JP4016514B2

JP4016514B2 - Toroidal continuously variable transmission

Info

Publication number: JP4016514B2
Application number: JP37234298A
Authority: JP
Inventors: 雅人吉田
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 1998-12-28
Filing date: 1998-12-28
Publication date: 2007-12-05
Anticipated expiration: 2018-12-28
Also published as: JP2000193057A

Description

【０００１】
【発明の属する技術分野】
この発明に係るトロイダル型無段変速機は、例えば自動車用の変速機として、或は各種産業機械用の変速機として利用する。
【０００２】
【従来の技術】
自動車用変速機として、図８〜９に略示する様なトロイダル型無段変速機を使用する事が研究されている。このトロイダル型無段変速機は、例えば実開昭６２−７１４６５号公報に開示されている様に、入力軸１と同心に入力側ディスク２を支持し、この入力軸１と同心に配置した出力軸３の端部に出力側ディスク４を固定している。トロイダル型無段変速機を納めたケーシングの内側には、上記入力軸１並びに出力軸３に対し捻れの位置にある枢軸５、５を中心として揺動するトラニオン６、６を設けている。
【０００３】
即ち、上記両ディスク２、４の中心軸から外れた部分に配置したこれら各トラニオン６、６は、それぞれの両端部外面に上記枢軸５、５を、上記両ディスク２、４の中心軸の方向に対し直角方向に、且つ、互いに同心に設けている。又、これら各トラニオン６、６の中間部には変位軸７、７の基端部を支持し、上記枢軸５、５を中心として上記各トラニオン６、６を揺動させる事により、上記各変位軸７、７の傾斜角度の調節を自在としている。上記各トラニオン６、６に支持した変位軸７、７の周囲には、それぞれパワーローラ８、８を回転自在に支持している。そして、これら各パワーローラ８、８を、上記入力側、出力側両ディスク２、４の、互いに対向する内側面２ａ、４ａ同士の間に挟持している。これら各内側面２ａ、４ａは、それぞれ断面が、上記枢軸５を中心とする円弧を回転させて得られる凹面をなしている。そして、球状凸面に形成した上記各パワーローラ８、８の周面８ａ、８ａを、上記内側面２ａ、４ａに当接させている。
【０００４】
上記入力軸１と入力側ディスク２との間には、ローディングカム装置９を設け、このローディングカム装置９によって、上記入力側ディスク２を出力側ディスク４に向け弾性的に押圧しつつ、この入力側ディスク２を回転駆動自在としている。このローディングカム装置９は、入力軸１と共に回転するローディングカム１０と、保持器１１により転動自在に保持した複数個（例えば４個）のローラ１２、１２とから構成している。上記ローディングカム１０の片側面（図８〜９の右側面）には、円周方向に亙る凹凸であるカム面１３を形成し、上記入力側ディスク２の外側面（図８〜９の左側面）にも、同様の形状を有するカム面１４を形成している。そして、上記複数個のローラ１２、１２を、上記入力軸１の中心に関し放射方向の軸を中心とする回転自在に支持している。
【０００５】
上述の様に構成するトロイダル型無段変速機の使用時、入力軸１の回転に伴ってローディングカム１０が回転すると、カム面１３が複数個のローラ１２、１２を、入力側ディスク２の外側面に形成したカム面１４に押圧する。この結果、上記入力側ディスク２が、上記複数のパワーローラ８、８に押圧されると同時に、上記両カム面１３、１４と複数個のローラ１２、１２との押し付け合いに基づいて、上記入力側ディスク２が回転する。そして、この入力側ディスク２の回転が、上記複数のパワーローラ８、８を介して出力側ディスク４に伝達され、この出力側ディスク４に固定の出力軸３が回転する。
【０００６】
