JP3890798B2 - Oil passage structure of continuously variable transmission - Google Patents

Oil passage structure of continuously variable transmission Download PDF

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JP3890798B2
JP3890798B2 JP05055199A JP5055199A JP3890798B2 JP 3890798 B2 JP3890798 B2 JP 3890798B2 JP 05055199 A JP05055199 A JP 05055199A JP 5055199 A JP5055199 A JP 5055199A JP 3890798 B2 JP3890798 B2 JP 3890798B2
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driven
oil
shaft
chamber
piston
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JP2000249205A (en
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正志 荒井
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Suzuki Motor Co Ltd
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Suzuki Motor Co Ltd
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Description

【0001】
【発明の属する技術分野】
この発明は、無段変速機のオイル通路構造に係り、特にプーリの油圧室に発生する遠心油圧を打ち消すように遠心油圧キャンセル室を設けた無段変速機のオイル通路構造に関する。
【0002】
【従来の技術】
車両においては、内燃機関の特性がそのままの状態では不向きなので、内燃機関と駆動輪間の伝動経路に変速機を設けている。この変速機には、ギヤ列によって変速比を段階的に変化させる歯車変速機や、プーリとベルトとによって変速比を無段階に変化させる無段変速機がある。
【0003】
図11に示す如く、無段変速機102としては、駆動側プーリ(プライマリプーリ)104と、被動側プーリ(セカンダリプーリ)106と、駆動側プーリ104と被動側プーリ106とに巻掛けられた金属製のベルト108とからなるものがある。駆動側プーリ104は、内燃機関のクランク軸(図示せず)と同軸心上に配設された一の回転軸である駆動側軸(プライマリシャフト)110と、この駆動側軸110に固定した駆動側固定プーリ片(シーブ)112と、駆動側軸110に軸方向移動可能且つ回転不可能に装着した駆動側可動プーリ片(シーブ)114と、この駆動側可動プーリ部片114の外周縁部位に固定されて該駆動側可動プーリ部片114の背面側に向かって突出した駆動側シリンダ116と、駆動側可動プーリ部片114の背面側で外周面が駆動側シリンダ116の内周面に摺動可能に密着して駆動側油圧室118を形成して駆動側軸110に固定された駆動側ピストン120とからなる。この場合、駆動側油圧室118には、駆動側バルブ(プライマリバルブ)122の作動によって駆動側油圧(プライマリ圧)が作用するものである。また、駆動側シリンダ116には、駆動側ピストン120の外側面と共働して駆動側遠心油圧キャンセル室124を形成する駆動側キャンセル室壁126を設け、この駆動側遠心油圧キャンセル室124にバランサプラグ128からオイルを噴射させ、これにより、駆動側油圧室118に発生する遠心油圧を打ち消して、駆動側可動プーリ部片114が押圧されるのを防止している。
【0004】
また、被動側プーリ106は、駆動側軸110と平行に配設された他の回転軸である被動側軸(セカンダリシャフト)130と、この被動側軸130に固定した被動側固定プーリ片(シーブ)132と、被動側軸130に軸方向移動可能且つ回転不可能に装着した被動側可動プーリ片(シーブ)134と、この被動側可動プーリ部片134の外周縁部位に固定されて該被動側可動プーリ部片134の背面側に向かって突出した被動側シリンダ136と、被動側可動プーリ部片134の背面側で外周面が被動側シリンダ136の内周面に摺動可能に密着して被動側油圧室138を形成して被動側軸130に固定された被動側ピストン140と、この被動側ピストン140と被動側可動プーリ部片134の背面との間に設けられたシーブ押圧スプリング142とからなる。この場合、被動側油圧室138には、被動側バルブ(セカンダリバルブ)144の作動によって被動側油圧(ライン圧)が作用するものである。また、被動側シリンダ136には、被動側ピストン140の外側面と共働して被動側遠心油圧キャンセル室146を形成する被動側キャンセル室壁148を設け、この被動側遠心油圧キャンセル室146には被動側軸130に形成した被動軸側オイル油路150及び被動軸側オイル連絡路152を経てオイルが供給され、これにより、被動側油圧室138に発生する遠心油圧を打ち消して、被動側可動プーリ部片134が押圧されるのを防止している。
【0005】
また、無段変速機としては、図12に示すものがある。無段変速機202は、駆動側プーリ(プライマリプーリ)204と、被動側プーリ(セカンダリプーリ)206と、駆動側プーリ204と被動側プーリ206とに巻掛けられた金属製のベルト208とからなる。駆動側プーリ204は、内燃機関のクランク軸210(図示せず)と同軸心上に配設された一の回転軸である駆動側軸(プライマリシャフト)212と、この駆動側軸212に固定した駆動側固定プーリ片(シーブ)214と、駆動側軸212に軸方向移動可能且つ回転不可能に装着した駆動側可動プーリ片(シーブ)216と、この駆動側可動プーリ部片216の外周縁部位に固定されて該駆動側可動プーリ部片216の背面側に向かって突出した駆動側シリンダ218と、駆動側可動プーリ部片216の背面側で外周面が駆動側シリンダ218の内周面に摺動可能に密着して駆動側油圧室220を形成して駆動側軸212に固定された駆動側ピストン222と、この駆動側ピストン222と駆動側可動プーリ部片216の背面との間に設けられた駆動側シーブ押圧スプリング224とからなる。駆動側軸212には、ロングトラベラダンパ226とオイルポンプ228と発進用のクラッチ230及び前後進切換機構232とが設けられている。また、駆動側シリンダ218には、駆動側ピストン222の外側面と共働して駆動側遠心油圧キャンセル室234を形成する駆動側キャンセル室壁236を設け、この駆動側遠心油圧キャンセル室234には専用回路としてのオイルパイプ238からオイルを供給し、これにより、駆動側油圧室220に発生する遠心油圧を打ち消して、駆動側可動プーリ部片216が押圧されるのを防止している。
【0006】
また、被動側プーリ206は、駆動側軸212と平行に配設された他の回転軸である被動側軸(セカンダリシャフト)240と、この被動側軸240に固定した被動側固定プーリ片(シーブ)242と、被動側軸240に軸方向移動可能且つ回転不可能に装着した被動側可動プーリ片(シーブ)244と、この被動側可動プーリ部片244の外周縁部位に固定されて該被動側可動プーリ部片244の背面側に向かって突出した被動側シリンダ246と、被動側可動プーリ部片244の背面側で外周面が被動側シリンダ246の内周面に摺動可能に密着して被動側油圧室248を形成して被動側軸240に固定された被動側ピストン250と、この被動側ピストン250と被動側可動プーリ部片244の背面との間に設けられた被動側シーブ押圧スプリング252とからなる。被動側軸240には、湿式のクラッチ254が設けられているとともに、カウンタ軸256のギヤ列を介してファイナルギヤ機構258と差動機260が連結されている。また、被動側シリンダ246には、被動側シーブ押圧ピストン250の外側面と共働して被動側遠心油圧キャンセル室262を形成する被動側キャンセル室壁264を設け、この被動側遠心油圧キャンセル室262には被動側軸240に形成した被動軸側オイル油路266のセカンダリ回路268から漏れたオイルを供給し、これにより、被動側油圧室248に発生する遠心油圧を打ち消して、被動側可動プーリ部片244が押圧されるのを防止している。被動側キャンセル室壁264部位においては、被動側ピストン250の加工を施した軸側端部には、オイルガイド体270を圧入して設けている。また、このオイルガイド体270の抜け止めをするスペーサ272が、変速機ケース274に取付ボルト276で取付けられている。このスペーサ272は、オイルガイド体270の径よりも大きな径に形成されている。更に、オイルガイド体270と被動側キャンセル室壁264との間には、被動側遠心油圧キャンセル室262を最大限に利用するように、この被動側遠心油圧キャンセル室262を密閉するオイルシール材278が設けられている。
