and the output rotation shaft with respect to the power transmission direction and switches the rotation direction of the power output from the output rotation shaft between normal rotation and reverse rotation. And
Of these, the toroidal-type continuously variable transmission includes a pair of input-side disks supported concentrically and freely in synchronization with each other via the input rotation shaft, and between the two input-side disks. The output side disk supported concentrically with both the input side disks and independent of the both input side disks, and both side surfaces of the output side disk and the side surfaces of the both input side disks A plurality of power rollers that are sandwiched between each of them and that transmit power between the input side disk and the output side disk are provided.
The power transmission mechanism is provided concentrically with the output-side disk, and is provided concentrically with the first power transmission member that rotates in synchronization with the output-side disk, and with the rotation transmission shaft. A second power transmission member that rotates synchronously, and transmits power between the output side disk and the rotation transmission shaft via the first and second power transmission members,
The forward / reverse switching mechanism is provided concentrically with the rotation transmission shaft, and is provided concentrically with the forward transmission power transmission member for transmitting power corresponding to the forward rotation direction. A reverse rotation power transmission member for transmitting power corresponding to the reverse rotation direction, and the rotation transmission shaft provided between the rotation transmission shaft and the normal rotation power transmission member with respect to the power transmission direction. And a forward rotation clutch that switches between a state where power is transmitted and a state where power is not transmitted between the forward rotation power transmission member and the forward rotation power transmission member, and is also provided between the rotation transmission shaft and the reverse rotation power transmission member. A reverse clutch that switches between a state where power is transmitted and a state where power is not transmitted between the transmission shaft and the reverse power transmission member;
A clutch housing constituting at least one of the forward rotation and reverse rotation clutches is incorporated in the second power transmission member.
Continuously variable transmission.

The continuously variable transmission according to claim 1, wherein an outer drum is coupled and fixed to one side surface portion of the second power transmission member.

The continuously variable transmission according to any one of claims 1 to 2, wherein a centrifugal oil pressure cancellation chamber is provided in one of the clutches.

The forward / reverse switching mechanism is constituted by a gear mechanism, and the forward rotation gear constituting the forward rotation power transmission member is directly meshed with the first output gear provided on the output rotation shaft, and the reverse rotation power transmission member is The continuously variable transmission according to any one of claims 1 to 3, wherein the reverse rotation gear is configured to mesh with a second output gear provided on the output rotation shaft via an idle gear.

The output side disk is constituted by a single member, and a first power transmission member is provided on the outer peripheral surface in the axial direction of the output side disk, and the power is increased from the first power transmission member to the second power transmission member. The continuously variable transmission according to any one of claims 1 to 4, wherein the continuously variable transmission is capable of being transmitted in a fast state.

The continuously variable power transmission member according to any one of claims 1 to 5, wherein the second power transmission member is provided between the forward rotation power transmission member and the reverse rotation power transmission member with respect to the axial direction of the rotation transmission shaft. Transmission device.