入力軸１と出力軸３との回転速度比（変速比）を変える場合で、先ず入力軸１と出力軸３との間で減速を行なう場合には、前記各枢軸５、５を中心として前記各トラニオン６、６を所定方向に揺動させる。そして、上記各パワーローラ８、８の周面８ａ、８ａが図８に示す様に、入力側ディスク２の内側面２ａの中心寄り部分と出力側ディスク４の内側面４ａの外周寄り部分とにそれぞれ当接する様に、前記各変位軸７、７を傾斜させる。反対に、増速を行なう場合には、上記枢軸５、５を中心として上記各トラニオン６、６を反対方向に揺動させる。そして、上記各パワーローラ８、８の周面８ａ、８ａが図９に示す様に、入力側ディスク２の内側面２ａの外周寄り部分と出力側ディスク４の内側面４ａの中心寄り部分とに、それぞれ当接する様に、上記各変位軸７、７を傾斜させる。各変位軸７、７の傾斜角度を図８と図９との中間にすれば、入力軸１と出力軸３との間で、中間の変速比を得られる。
【０００７】
又、図１０〜１１は、実願昭６３−６９２９３号（実開平１−１７３５５２号）のマイクロフィルムに記載された、より具体化されたトロイダル型無段変速機の１例を示している。入力側ディスク２と出力側ディスク４とは円管状の入力軸１５の周囲に、それぞれニードル軸受１６、１６を介して、回転自在に支持している。即ち、上記入力側ディスク２及び出力側ディスク４の中心部には断面形状が円形である貫通孔１７、１７を、それぞれ上記各ディスク２、４の内側面と外側面とを軸方向（図１０の左右方向）に貫通する状態で形成している。上記各ニードル軸受１６、１６は、上記各貫通孔１７、１７の内周面と上記入力軸１５の中間部外周面との間に設けている。又、上記各貫通孔１７、１７の内側面寄り端部内周面に形成した係止溝１８、１８には止め輪１９、１９を係止して、上記各ニードル軸受１６、１６が上記各貫通孔１７、１７から、上記各ディスク２、４の内側面２ａ、４ａ側に抜け出る事を防止している。又、ローディングカム１０は上記入力軸１５の端部（図１０の左端部）外周面にスプライン係合させ、外向フランジ状の鍔部２０により上記入力側ディスク２から離れる方向への移動を阻止している。そして、このローディングカム１０とローラ１２、１２とにより、上記入力軸１５の回転に基づいて上記入力側ディスク２を、上記出力側ディスク４に向け押圧しつつ回転させるローディングカム装置９を構成している。上記出力側ディスク４には出力歯車２１を、キー２２、２２により結合し、これら出力側ディスク４と出力歯車２１とが同期して回転する様にしている。
【０００８】
１対のトラニオン６、６の両端部は１対の支持板２３、２３に、揺動並びに軸方向（図１０の表裏方向、図１１の左右方向）に亙る変位自在に支持している。そして、上記各トラニオン６、６の中間部に形成した円孔２４、２４部分に、変位軸７、７を支持している。これら各変位軸７、７は、互いに平行で且つ偏心した支持軸部２５、２５と枢支軸部２６、２６とを、それぞれ有する。このうちの各支持軸部２５、２５を上記各円孔２４、２４の内側に、ラジアルニードル軸受２７、２７を介して、回転自在に支持している。又、上記各枢支軸部２６、２６の周囲にパワーローラ８、８を、別のラジアルニードル軸受２８、２８を介して、回転自在に支持している。
【０００９】
尚、上記１対の変位軸７、７は、上記入力軸１５に対して１８０度反対側位置に設けている。又、これら各変位軸７、７の各枢支軸部２６、２６が各支持軸部２５、２５に対し偏心している方向は、上記入力側、出力側両ディスク２、４の回転方向に関し同方向（図１１で左右逆方向）としている。又、偏心方向は、上記入力軸１５の配設方向に対しほぼ直交する方向としている。従って、上記各パワーローラ８、８は、上記入力軸１５の配設方向に亙る若干の変位自在に支持される。この結果、回転力の伝達状態で構成各部材に加わる大きな荷重に基づく、これら構成各部材の弾性変形に起因して、上記各パワーローラ８、８が上記入力軸１５の軸方向（図１０の左右方向、図１１の表裏方向）に変位する傾向となった場合でも、上記構成各部品に無理な力を加える事なく、この変位を吸収できる。
【００１０】
又、上記各パワーローラ８、８の外側面と上記各トラニオン６、６の中間部内側面との間には、パワーローラ８、８の外側面の側から順に、スラスト玉軸受２９、２９とスラストニードル軸受３０、３０とを設けている。このうちのスラスト玉軸受２９、２９は、上記各パワーローラ８、８に加わるスラスト方向の荷重を支承しつつ、これら各パワーローラ８、８の回転を許容するものである。又、上記各スラストニードル軸受３０、３０は、上記各パワーローラ８、８から上記各スラスト玉軸受２９、２９を構成する外輪３１、３１に加わるスラスト荷重を支承しつつ、前記各枢支軸部２６、２６及び上記外輪３１、３１が、前記支持軸部２５、２５を中心に揺動する事を許容するものである。