【0007】
即ち、このような無段変速機の構造においては、図13に示す如く、プーリ302は、回転軸304に固定した固定プーリ片306と、回転軸304に軸方向移動可能且つ回転不可能に装着した可動プーリ片308と、この可動プーリ部片308の外周縁部位に固定されて該可動プーリ部片308の背面側に向かって突出したシリンダ310と、可動プーリ部片308の背面側で外周面がシリンダ308の内周面に摺動可能に密着して油圧室312を形成して回転軸304に固定されたピストン314とからなる。このプーリ302の回転中においては、遠心力によって油圧室312には遠心油圧が発生して可動プーリ片308を押圧してしまうものである(白抜きの矢印で示す)。このために、図14に示す如く、シリンダ310には、ピストン314の外周面と共働して遠心油圧キャンセル室316を形成するキャンセル室壁318を設け、この遠心油圧キャンセル室316にオイルを供給してこのオイルの遠心力と油圧室312内の遠心油圧とを打ち消して、可動プーリ部片308が押圧されるのを防止している。この場合に、遠心油圧キャンセル室316の容積がプーリ302の移動(変速比の変化)に伴って変化するので、常に、遠心油圧キャンセル室316にはオイルを供給し続ける必要があるものである。
【0008】
また、このような無段変速機の構造としては、例えば、特開平7−217715号公報、特開平10−184833号公報に開示されている。特開平7−217715号公報に記載のものは、駆動側軸オイル通路と駆動側油圧室とを連通する駆動側プーリオイル通路を駆動側可動プーリ部片に設け、レシオダウンのときに駆動側プーリオイル通路の開孔面積を減少させる面積減少機構を設けたものである。特開平10−184833号公報に記載のものは、可動シーブを軸方向に移動させる油圧アクチュエータの構造において、ピストン部材の突出面と可動シーブの当接面とをカシメ固定後に当接させ、ピストン部材の変形を防止するものである。
【0009】
【発明が解決しようとする課題】
ところで、従来、無段変速機のオイル通路構造にあって、図10のような構造の場合には、駆動側プーリにおいて、駆動側遠心油圧キャンセル室にはバランサプラグからオイルを勢いよく噴射させるので、オイルの供給に確実さが欠け、遠心油圧を良好に打ち消すことが困難になるとともに、被動側プーリにおいては、そのプーリ位置に拘らず、被動側遠心油圧キャンセル室にはオイルを供給するので、被動側軸に形成する被動側軸オイル連絡路が軸方向に所要の長さが必要とされることから、被動側軸の軸方向の長さLが大きく必要となり、大型化を招くという不都合があった。
【0010】
また、図11のような構造の場合には、駆動側プーリにおいて、駆動側遠心油圧キャンセル室にオイルを供給するために、オイルパイプ等の専用回路が必要になり、部品点数が増加して構成が複雑になり、また、被動側プーリにおいては、セカンダリ回路から漏れたオイルを被動側遠心油圧キャンセル室に導いているので、セカンダリ回路の油圧が大きく変化することから、オイルの漏れ量が安定せず、もって、被動側遠心油圧キャンセル室へのオイル量が安定せず、また、ピストンの軸側端部を加工(嵌め合い、穴あけ)してオイルガイド体を圧入し、また、このオイルガイド体の抜け止めに、オイルガイド体よりも外径の大きなスペーサを設けてあり、更に、遠心油圧キャンセル室を最大限に利用するために、オイルガイド体と被動側キャンセル室壁との間にオイルシール材を設けているが、被動側遠心油圧キャンセル室の容積が減少するような変速時に、被動側遠心油圧キャンセル室のオイルが抜けにくくなり、プーリの移動(変速)を妨げてしまうという不都合があった。
【0011】
【課題を解決するための手段】
そこで、この発明は、上述の不都合を除去するために、被動側軸に固定した被動側固定プーリ部片と前記被動側軸に軸方向移動可能且つ回転不可能に軸端部を嵌合させた被動側可動プーリ部片とからなる被動側プーリを設け、前記被動側可動プーリ部片の外周縁部位には該被動側可動プーリ部片の背面側に向かって被動側シリンダを突出して設け、前記被動側軸には前記被動側可動プーリ部片の背面側で外周面が前記被動側シリンダの内周面に摺動可能に密着して被動側油圧室を形成する被動側ピストンを設け、前記被動側シリンダの突出端部に固定されたキャンセル室壁と前記被動側ピストンの外側面との間でオイルが供給される遠心油圧キャンセル室を設け、この遠心油圧キャンセル室を開放状態とした無段変速機のオイル通路構造において、前記被動側ピストンには前記被動側可動プーリ部片の軸端部先端側を収容する軸芯側の突出部分と前記被動側可動プーリ部片の嵌合軸部位の外周面に配設される押圧スプリングを収容する中央側の突出部分とを設け、前記無段変速機の変速比が最小のとき前記キャンセル室壁が前記被動側ピストンの中央側の突出部分に沿うように前記キャンセル室壁を前記被動側ピストンの軸芯側に延出させ、前記無段変速機の変速比が最小のとき前記被動側軸に設けたオイルガイド体が前記被動側ピストンの軸芯側の突出部分に沿うように前記オイルガイド体を外周側に延出させ、前記オイルガイド体の外周側端部と前記遠心油圧キャンセル室の軸芯側壁端部とを前記被動側ピストンの軸芯側の突出部分と中央側の突出部分とを連結する部分で隙間を保持した状態で対向させて配設し、前記無段変速機の変速比が大きくなるのに伴って前記隙間を前記被動側軸の軸方向に拡大させ、前記オイルガイド体と前記被動側ピストンの軸芯側の突出部分との間に開口する被動側軸オイル油路を前記被動側軸に設け、前記無段変速機の変速比が最大のとき前記被動側ピストンの中央側の突出部分と該中央側の突出部分に対応する前記キャンセル室壁の突出部分とで前記遠心油圧キャンセル室外側のキャンセル室空間と中央側のキャンセル室空間とに区画され、前記被動側軸オイル油路から供給されるオイルを前記オイルガイド体によって前記被動側ピストンの軸芯側の突出部分の外側面に沿わせて前記遠心油圧キャンセル室の中央側のキャンセル室空間に流入させ、この遠心油圧キャンセル室の中央側のキャンセル室空間に流入したオイルは前記被動側ピストンの中央側の突出部分に沿わせることで遠心力により流れが前記遠心油圧キャンセル室の外側のキャンセル室空間に指向されて該外側のキャンセル室空間に流入して保持されることを特徴とする。
【0012】
【発明の実施の形態】
この発明は、遠心油圧を良好に打ち消すことができるとともに、被動側軸の軸方向の長さを短くして小型化を図り、また、オイルを遠心油圧キャンセル室に導く専用回路を不要として構成を簡単にするとともにオイルを遠心油圧キャンセル室に安定して供給させ、更に、遠心油圧キャンセル室の容積が減少するような変速時のオイル抜きを容易として被動側プーリの移動(変速)を妨げることがなく、更にまた、被動側ピストンの成形後の加工を簡略させ、オイルガイド体の内周部位とスペーサの小型化を図ってコンパクトとし、また、組付工数を削減し、しかも、廉価とすることができる。
【0013】
【実施例】
以下図面に基づいてこの発明の実施例を詳細且つ具体的に説明する。図1〜7は、この発明の第1実施例を示すものである。図7において、2は車両(図示せず)に搭載される内燃機関、4はこの内燃機関2に連結される無段変速機(CVT)、6は変速機ケースである。
【0014】
変速機ケース6内においては、内燃機関2のクランク軸8と同軸心上に配置された入力軸10と、この入力軸10と同軸心上に配置された駆動側軸(プライマリシャフト)12と、この駆動側軸12と平行に配置された被動側軸(セカンダリシャフト)14と、この被動側軸14と同軸心上に配置された出力軸16と、この出力軸16及び被動側軸14と平行に配置されたカウンタ軸18と、駆動側軸12の内燃機関2側の端部位に配置されたトルクコンバータ20と、このトルクコンバータ20に隣接したオイルポンプ22と、このオイルポンプ22に隣接した前後進切換機構24と、この前後進切換機構24に隣接して駆動側軸12の内燃機関2から離れた端部位に設けられた駆動側プーリ(プライマリプーリ)26と、この駆動側プーリ26に対応して被動側軸14の内燃機関2から離れた端部位に設けられた被動側プーリ(セカンダリプーリ)28と、駆動側プーリ26と被動側プーリ28とに巻掛けられた金属製のベルト30と、被動側軸14と出力軸16との間に設けられたクラッチ32と、出力軸16とカウンタ軸18との間に設けられたリダクションギヤ機構34と、カウンタ軸18に連結されたファイナルギヤ機構36と、このファイナルギヤ機構36に連結された差動機38とが設けられている。
【0015】
駆動側プーリ26にあっては、第1、第2駆動側軸受40−1、40−2に回転自在に支持された駆動側軸12に固定した駆動側固定プーリ片42と、駆動側軸12に軸方向移動可能且つ回転不可能に装着した駆動側可動プーリ片44とが設けられている。この駆動側可動プーリ片44の外周縁部位には、該駆動側可動プーリ片44の背面側に向かって駆動側シリンダ46が突出して設けられている。また、駆動側軸12には、駆動側可動プーリ部片44の背面側で内周面に駆動側シリンダ46の外周面を摺動可能に密着させて駆動側油圧室48を形成する駆動側ピストン50が設けられている。
【0016】
被動側プーリ28にあっては、第1、第2被動側軸受52−1、52−2に回転自在に支持された被動側軸14に固定した被動側固定プーリ片54と、被動側軸14に軸方向移動可能且つ回転不可能に装着した被動側可動プーリ片56とが設けられている。この被動側可動プーリ片56の外周縁部位には、該被動側可動プーリ片56の背面側に向かって被動側シリンダ58が突出して設けられている。また、被動側軸14には、被動側可動プーリ部片56の背面側で外周面が被動側シリンダ58の内周面に摺動可能に密着して被動側油圧室60を形成する被動側ピストン62が設けられている。更に、この被動側ピストン62と被動側可動プーリ片56との間には、シーブ押圧スプリング64が設けられている。
【0017】
この被動側プーリ28にあっては、図1に示す如く、被動側シリンダ58には、被動側ピストン62の外側面と共働して遠心油圧キャンセル室66の外側の一部分を形成するキャンセル室壁68が固定して設けられる。また、被動側軸14には、被動側ピストン62の外側面側でスペーサ70が固定して設けられる。スペーサ70は、図3、4に示す如く、円環形状に形成され、中央の軸用孔72と、被動側ピストン62の外側面に合わされる面で径方向に指向したオイル通路としてのオイル溝74が複数(例えば4つ)形成されている。
【0018】
また、このスペーサ70には、オイルガイド体76が圧入して設けられる。このオイルガイド体76は、スペーサ70のオイル溝74を包囲するように配設されている。よって、遠心油圧キャンセル室66は、開放状態に形成される。
【0019】
更に、被動側軸14には、軸心方向に被動側軸オイル油路78と、この被動側軸オイル油路78に連通し且つ径方向に指向してスペーサ70のオイル溝74に連通する被動側軸オイル連絡路80が形成されている。これにより、被動側軸オイル油路78の潤滑用のオイルは、被動側軸オイル連絡路80からオイル溝74を経て、遠心油圧キャンセル室66に供給されるものである。
【0020】
また、スペーサ70は、側面が第1被動側軸受52−1に当接し、この第1被動側軸受52−1でオイルガイド体76の抜け防止が図られている。
【0021】
更に、この無段変速機4においては、図6に示す如く、上流回路からのオイルは、調圧バルブ82で調圧され、オイルクーラ84に送られ、そして、潤滑回路を経て遠心油圧キャンセル室66に供給されるとともに、トルコンロックアップ制御バルブ86を経てトルクコンバータ20に供給される。また、トルコンロックアップ制御バルブ86には、上流回路からのオイルがロックアップ制御ソレノイド88を経て送られている。
【0022】
次に、この第1実施例の作用を説明する。
【0023】
遠心油圧キャンセル室66の形成時には、被動側シリンダ58にキャンセル室壁68を固定し、また、被動側軸14には被動側ピストン62の中心側の外側面側にスペーサ70を固定して設けるとともに、このスペーサ70にはオイルガイド体76を圧入して設け、よって、遠心油圧キャンセル室66を開放状態に形成し、更に、このオイルガイド体76を第1被動側軸受52−1によって抜け止めさせる。これにより、被動側軸オイル油路78がオイル溝74を介して遠心油圧キャンセル室66に連通され、この遠心油圧キャンセル室66にはオイルが供給される。
【0024】
そして、変速比が最大のときには、図1に示す如く、被動側油圧室60の容積が小さくなるとともに、遠心油圧キャンセル室66の容積が大きくなる。一方、変速比が最小のときには、図2に示す如く、被動側油圧室60の容積が大きくなるとともに、遠心油圧キャンセル室66の容積が小さくなる。。
【0025】
この結果、遠心油圧キャンセル室66をキャンセル室壁68とオイルガイド体76との2部材で形成したことにより、被動側可動プーリ片56の位置に拘らず、遠心油圧キャンセル室66にはオイルを確実に供給させることができる。
【0026】
また、図5に示す如く、遠心油圧キャンセル室66が、重合するキャンセル室壁68とオイルガイド体76とによって開放状態に形成されるので、被動側軸14の軸方向の長さを距離Dだけ短くすることができ、小型化を図ることができる。
【0027】
更に、オイルを遠心油圧キャンセル室66に導くために、オイルパイプ等の専用回路を不要とし、部品点数を低減し、構成を簡単にするとともに、組付工数も削減し、また、オイルを遠心油圧キャンセル室66に安定して供給させることができる。
【0028】
また、遠心油圧キャンセル室66が開放状態になっているので、遠心油圧キャンセル室66の容積が減少するような変速時に、オイル抜きが容易であり、被動側可動プーリ片56の移動を妨げることがない。
【0029】
更に、被動側ピストン62の成形後の加工を簡略することができ、被動側ピストン62の加工を容易とし、また、オイルガイド体76の内周部とスペースの小径化を図ることができる。
【0030】
更にまた、オイルガイド体76が第1被動側軸受52−1によってその抜け防止がなされているので、抜け止め部材を別途の不要とし、構成を簡単にすることができる。
【0031】
図8、9は、この発明の第2実施例を示すものである。
【0032】
以下の実施例においては、上述の第1実施例の同一機能を果たす箇所には同一符号を付して説明する。
【0033】
この第2実施例の特徴とするところは、以下の点にある。即ち、スペーサ70には、オイル通路として径方向に指向するオイル貫通孔92を複数形成した。
【0034】
この第2実施例の構成によれば、オイル貫通孔92により、オイルの流れをより安定させることができる。
【0035】
図10は、この発明の特別構成であり、第3実施例を示すものである。
【0036】
この第3実施例の特徴とするところは、以下の点にある。即ち、被動側ピストン62の外周面には、一端側がオイル通路に連通するとともに、他端側が遠心油圧キャンセル室66の外縁側に位置するオイルパイプ94を放射状に複数個設けた。
【0037】
この第3実施例の構成によれば、オイルをオイルパイプ94によって遠心油圧キャンセル室66に確実に導くとともに、キャンセル室壁68の幅Wを小さくすることができ、さらにコンパクト化を図ることができる。
【0038】
【発明の効果】
以上詳細な説明から明らかなようにこの発明によれば、遠心油圧を良好に打ち消すことができるとともに、被動側軸の軸方向の長さを短くして小型化を図り、また、オイルを遠心油圧キャンセル室に導く専用の油圧回路を不要として構成を簡単にするとともにオイルを遠心油圧キャンセル室に安定して供給させ、更に、遠心油圧キャンセル室の容積が減少するような変速時のオイル抜きを容易として被動側プーリの移動(変速)を妨げることがなく、更にまた、被動側ピストンの成形後の加工を簡略させ、オイルガイド体の内周部位とスペーサの小型化を図ってコンパクトとし、また、組付工数を削減し、しかも、廉価とし得る。
【図面の簡単な説明】
【図1】変速比が最大のときの被動側プーリの断面図である。
【図2】変速比が最小のときの被動側プーリの断面図である。
【図3】スペーサの正面図である。
【図4】図3のスペーサの側面図である。
【図5】オイルガイド体の有無による軸方向の長さを説明する被動側プーリの一部断面図である。
【図6】無段変速機の油圧回路図である。
【図7】無段変速機の断面図である。
【図8】第2実施例におけるスペーサの正面図である。
【図9】図8のスペーサの側面図である。
【図10】第3実施例における被動側プーリの半断面図である。
【図11】従来における無段変速機の断面図である。
【図12】従来における他の無段変速機の断面図である。
【図13】遠心油圧キャンセル室がない場合の説明をする図である。
【図14】遠心油圧キャンセル室がある場合の説明をする図である。
【符号の説明】
2 内燃機関
4 無段変速機
6 変速機ケース
12 駆動側軸
14 被動側軸
20 トルクコンバータ
26 駆動側プーリ
28 被動側プーリ
30 ベルト
58 被動側シリンダ
60 被動側油圧室
62 被動側ピストン
66 遠心油圧キャンセル室
68 キャンセル室壁
70 スペーサ
76 オイルガイド体
[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an oil passage structure of a continuously variable transmission, and more particularly to an oil passage structure of a continuously variable transmission provided with a centrifugal hydraulic pressure canceling chamber so as to cancel centrifugal hydraulic pressure generated in a hydraulic chamber of a pulley.
[0002]
[Prior art]