【００１１】
更に、上記各トラニオン６、６の一端部（図１１の左端部）にはそれぞれ駆動ロッド３２、３２を結合し、これら各駆動ロッド３２、３２の中間部外周面に駆動ピストン３３、３３を固設している。そして、これら各駆動ピストン３３、３３を、それぞれ駆動シリンダ３４、３４内に油密に嵌装している。
【００１２】
上述の様に構成するトロイダル型無段変速機の場合、入力軸１５の回転は、ローディングカム装置９を介して入力側ディスク２に伝わる。そして、この入力側ディスク２の回転が、１対のパワーローラ８、８を介して出力側ディスク４に伝わり、更にこの出力側ディスク４の回転が、出力歯車２１より取り出される。入力軸１５と出力歯車２１との間の回転速度比を変える場合には、上記１対の駆動ピストン３３、３３を互いに逆方向に変位させる。これら各駆動ピストン３３、３３の変位に伴って上記１対のトラニオン６、６が、それぞれ逆方向に変位し、例えば図１１の下側のパワーローラ８が同図の右側に、同図の上側のパワーローラ８が同図の左側に、それぞれ変位する。この結果、これら各パワーローラ８、８の周面８ａ、８ａと上記入力側ディスク２及び出力側ディスク４の内側面２ａ、４ａとの当接部に作用する、接線方向の力の向きが変化する。そして、この力の向きの変化に伴って上記各トラニオン６、６が、支持板２３、２３に枢支された枢軸５、５を中心として、互いに逆方向に揺動する。この結果、前述の図８〜９に示した様に、上記各パワーローラ８、８の周面８ａ、８ａと上記各内側面２ａ、４ａとの当接位置が変化し、上記入力軸１５と出力歯車２１との間の回転速度比が変化する。
【００１３】
尚、この様に上記入力軸１５と出力歯車２１との間で回転力の伝達を行なう際には、構成各部材の弾性変形に基づいて上記各パワーローラ８、８が、上記入力軸１５の軸方向に変位し、これら各パワーローラ８、８を枢支している前記各変位軸７、７が、前記各支持軸部２５、２５を中心として僅かに回動する。この回動の結果、前記各スラスト玉軸受２９、２９の外輪３１、３１の外側面と上記各トラニオン６、６の内側面とが相対変位する。これら外側面と内側面との間には、前記各スラストニードル軸受３０、３０が存在する為、この相対変位に要する力は小さい。従って、上述の様に各変位軸７、７の傾斜角度を変化させる為の力が小さくて済む。
【００１４】
上述の様に構成され作用するトロイダル型無段変速機の運転時に各パワーローラ８、８は、大きなスラスト荷重を受けつつ高速で回転する。従って、これら各パワーローラ８、８と各トラニオン６、６の内側面との間に設けるスラスト玉軸受２９には、十分量の潤滑油（トラクションオイル）を供給する必要がある。この為従来から、例えば特開平７−１７４１４６号公報、実開平７−３５８４７号公報等に記載されている様に、パワーローラを支持する為のスラスト玉軸受を構成する外輪に給油孔を形成したり、更にはこのスラスト玉軸受を構成する保持器に給油用の凹溝を形成する事が考えられている。
【００１５】
【発明が解決しようとする課題】
従来構造の場合、パワーローラ８に加わるスラスト荷重を支承しつつ、このパワーローラ８の回転を許容する為のスラスト玉軸受２９のうちの特定部位に給油する事を考慮してはいなかった。言い換えれば、このスラスト玉軸受２９の全周のうちの何れかの部分に給油すれば、当該部分から他の部分に潤滑油が回り、必要な潤滑を行なえると考えていた。
【００１６】
ところが、トロイダル型無段変速機の運転時に上記スラスト玉軸受２９に加わるスラスト荷重は、全周に亙り均等な訳ではなく、トラニオン６の長さ方向に関しては大きく、これと直角な方向に関しては小さくなる。即ち、図１２に示す様に、スラスト玉軸受２９の軌道面上で円周方向等間隔位置に存在する▲１▼〜▲８▼点を考えた場合、各点のスラスト荷重の大きさは、図１３に示す様になる。この図１３は、外径側程大きなスラスト荷重が加わる事を示す。この様にスラスト荷重の大きさが異なる理由は、運転時に上記パワーローラ８に加わる大きなスラスト荷重に基づいて上記トラニオン６が、内側面が凹面となる方向に湾曲する為である。