In a vehicle, since the characteristics of the internal combustion engine are not suitable as they are, a transmission is provided in the transmission path between the internal combustion engine and the drive wheels. This transmission includes a gear transmission that changes a gear ratio stepwise by a gear train and a continuously variable transmission that changes a gear ratio steplessly by a pulley and a belt.
[0003]
As shown in FIG. 11, the continuously variable transmission 102 includes a driving pulley (primary pulley) 104, a driven pulley (secondary pulley) 106, a metal wound around the driving pulley 104 and the driven pulley 106. Some belts are made of a belt 108 made of steel. The drive pulley 104 is a drive side shaft (primary shaft) 110 that is a single rotation shaft disposed coaxially with a crankshaft (not shown) of the internal combustion engine, and a drive fixed to the drive side shaft 110. Side fixed pulley piece (sheave) 112, drive side movable pulley piece (sheave) 114 mounted on the drive side shaft 110 so as to be axially movable and non-rotatable, and an outer peripheral edge portion of the drive side movable pulley piece 114 The drive side cylinder 116 that is fixed and protrudes toward the back side of the drive side movable pulley part piece 114, and the outer peripheral surface slides on the inner peripheral surface of the drive side cylinder 116 on the back side of the drive side movable pulley part piece 114. It comprises a drive side piston 120 fixed to the drive side shaft 110 by forming a drive side hydraulic chamber 118 in close contact with each other. In this case, a drive side hydraulic pressure (primary pressure) is applied to the drive side hydraulic chamber 118 by the operation of the drive side valve (primary valve) 122. Further, the drive side cylinder 116 is provided with a drive side cancel chamber wall 126 that cooperates with the outer surface of the drive side piston 120 to form a drive side centrifugal hydraulic pressure cancel chamber 124, and the drive side centrifugal hydraulic pressure cancel chamber 124 has a balancer. Oil is injected from the plug 128, thereby canceling the centrifugal hydraulic pressure generated in the driving side hydraulic chamber 118 and preventing the driving side movable pulley portion 114 from being pressed.
[0004]
The driven pulley 106 includes a driven side shaft (secondary shaft) 130 that is another rotating shaft disposed in parallel with the driving side shaft 110, and a driven side fixed pulley piece (sheave) fixed to the driven side shaft 130. ) 132, a driven movable pulley piece (sheave) 134 that is mounted on the driven side shaft 130 so as to be axially movable and non-rotatable, and is fixed to the outer peripheral edge portion of the driven side movable pulley part piece 134. The driven cylinder 136 protrudes toward the back side of the movable pulley piece 134, and the outer peripheral surface of the driven side movable pulley piece 134 is slidably in close contact with the inner peripheral surface of the driven cylinder 136. Driven side piston 140 that is fixed to the driven side shaft 130 by forming a side hydraulic chamber 138, and a sheave pressing sp provided between the driven side piston 140 and the back surface of the driven side movable pulley part piece 134. Consisting of ring 142. In this case, driven hydraulic pressure (line pressure) acts on the driven hydraulic chamber 138 by the operation of the driven valve (secondary valve) 144. The driven cylinder 136 is provided with a driven cancel chamber wall 148 that cooperates with the outer surface of the driven piston 140 to form a driven centrifugal oil pressure cancel chamber 146. Oil is supplied through a driven shaft side oil oil passage 150 and a driven shaft side oil communication passage 152 formed in the driven side shaft 130, thereby canceling the centrifugal hydraulic pressure generated in the driven side hydraulic chamber 138, and the driven side movable pulley. The part 134 is prevented from being pressed.