【００１７】
この様に上記スラスト玉軸受２９に加わるスラスト荷重の大小が、円周方向に関し特定の位相で異なる事に鑑みて、上記スラスト玉軸受２９への給油状態を工夫すれば、少ない給油量で十分な潤滑を行なえて、このスラスト玉軸受２９の転がり抵抗の低減（過剰な潤滑油供給に基づくトルク増大の防止）と転がり疲れ寿命の確保（潤滑油の供給不足による転がり疲れ寿命の低下防止）とを図れる。ところが、従来のトロイダル型無段変速機は、この様な事を考慮してはいなかった。
【００１８】
特に、上記スラスト玉軸受２９内に潤滑油を送り込む為には、このスラスト玉軸受２９を構成する外輪３１の一部に給油孔を形成する事が好ましいが、この外輪３１は変位軸７の中間部に、この変位軸７に対する回転自在に嵌合支持している。この為、上記外輪３１に形成した給油孔の円周方向に亙る位相が、上記スラスト玉軸受２９に加わるスラスト荷重の大きさとの関係で規制できない。
本発明のトロイダル型無段変速機は、上述の様な事情に鑑み、スラスト玉軸受２９のうちの特定部位に給油する構造を実現して、このスラスト玉軸受２９の転がり抵抗の低減と転がり疲れ寿命の確保との両立を図るべく発明したものである。
【００１９】
【課題を解決するための手段】
本発明のトロイダル型無段変速機は、前述した従来のトロイダル型無段変速機と同様に、互いの内側面同士を対向させた状態で、互いに同心に、且つ回転自在に支持された第一、第二のディスクと、これら第一、第二のディスクの中心軸と交差はしないがこれら両ディスクの中心軸の方向に対して直角方向位置である捻れの位置にある枢軸を中心として揺動するトラニオンと、このトラニオンの中間部に上記枢軸と直交する方向に形成された円孔と、互いに平行で且つ偏心した支持軸部及び枢支軸部を有する変位軸と、このうちの支持軸部の外周面と上記円孔の内周面との間に設けられて上記変位軸を上記トラニオンに対して回転自在に支持するラジアルニードル軸受と、上記変位軸のうちで上記トラニオンの内側面から突出した上記枢支軸部の周囲に回転自在に支持された状態で、前記第一、第二の両ディスクの間に挟持されたパワーローラと、このパワーローラの外側面に添設して設けられ、このパワーローラに加わるスラスト方向の荷重を支承しつつ、このパワーローラの回転を許容するスラスト玉軸受と、このスラスト玉軸受を構成するスラスト玉軸受外輪の外側面と上記トラニオンの内側面との間に設けられ、上記パワーローラから上記スラスト玉軸受外輪に加わるスラスト荷重を支承しつつ、上記枢支軸部及び上記スラスト玉軸受外輪が上記支持軸部を中心として揺動する事を許容するスラスト軸受とを備える。そして、上記第一、第二のディスクの内側面はそれぞれ断面が円弧形の凹面であり、パワーローラの周面は球面状の凸面であり、この周面と上記両ディスクの内側面とが互いに当接している。
特に、本発明のトロイダル型無段変速機に於いては、上記スラスト玉軸受外輪が上記変位軸に対し、相対回転を阻止した状態で支持されており、且つ、このスラスト玉軸受外輪の一部で少なくとも上記スラスト玉軸受が受けるスラスト荷重が大きい部分に対応する部分に、この部分に潤滑油を供給する為の給油孔を設けている。
そして、上記相対回転を阻止する為に、請求項１に記載した発明の場合には、上記変位軸を構成する上記枢支軸部の基端部に形成した鍔部に上記スラスト玉軸受外輪を外嵌すると共に、これら鍔部の外周縁部とスラスト玉軸受外輪の内周縁部との間にキーを掛け渡している。
又、請求項２に記載した発明の場合には、内周面形状が小判形である上記スラスト玉軸受外輪を、上記変位軸の中間部に形成した、外周面形状が小判形の鍔部に外嵌している。更に、請求項３に記載した発明の場合には、上記スラスト玉軸受外輪と上記変位軸とをスプライン係合させている。
【００２０】
【作用】
上述の様に構成する本発明のトロイダル型無段変速機により、第一、第二両ディスク同士の間で回転力の伝達を行なわせる作用、並びにこれら両ディスク同士の間の変速比を変化させる作用は、前述した様な従来から知られているトロイダル型無段変速機の場合と同様である。