[0005]
As a continuously variable transmission, there is one shown in FIG. The continuously variable transmission 202 includes a driving pulley (primary pulley) 204, a driven pulley (secondary pulley) 206, and a metal belt 208 wound around the driving pulley 204 and the driven pulley 206. . The drive side pulley 204 is fixed to the drive side shaft 212 and a drive side shaft (primary shaft) 212 which is one rotational shaft disposed coaxially with the crankshaft 210 (not shown) of the internal combustion engine. Driving side fixed pulley piece (sheave) 214, driving side movable pulley piece (sheave) 216 mounted on the driving side shaft 212 so as to be axially movable and non-rotatable, and an outer peripheral edge portion of the driving side movable pulley part piece 216 A drive-side cylinder 218 that is fixed to the drive-side movable pulley part piece 216 and protrudes toward the back side of the drive-side movable pulley part piece 216; A drive-side piston 222 fixed to the drive-side shaft 212 by forming a drive-side hydraulic chamber 220 in close contact with the drive side, and a back surface of the drive-side piston 222 and the drive-side movable pulley piece 216 is provided. It was a driving sheave compression spring 224.. The driving side shaft 212 is provided with a long traveler damper 226, an oil pump 228, a starting clutch 230, and a forward / reverse switching mechanism 232. The drive side cylinder 218 is provided with a drive side cancel chamber wall 236 that cooperates with the outer surface of the drive side piston 222 to form a drive side centrifugal oil pressure cancel chamber 234. Oil is supplied from an oil pipe 238 as a dedicated circuit, thereby canceling the centrifugal hydraulic pressure generated in the drive-side hydraulic chamber 220 and preventing the drive-side movable pulley portion 216 from being pressed.
[0006]
The driven pulley 206 includes a driven side shaft (secondary shaft) 240 that is another rotating shaft arranged in parallel with the driving side shaft 212 and a driven side fixed pulley piece (sheave) fixed to the driven side shaft 240. 242; a driven movable pulley piece (sheave) 244 mounted on the driven side shaft 240 so as to be axially movable and non-rotatable; and fixed to an outer peripheral edge portion of the driven side movable pulley part piece 244; The driven cylinder 246 that protrudes toward the back side of the movable pulley part piece 244 and the outer peripheral surface of the driven side movable pulley part piece 244 that is slidably in close contact with the inner peripheral surface of the driven cylinder 246 are driven. Driven-side sheave pusher provided between the driven-side piston 250 and the back of the driven-side movable pulley part 244 formed with a side hydraulic chamber 248 and fixed to the driven-side shaft 240. Consisting of a spring 252. The driven shaft 240 is provided with a wet clutch 254, and a final gear mechanism 258 and a differential 260 are connected to each other via a gear train of the counter shaft 256. The driven cylinder 246 is provided with a driven cancel chamber wall 264 that cooperates with the outer surface of the driven sheave pressing piston 250 to form a driven centrifugal oil pressure cancel chamber 262, and this driven centrifugal oil pressure cancel chamber 262 is provided. Is supplied with oil leaking from the secondary circuit 268 of the driven shaft side oil oil passage 266 formed in the driven side shaft 240, thereby canceling the centrifugal hydraulic pressure generated in the driven side hydraulic chamber 248, and the driven side movable pulley portion. The piece 244 is prevented from being pressed. In the driven-side cancel chamber wall 264, an oil guide body 270 is press-fitted and provided at the shaft-side end where the driven-side piston 250 has been processed. In addition, a spacer 272 that prevents the oil guide body 270 from coming off is attached to the transmission case 274 with mounting bolts 276. The spacer 272 is formed with a diameter larger than the diameter of the oil guide body 270. Further, between the oil guide body 270 and the driven-side cancellation chamber wall 264, an oil seal member 278 that seals the driven-side centrifugal hydraulic pressure cancellation chamber 262 so as to make maximum use of the driven-side centrifugal hydraulic pressure cancellation chamber 262. Is provided.
[0007]
That is, in such a continuously variable transmission structure, as shown in FIG. 13, the pulley 302 is fixedly attached to the rotary shaft 304 and the pulley 302 is mounted on the rotary shaft 304 so as to be axially movable and non-rotatable. A movable pulley piece 308, a cylinder 310 fixed to the outer peripheral edge of the movable pulley piece 308 and projecting toward the back side of the movable pulley piece 308, and an outer peripheral surface on the back side of the movable pulley piece 308. Comprises a piston 314 fixed to the rotating shaft 304 by forming a hydraulic chamber 312 in close contact with the inner peripheral surface of the cylinder 308. During the rotation of the pulley 302, centrifugal hydraulic pressure is generated in the hydraulic chamber 312 due to centrifugal force and presses the movable pulley piece 308 (indicated by a white arrow). For this purpose, as shown in FIG. 14, the cylinder 310 is provided with a cancel chamber wall 318 that forms a centrifugal oil pressure cancel chamber 316 in cooperation with the outer peripheral surface of the piston 314, and supplies oil to the centrifugal oil pressure cancel chamber 316. Thus, the centrifugal force of the oil and the centrifugal hydraulic pressure in the hydraulic chamber 312 are canceled out to prevent the movable pulley portion 308 from being pressed. In this case, since the volume of the centrifugal hydraulic pressure cancellation chamber 316 changes with the movement of the pulley 302 (change in the transmission gear ratio), it is necessary to always supply oil to the centrifugal hydraulic pressure cancellation chamber 316.
[0008]
Moreover, as a structure of such a continuously variable transmission, it is disclosed by Unexamined-Japanese-Patent No. 7-217715, Unexamined-Japanese-Patent No. 10-184833, for example. Japanese Patent Application Laid-Open No. 7-217715 discloses that a drive side pulley oil passage that communicates a drive side shaft oil passage and a drive side hydraulic chamber is provided in the drive side movable pulley part piece, and the drive side pulley is used when the ratio is lowered. An area reduction mechanism for reducing the opening area of the oil passage is provided. Japanese Patent Application Laid-Open No. 10-184833 discloses a structure of a hydraulic actuator for moving a movable sheave in an axial direction, wherein the projecting surface of the piston member and the contact surface of the movable sheave are brought into contact after being fixed by caulking, Is to prevent the deformation.
[0009]
[Problems to be solved by the invention]
By the way, in the case of an oil passage structure of a continuously variable transmission and having a structure as shown in FIG. 10, oil is vigorously injected from the balancer plug into the drive side centrifugal hydraulic pressure cancel chamber in the drive side pulley. The oil supply lacks certainty, making it difficult to cancel the centrifugal oil pressure well.In the driven pulley, the oil is supplied to the driven centrifugal oil pressure canceling chamber regardless of the position of the pulley. Since the required length in the axial direction of the driven-side shaft oil communication path formed on the driven-side shaft is required, the length L in the axial direction of the driven-side shaft is required to be large, leading to an increase in size. there were.
[0010]
In the case of the structure as shown in FIG. 11, a dedicated circuit such as an oil pipe is required in the driving pulley to supply oil to the driving centrifugal oil pressure canceling chamber, which increases the number of parts. In the driven pulley, the oil leaked from the secondary circuit is led to the driven centrifugal oil pressure canceling chamber, so the oil pressure in the secondary circuit changes greatly. Therefore, the amount of oil to the driven centrifugal hydraulic pressure cancellation chamber is not stable, and the oil guide body is press-fitted by machining (fitting and drilling) the shaft side end of the piston. A spacer with an outer diameter larger than that of the oil guide body is provided to prevent the oil guide body from being removed. An oil sealant is provided between the wall of the cancel chamber and the oil in the driven centrifugal hydraulic pressure canceling chamber becomes difficult to escape during gear shifting in which the volume of the driven centrifugal hydraulic pressure canceling chamber decreases. ).