特に、本発明のトロイダル型無段変速機の場合には、パワーローラを支承するスラスト玉軸受のうち、このスラスト玉軸受が受けるスラスト荷重が大きい部分に潤滑油を、このスラスト玉軸受全体に供給する潤滑油の量を過剰にする事なく、十分に供給できる。
【００２１】
【発明の実施の形態】
図１〜２は、請求項１に対応する、本発明の実施の形態の第１例を示している。尚、本発明の特徴は、パワーローラ８をトラニオン６に支持する為のスラスト玉軸受２９に潤滑油を供給する部分の構造にある。その他の部分の構造及び作用は、前述した従来構造を含め、従来から知られ、或は考えられている各種トロイダル型無段変速機と同様であるから、同等部分に関する図示及び説明は、省略若しくは簡略にし、以下、本発明の特徴部分を中心に説明する。
【００２２】
スラスト玉軸受２９を構成する円輪状の外輪３１は、変位軸７を構成する枢支軸部２６の基端部に形成した鍔部３５に外嵌している。この鍔部３５の外周縁部と上記外輪３１の内周縁部との間にはキー１７を掛け渡して、この外輪３１が上記変位軸７に対し回転する事を防止している。この変位軸７のトラニオン６に対する揺動変位量は限られているので、このトラニオン６の長さ方向と上記外輪３１の円周方向に亙る位相とがずれる程度は、限られたものとなる。
【００２３】
又、上記外輪３１に形成した外輪軌道３７よりも内径側部分の４個所で円周方向等間隔位置に、上記外輪３１の両面同士を連通させる給油孔３８、３８を、この外輪３１の中心軸に対し平行に設けている。そして、これら４本の給油孔３８、３８のうちの２本の給油孔３８、３８を、上記トラニオン６の長さ方向に配置している。又、上記スラスト玉軸受２９を構成する保持器３９の両面には給油溝４０、４０を形成している。
【００２４】
トロイダル型無段変速機の運転時、駆動ロッド３２（図１１）及びトラニオン６の内部に設けた給油通路４１を通じて供給され、上記トラニオン６の中間部内側面に吐出した潤滑油は、上記変位軸７の枢支軸部２６内に設けた第二の給油通路４２を通じて上記スラスト玉軸受２９の内径側及びラジアルニードル軸受２８部分に供給する他、上記各給油孔３８、３８及び給油溝４０、４０を介して、上記スラスト玉軸受２９を構成する玉４３、４３の転動面と、上記外輪軌道３７及びパワーローラ８の内端面に形成した内輪軌道４４との当接部に送り込まれる。
【００２５】
この様に本発明のトロイダル型無段変速機の場合には、上記パワーローラ８を支承するスラスト玉軸受２９のうち、このスラスト玉軸受２９が受けるスラスト荷重が大きい部分である、上記トラニオン６の長さ方向両端部に潤滑油を、他の部分を介する事なく、直接的に送り込む。この為、上記スラスト玉軸受２９全体に供給する潤滑油の量を過剰にする事なく、上記トラニオン６の長さ方向両端部に潤滑油を十分に供給できる。
【００２６】
次に、図３〜４は、請求項４に記載した構造に対応する、本発明に関する参考例の第１例を示している。本参考例の場合、外輪３１に形成した４本の給油孔３８、３８のうち、トラニオン６の長さ方向に位置する２本の給油孔３８、３８の下流端を、上記外輪３１の内周縁と上記外輪軌道３７との間に設けた凹溝４５、４５の内側に開口させている。又、上記外輪３１は変位軸７に設けた鍔部３５に、締り嵌めにより外嵌固定して、この変位軸７に対する相対回転を防止している。
【００２７】
この様な本参考例の場合、トラニオン６の長さ方向に位置する２本の給油孔３８、３８から吐出した潤滑油は、上記各凹溝４５、４５を通じて、スラスト玉軸受２９のうちで最も大きなスラスト荷重が加わる部分に効率良く送り込まれる。その他の部分の構成及び作用は、上述した本発明の実施の形態の第１例の場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。
【００２８】
次に、図５は、請求項２に対応する、本発明の実施の形態の第２例を示している。本例の場合、スラスト玉軸受を構成する外輪３１の内周面形状を小判形とし、この外輪３１を、変位軸７の中間部に形成した、外周面形状が小判形の鍔部に外嵌する事により、上記外輪３１と変位軸７との相対回転を防止する様にしている。その他の構成及び作用は、前述した第１例の場合と同様であるから、同等部分に関する図示並びに説明は省略する。
【００２９】
次に、図６〜７は、請求項５に記載した構造に対応する、本発明に関する参考例の第２例を示している。本参考例の場合、外輪３１に形成した４本の給油孔３８、３８ａのうち、トラニオン６の長さ方向に位置する２本の給油孔３８ａ、３８ａを、上記外輪３１の中心軸に対し傾斜方向に形成し、これら各給油孔３８ａ、３８ａの下流端を、上記外輪３１に形成した外輪軌道３７の内径側端部で、玉４３、４３の転動面と当接しない部分に開口させている。
【００３０】
この様な本参考例の場合、トラニオン６の長さ方向に位置する２本の給油孔３８ａ、３８ａから吐出した潤滑油は、上記外輪軌道３７のうちで最も大きなスラスト荷重が加わる部分に、直接送り込まれる。本参考例の場合も、前述した参考例の第１例の場合と同様、上記外輪３１は変位軸７に設けた鍔部３５に、締り嵌めにより外嵌固定して、この変位軸７に対する相対回転を防止している。その他の部分の構成及び作用は、前述した本発明の実施の形態の第１例の場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。
【００３１】
尚、本発明を実施する場合に、外輪３１と変位軸７との相対回転を防止する為の構造と、スラスト玉軸受２９に潤滑油を送り込む為の構造とは、適宜組み合わせを変えて実施する事もできる。更には、外輪３１と変位軸７との相対回転を防止する為の構造としては、スプライン係合を採用する事もできる。
【００３２】
【発明の効果】
本発明のトロイダル型無段変速機は、以上に述べた通り構成され作用するので、パワーローラを支持する為のスラスト玉軸受に過剰の潤滑油を送り込む事なく、このスラスト玉軸受の耐久性を確保できる。そして、過剰の潤滑油を送り込む必要をなくす事により、上記スラスト玉軸受部分での潤滑油による抵抗の増大を防止すると共に、潤滑油供給の為のポンプ部分での動力損失の低減も図れる。この結果、優れた効率及び耐久性を有するトロイダル型無段変速機を実現して、トロイダル型無段変速機の実用化に寄与できる。
【図面の簡単な説明】
【図１】本発明の実施の形態の第１例を示す、トラニオンに対するパワーローラ支持部分の断面図。
【図２】パワーローラと保持器及び玉を除くと共に変位軸の一部を省略して、図１の下方から見た図。
【図３】本発明に関する参考例の第１例を示す、図１と同様の図。
【図４】パワーローラと保持器及び玉を除くと共に変位軸の一部を省略して、図３の下方から見た図。
【図５】本発明の実施の形態の第２例を示す、図４と同様の図。
【図６】本発明に関する参考例の第２例を示す、図１と同様の図。
【図７】パワーローラと保持器及び玉を除くと共に変位軸の一部を省略して、図６の下方から見た図。
【図８】本発明の対象となるトロイダル型無段変速機を最大減速時の状態で示す略側面図。
【図９】同じく最大増速時の状態で示す略側面図。
【図１０】トロイダル型無段変速機の具体的構造の１例を示す断面図。
【図１１】図１０のＡ−Ａ断面図。
【図１２】パワーローラをトラニオンに支持する為のスラスト玉軸受の位相を説明する為の略図。
【図１３】パワーローラをトラニオンに支持する為のスラスト玉軸受の円周方向に亙る位相とスラスト荷重の大きさとの関係を表す線図。
【符号の説明】
１入力軸
２入力側ディスク
２ａ内側面
３出力軸
４出力側ディスク
４ａ内側面
５枢軸
６トラニオン
７変位軸
８パワーローラ
８ａ周面
９ローディングカム装置
１０ローディングカム
１１保持器
１２ローラ
１３、１４カム面
１５入力軸
１６ニードル軸受
１７貫通孔
１８係止溝
１９止め輪
２０鍔部
２１出力歯車
２２キー
２３支持板
２４円孔
２５支持軸部
２６枢支軸部
２７ラジアルニードル軸受
２８ラジアルニードル軸受
２９スラスト玉軸受
３０スラストニードル軸受
３１外輪
３２駆動ロッド
３３駆動ピストン
３４駆動シリンダ
３５鍔部
３６キー
３７外輪軌道
３８、３８ａ給油孔
３９保持器
４０給油溝
４１給油通路
４２第二の給油通路
４３玉
４４内輪軌道
４５凹溝[0001]
BACKGROUND OF THE INVENTION
The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for an automobile or as a transmission for various industrial machines.