[0011]
[Means for Solving the Problems]
Therefore, in order to eliminate the above-mentioned inconveniences, the present invention has a driven-side fixed pulley portion piece fixed to a driven-side shaft and a shaft end portion fitted to the driven-side shaft so as to be axially movable and non-rotatable. A driven-side pulley comprising a driven-side movable pulley part piece is provided, and a driven-side cylinder is provided at the outer peripheral edge of the driven-side movable pulley part piece so as to protrude toward the back side of the driven-side movable pulley part piece; The driven-side shaft is provided with a driven-side piston that forms a driven-side hydraulic chamber in which the outer peripheral surface is slidably in close contact with the inner peripheral surface of the driven-side cylinder on the back side of the driven-side movable pulley piece. A continuously variable transmission in which a centrifugal oil pressure cancel chamber is provided between the cancel chamber wall fixed to the protruding end of the side cylinder and the outer surface of the driven piston, and the centrifugal oil pressure cancel chamber is opened. The oil passage structure of the machine The driven-side piston is disposed on the outer peripheral surface of the shaft-side protruding portion that houses the distal end side of the shaft end of the driven-side movable pulley piece and the fitting shaft portion of the driven-side movable pulley piece. A center-side protruding portion that accommodates the pressing spring, and the cancel chamber wall extends along the center-side protruding portion of the driven-side piston when the gear ratio of the continuously variable transmission is minimum. Is extended to the shaft core side of the driven piston, and when the gear ratio of the continuously variable transmission is minimum, the oil guide body provided on the driven shaft follows the protruding portion on the shaft core side of the driven piston. The oil guide body is extended to the outer peripheral side, and the outer peripheral side end portion of the oil guide body and the axial side wall end portion of the centrifugal hydraulic pressure canceling chamber are connected to the protruding portion and the center of the driven side piston. Gap at the part connecting the protruding part on the side Is opposed by the holding state is disposed, the said gap along with the gear ratio of the continuously variable transmission is greatly enlarged in the axial direction of the driven-side shaft, the oil guide member and the driven-side piston A driven-side shaft oil passage that opens between the protruding portion on the shaft core side is provided in the driven-side shaft, and when the transmission ratio of the continuously variable transmission is maximum, the protruding portion on the center side of the driven-side piston and the wherein in the projecting portion of the cancel chamber wall corresponding to the projecting portion of the center-side centrifugal-pressure canceling chamber is partitioned into an outer cancellation chamber space and the central-side cancel chamber space is supplied from the driven-side shaft oil oil passage The oil guide body causes the oil guide body to flow along the outer surface of the protruding portion on the shaft core side of the driven piston into the cancellation chamber space on the center side of the centrifugal hydraulic pressure cancellation chamber. Oil that has flowed into the cancellation chamber space side is directed to the cancellation chamber space outside of said flow by a centrifugal force by making along the central-side protruding portion of the driven-side piston the centrifugal-pressure canceling chamber said outer cancel chamber It is characterized by flowing into the space and being held.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
According to the present invention, the centrifugal hydraulic pressure can be canceled satisfactorily, the axial length of the driven side shaft is shortened to reduce the size, and a dedicated circuit for guiding the oil to the centrifugal hydraulic pressure canceling chamber is unnecessary. easy to stably supply the oil to the centrifugal hydraulic pressure cancel chamber while, further, may hinder the movement of the driven side pulley (the shift) the oil drain in the gear shifting, such as the volume of the centrifugal-pressure canceling chamber decreases as easily In addition, the processing after molding of the driven piston is simplified, the inner peripheral part of the oil guide body and the spacer are reduced in size, and the assembly man-hour is reduced and the cost is reduced. Can do.
[0013]
【Example】
Embodiments of the present invention will be described in detail and specifically with reference to the drawings. 1 to 7 show a first embodiment of the present invention. In FIG. 7, 2 is an internal combustion engine mounted on a vehicle (not shown), 4 is a continuously variable transmission (CVT) connected to the internal combustion engine 2, and 6 is a transmission case.
[0014]
In the transmission case 6, an input shaft 10 disposed coaxially with the crankshaft 8 of the internal combustion engine 2, a drive side shaft (primary shaft) 12 disposed coaxially with the input shaft 10, A driven side shaft (secondary shaft) 14 disposed parallel to the drive side shaft 12, an output shaft 16 disposed coaxially with the driven side shaft 14, and parallel to the output shaft 16 and the driven side shaft 14. Counter shaft 18 arranged at the end, torque converter 20 arranged at the end portion of drive side shaft 12 on the internal combustion engine 2 side, oil pump 22 adjacent to torque converter 20, and front and rear sides adjacent to oil pump 22. A forward switching mechanism 24, a driving pulley (primary pulley) 26 provided at an end portion of the driving side shaft 12 adjacent to the forward / backward switching mechanism 24 and away from the internal combustion engine 2, and the driving side pulley. 26, a driven pulley (secondary pulley) 28 provided at an end portion of the driven shaft 14 away from the internal combustion engine 2, a drive pulley 26, and a driven pulley 28. The belt 30, the clutch 32 provided between the driven side shaft 14 and the output shaft 16, the reduction gear mechanism 34 provided between the output shaft 16 and the counter shaft 18, and the counter shaft 18 are connected. A final gear mechanism 36 and a differential 38 connected to the final gear mechanism 36 are provided.
[0015]
In the driving pulley 26, the driving side fixed pulley piece 42 fixed to the driving side shaft 12 rotatably supported by the first and second driving side bearings 40-1 and 40-2, and the driving side shaft 12. And a drive-side movable pulley piece 44 that is mounted so as to be axially movable and non-rotatable. A drive side cylinder 46 projects from the outer peripheral edge portion of the drive side movable pulley piece 44 toward the back side of the drive side movable pulley piece 44. Further, the driving side piston 12 forms a driving side hydraulic chamber 48 by slidably contacting the outer peripheral surface of the driving side cylinder 46 to the inner peripheral surface on the back side of the driving side movable pulley part piece 44 on the driving side shaft 12. 50 is provided.
[0016]
In the driven pulley 28, a driven fixed pulley piece 54 fixed to the driven shaft 14 rotatably supported by the first and second driven bearings 52-1, 52-2, and the driven shaft 14 are provided. And a driven-side movable pulley piece 56 mounted so as to be axially movable and non-rotatable. A driven cylinder 58 is provided at the outer peripheral edge of the driven movable pulley piece 56 so as to protrude toward the back side of the driven movable pulley piece 56. Further, a driven-side piston that forms a driven-side hydraulic chamber 60 in which the outer peripheral surface is slidably in close contact with the inner peripheral surface of the driven-side cylinder 58 on the back side of the driven-side movable pulley part piece 56. 62 is provided. Further, a sheave pressing spring 64 is provided between the driven side piston 62 and the driven side movable pulley piece 56.