[0002]
[Prior art]
The use of a toroidal continuously variable transmission as schematically shown in FIGS. This toroidal continuously variable transmission, for example, as disclosed in Japanese Utility Model Laid-Open No. 62-71465, supports an input side disk 2 concentrically with an input shaft 1, and outputs arranged concentrically with the input shaft 1. An output side disk 4 is fixed to the end of the shaft 3. On the inner side of the casing in which the toroidal continuously variable transmission is housed, trunnions 6 and 6 that swing around pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided.
[0003]
That is, the trunnions 6 and 6 disposed in the portions deviating from the central axes of the two disks 2 and 4 have the pivots 5 and 5 on the outer surfaces of both ends, and the direction of the central axes of the two disks 2 and 4. Are provided at right angles to each other and concentrically with each other. In addition, the base portions of the displacement shafts 7 and 7 are supported at intermediate portions of the trunnions 6 and 6, and the trunnions 6 and 6 are swung around the pivot shafts 5 and 5, so that the respective displacements are displaced. The inclination angle of the shafts 7 and 7 can be freely adjusted. Power rollers 8 and 8 are rotatably supported around the displacement shafts 7 and 7 supported by the trunnions 6 and 6, respectively. Each of these power rollers 8 and 8 is sandwiched between inner surfaces 2a and 4a of the input side and output side disks 2 and 4 facing each other. Each of these inner side surfaces 2a, 4a has a concave surface obtained by rotating a circular arc with the pivot axis 5 as the center. And the peripheral surfaces 8a and 8a of each said power roller 8 and 8 formed in the spherical convex surface are made to contact | abut to the said inner surface 2a and 4a.