[0017]
In the driven pulley 28, as shown in FIG. 1, the driven cylinder 58 forms a part of the outside of the centrifugal hydraulic pressure canceling chamber 66 in cooperation with the outer surface of the driven piston 62. 68 is fixedly provided. The driven shaft 14 is provided with a spacer 70 fixed on the outer surface side of the driven piston 62. As shown in FIGS. 3 and 4, the spacer 70 is formed in an annular shape, and has an oil groove as an oil passage oriented in the radial direction on a surface that is fitted with the central shaft hole 72 and the outer surface of the driven piston 62. A plurality of (for example, four) 74 are formed.
[0018]
An oil guide body 76 is press-fitted into the spacer 70. The oil guide body 76 is disposed so as to surround the oil groove 74 of the spacer 70. Therefore, the centrifugal hydraulic pressure cancellation chamber 66 is formed in an open state.
[0019]
Further, the driven shaft 14 is connected to the driven shaft oil oil passage 78 in the axial direction, and the driven shaft oil oil passage 78 is connected to the oil groove 74 of the spacer 70 in the radial direction. A side shaft oil communication path 80 is formed. As a result, the lubricating oil in the driven-side shaft oil passage 78 is supplied from the driven-side shaft oil communication passage 80 through the oil groove 74 to the centrifugal hydraulic pressure cancellation chamber 66.
[0020]
Further, the side surface of the spacer 70 is in contact with the first driven bearing 52-1, and the oil guide body 76 is prevented from coming off by the first driven bearing 52-1.
[0021]
Further, in the continuously variable transmission 4, as shown in FIG. 6, the oil from the upstream circuit is regulated by the pressure regulating valve 82, sent to the oil cooler 84, and then passed through the lubricating circuit to the centrifugal hydraulic pressure cancellation chamber. 66 and supplied to the torque converter 20 via the torque converter lockup control valve 86. Further, oil from the upstream circuit is sent to the torque converter lockup control valve 86 via a lockup control solenoid 88.
[0022]
Next, the operation of the first embodiment will be described.
[0023]
When the centrifugal hydraulic pressure canceling chamber 66 is formed, the cancel chamber wall 68 is fixed to the driven side cylinder 58, and the spacer 70 is fixed to the driven side shaft 14 on the outer side of the center side of the driven side piston 62. The spacer 70 is press-fitted with an oil guide body 76, so that the centrifugal oil pressure cancellation chamber 66 is formed in an open state, and the oil guide body 76 is prevented from being detached by the first driven bearing 52-1. . As a result, the driven-side shaft oil passage 78 communicates with the centrifugal hydraulic pressure cancel chamber 66 via the oil groove 74, and oil is supplied to the centrifugal hydraulic pressure cancel chamber 66.
[0024]
When the speed ratio is the maximum, as shown in FIG. 1, the volume of the driven hydraulic chamber 60 decreases and the volume of the centrifugal hydraulic cancel chamber 66 increases. On the other hand, when the speed ratio is minimum, as shown in FIG. 2, the volume of the driven hydraulic chamber 60 increases and the volume of the centrifugal hydraulic cancel chamber 66 decreases. .
[0025]
As a result, the centrifugal hydraulic pressure canceling chamber 66 is formed by two members, the canceling chamber wall 68 and the oil guide body 76, so that the centrifugal hydraulic pressure canceling chamber 66 is reliably supplied with oil regardless of the position of the driven-side movable pulley piece 56. Can be supplied.
[0026]
Further, as shown in FIG. 5, the centrifugal hydraulic pressure canceling chamber 66 is formed in an open state by the canceling chamber wall 68 and the oil guide body 76 to be overlapped, so that the axial length of the driven shaft 14 is set to the distance D. It can be shortened and downsizing can be achieved.
[0027]
Furthermore, in order to guide the oil to the centrifugal hydraulic pressure canceling chamber 66, a dedicated circuit such as an oil pipe is not necessary, the number of parts is reduced, the configuration is simplified, the number of assembling steps is reduced, and the oil is centrifugal hydraulic pressure. The cancellation chamber 66 can be stably supplied.
[0028]
In addition, since the centrifugal hydraulic pressure canceling chamber 66 is in an open state, it is easy to drain oil at the time of shifting such that the volume of the centrifugal hydraulic pressure canceling chamber 66 is reduced, and the movement of the driven-side movable pulley piece 56 is hindered. Absent.
[0029]
Furthermore, the processing after molding of the driven side piston 62 can be simplified, the processing of the driven side piston 62 can be facilitated, and the inner peripheral portion of the oil guide body 76 and the space can be reduced in diameter.
[0030]
Furthermore, since the oil guide body 76 is prevented from coming off by the first driven bearing 52-1, a separate retaining member is not required and the configuration can be simplified.
[0031]
8 and 9 show a second embodiment of the present invention.
[0032]
In the following embodiments, portions having the same functions as those of the first embodiment will be described with the same reference numerals.
[0033]
The features of the second embodiment are as follows. That is, the spacer 70 is formed with a plurality of oil through-holes 92 that are oriented in the radial direction as oil passages.
[0034]
According to the configuration of the second embodiment, the oil flow can be further stabilized by the oil through hole 92.
[0035]
FIG. 10 shows a special configuration of the present invention and shows a third embodiment.
[0036]
The features of the third embodiment are as follows. That is, on the outer peripheral surface of the driven-side piston 62, a plurality of oil pipes 94 whose one end side communicates with the oil passage and whose other end side is located on the outer edge side of the centrifugal hydraulic pressure canceling chamber 66 are provided radially.
[0037]
According to the configuration of the third embodiment, oil can be reliably guided to the centrifugal hydraulic pressure cancellation chamber 66 by the oil pipe 94, the width W of the cancellation chamber wall 68 can be reduced, and further downsizing can be achieved. .
[0038]
【The invention's effect】
As is clear from the above detailed description, according to the present invention, the centrifugal hydraulic pressure can be canceled satisfactorily, the axial length of the driven side shaft is shortened to reduce the size, and the oil is supplied to the centrifugal hydraulic pressure. Eliminates the need for a dedicated hydraulic circuit that leads to the cancellation chamber, simplifies the configuration, supplies oil stably to the centrifugal hydraulic cancellation chamber, and facilitates oil removal during shifting that reduces the volume of the centrifugal hydraulic cancellation chamber as the movement of the driven side pulley (gear) without interfering with the further addition, to simplify the processing after the molding of the driven-side piston, a compact reduced size of the inner peripheral portion and the spacer of the oil guide member, also, The number of assembly steps can be reduced and the cost can be reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a driven pulley when a gear ratio is maximum.
FIG. 2 is a sectional view of a driven pulley when the speed ratio is minimum.
FIG. 3 is a front view of a spacer.
4 is a side view of the spacer of FIG. 3. FIG.
FIG. 5 is a partial cross-sectional view of a driven pulley for explaining an axial length depending on the presence or absence of an oil guide body.
FIG. 6 is a hydraulic circuit diagram of a continuously variable transmission.
FIG. 7 is a cross-sectional view of a continuously variable transmission.
FIG. 8 is a front view of a spacer according to a second embodiment.
9 is a side view of the spacer of FIG. 8. FIG.
FIG. 10 is a half sectional view of a driven pulley in a third embodiment.
FIG. 11 is a cross-sectional view of a conventional continuously variable transmission.
FIG. 12 is a cross-sectional view of another conventional continuously variable transmission.
FIG. 13 is a diagram illustrating a case where there is no centrifugal hydraulic pressure cancellation chamber.
FIG. 14 is a diagram illustrating a case where there is a centrifugal oil pressure canceling chamber.
[Explanation of symbols]
2 internal combustion engine 4 continuously variable transmission 6 transmission case 12 drive side shaft 14 driven side shaft 20 torque converter 26 drive side pulley 28 driven side pulley 30 belt 58 driven side cylinder 60 driven side hydraulic chamber 62 driven side piston 66 centrifugal hydraulic pressure cancellation Chamber 68 Cancel chamber wall 70 Spacer 76 Oil guide body

Claims (2)

被動側軸に固定した被動側固定プーリ部片と前記被動側軸に軸方向移動可能且つ回転不可能に軸端部を嵌合させた被動側可動プーリ部片とからなる被動側プーリを設け、前記被動側可動プーリ部片の外周縁部位には該被動側可動プーリ部片の背面側に向かって被動側シリンダを突出して設け、前記被動側軸には前記被動側可動プーリ部片の背面側で外周面が前記被動側シリンダの内周面に摺動可能に密着して被動側油圧室を形成する被動側ピストンを設け、前記被動側シリンダの突出端部に固定されたキャンセル室壁と前記被動側ピストンの外側面との間でオイルが供給される遠心油圧キャンセル室を設け、この遠心油圧キャンセル室を開放状態とした無段変速機のオイル通路構造において、前記被動側ピストンには前記被動側可動プーリ部片の軸端部先端側を収容する軸芯側の突出部分と前記被動側可動プーリ部片の嵌合軸部位の外周面に配設される押圧スプリングを収容する中央側の突出部分とを設け、前記無段変速機の変速比が最小のとき前記キャンセル室壁が前記被動側ピストンの中央側の突出部分に沿うように前記キャンセル室壁を前記被動側ピストンの軸芯側に延出させ、前記無段変速機の変速比が最小のとき前記被動側軸に設けたオイルガイド体が前記被動側ピストンの軸芯側の突出部分に沿うように前記オイルガイド体を外周側に延出させ、前記オイルガイド体の外周側端部と前記遠心油圧キャンセル室の軸芯側壁端部とを前記被動側ピストンの軸芯側の突出部分と中央側の突出部分とを連結する部分で隙間を保持した状態で対向させて配設し、前記無段変速機の変速比が大きくなるのに伴って前記隙間を前記被動側軸の軸方向に拡大させ、前記オイルガイド体と前記被動側ピストンの軸芯側の突出部分との間に開口する被動側軸オイル油路を前記被動側軸に設け、前記無段変速機の変速比が最大のとき前記被動側ピストンの中央側の突出部分と該中央側の突出部分に対応する前記キャンセル室壁の突出部分とで前記遠心油圧キャンセル室外側のキャンセル室空間と中央側のキャンセル室空間とに区画され、前記被動側軸オイル油路から供給されるオイルを前記オイルガイド体によって前記被動側ピストンの軸芯側の突出部分の外側面に沿わせて前記遠心油圧キャンセル室の中央側のキャンセル室空間に流入させ、この遠心油圧キャンセル室の中央側のキャンセル室空間に流入したオイルは前記被動側ピストンの中央側の突出部分に沿わせることで遠心力により流れが前記遠心油圧キャンセル室の外側のキャンセル室空間に指向されて該外側のキャンセル室空間に流入して保持されることを特徴とする無段変速機のオイル通路構造。A driven-side pulley comprising a driven-side fixed pulley portion fixed to the driven-side shaft and a driven-side movable pulley portion that is axially movable and non-rotatably fitted to the driven-side shaft; A driven cylinder is provided at the outer peripheral edge of the driven side movable pulley part piece so as to protrude toward the back side of the driven side movable pulley part piece, and the back side of the driven side movable pulley part piece is provided on the driven side shaft. And a canceling chamber wall fixed to the projecting end of the driven cylinder, and a canceling chamber wall provided with a driven piston that forms a driven hydraulic chamber by slidably contacting the inner peripheral surface of the driven cylinder. In the oil passage structure of a continuously variable transmission in which a centrifugal hydraulic pressure cancellation chamber to which oil is supplied is provided between the outer surface of the driven piston and the centrifugal hydraulic pressure cancellation chamber is opened, the driven piston is provided with the driven Side movable pulley A protruding portion on the shaft core side that accommodates the distal end side of the shaft end portion and a protruding portion on the central side that accommodates a pressing spring disposed on the outer peripheral surface of the fitting shaft portion of the driven-side movable pulley piece, Extending the cancel chamber wall toward the axis of the driven piston so that the cancel chamber wall follows a central protruding portion of the driven piston when the transmission ratio of the continuously variable transmission is minimum; When the gear ratio of the continuously variable transmission is minimum, the oil guide body provided on the driven side shaft extends along the protruding portion on the shaft core side of the driven side piston, and the oil guide body extends to the outer peripheral side, A state in which a gap is held between the outer peripheral side end of the oil guide body and the axial side wall end of the centrifugal hydraulic pressure canceling chamber at the portion connecting the protruding portion on the axial center side and the protruding portion on the central side of the driven piston. in is opposed by arranging, in the continuously variable transmission With the the speed ratio increases to expand the gap in the axial direction of the driven-side shaft, the driven-side shaft oil oil which opens between the oil guide member and the protruding portion of the axial core side of the driven-side piston A path is provided on the driven side shaft, and when the gear ratio of the continuously variable transmission is the maximum, a protruding portion on the center side of the driven side piston and a protruding portion of the cancel chamber wall corresponding to the protruding portion on the center side the centrifugal-pressure canceling chamber is partitioned into an outer cancellation chamber space and the central-side cancel chamber space, the axis side of the driven-side piston by the oil guide body oil supplied from the driven-side shaft oil oil passage The oil flowing into the central canceling chamber space of the centrifugal hydraulic pressure canceling chamber is caused to flow along the outer surface of the protruding portion, and the oil flowing into the central canceling chamber space of the centrifugal hydraulic pressure canceling chamber is transferred to the driven side pipe. It is directed to flow by centrifugal force by making along the central-side protruding portion of the piston to cancel chamber space outside of the centrifugal-pressure canceling chamber, characterized in that it is held to flow into the cancellation chamber space of the outer Oil passage structure for continuously variable transmission. 前記被動側軸にスペーサを嵌合させ、前記被動側ピストンの外側面と前記被動軸を保持する被動側軸受とによって前記スペーサを挟持し、前記スペーサには前記被動側軸オイル油路に連絡するオイル溝を設けたことを特徴とする請求項1に記載の無段変速機のオイル通路構造。A spacer is fitted to the driven side shaft, and the spacer is sandwiched between an outer surface of the driven side piston and a driven side bearing holding the driven side shaft, and the spacer communicates with the driven side shaft oil passage. 2. An oil passage structure for a continuously variable transmission according to claim 1, wherein an oil groove is provided.
JP05055199A 1999-02-26 1999-02-26 Oil passage structure of continuously variable transmission Expired - Fee Related JP3890798B2 (en)

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KR100376696B1 (en) * 2000-09-04 2003-03-17 현대자동차주식회사 Belt-pulley system for continuously variable transmission
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