[0004]
A loading cam device 9 is provided between the input shaft 1 and the input side disc 2, and the input cam 2 is elastically pressed against the output side disc 4 by the loading cam device 9, The side disk 2 is rotatable. The loading cam device 9 includes a loading cam 10 that rotates together with the input shaft 1, and a plurality of (for example, four) rollers 12 and 12 that are rotatably held by a cage 11. On one side surface (the right side surface in FIGS. 8 to 9) of the loading cam 10 is formed a cam surface 13 that is uneven in the circumferential direction, and the outer side surface of the input disk 2 (the left side surface in FIGS. 8 to 9). ) Also has a cam surface 14 having a similar shape. The plurality of rollers 12 and 12 are supported so as to be rotatable about the radial axis with respect to the center of the input shaft 1.
[0005]
When the toroidal type continuously variable transmission configured as described above is used, when the loading cam 10 rotates as the input shaft 1 rotates, the cam surface 13 causes the plurality of rollers 12 and 12 to move outside the input side disk 2. The cam surface 14 formed on the side surface is pressed. As a result, the input-side disk 2 is pressed against the plurality of power rollers 8 and 8 and at the same time, based on the pressing force between the cam surfaces 13 and 14 and the plurality of rollers 12 and 12, the input disk 2 is pressed. The side disk 2 rotates. The rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, 8, and the output shaft 3 fixed to the output side disk 4 rotates.
[0006]
When changing the rotational speed ratio (transmission ratio) between the input shaft 1 and the output shaft 3, and when first decelerating between the input shaft 1 and the output shaft 3, the pivots 5 and 5 are used as the centers. Each trunnion 6, 6 is swung in a predetermined direction. As shown in FIG. 8, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 are formed on a portion near the center of the inner surface 2a of the input side disc 2 and a portion near the outer periphery of the inner surface 4a of the output side disc 4, respectively. The displacement shafts 7 and 7 are inclined so as to contact each other. On the other hand, when increasing the speed, the trunnions 6 and 6 are swung in the opposite directions around the pivots 5 and 5. The peripheral surfaces 8a and 8a of the power rollers 8 and 8 are formed on the outer peripheral portion of the inner side surface 2a of the input side disc 2 and the central portion of the inner side surface 4a of the output side disc 4 as shown in FIG. The displacement shafts 7 and 7 are inclined so as to contact each other. If the inclination angle of each of the displacement shafts 7 and 7 is set intermediate between those shown in FIGS. 8 and 9, an intermediate transmission ratio can be obtained between the input shaft 1 and the output shaft 3.
[0007]
FIGS. 10 to 11 show an example of a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application No. 63-69293 (Japanese Utility Model Laid-Open No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around needle-shaped input shafts 15 via needle bearings 16 and 16, respectively. That is, through-holes 17 and 17 having a circular cross-sectional shape are formed in the center of the input side disk 2 and the output side disk 4, and the inner side surface and the outer side surface of each of the disks 2 and 4 are axially directed (FIG. 10). In the left-right direction). The needle bearings 16 and 16 are provided between the inner peripheral surface of the through holes 17 and 17 and the outer peripheral surface of the intermediate portion of the input shaft 15. Further, retaining rings 19 and 19 are latched in locking grooves 18 and 18 formed on the inner peripheral surface of the through holes 17 and 17 on the inner surface side, and the needle bearings 16 and 16 are inserted into the through holes. The holes 17 and 17 prevent the discs 2 and 4 from coming out to the inner side surfaces 2a and 4a. The loading cam 10 is spline-engaged with the outer peripheral surface of the end of the input shaft 15 (the left end of FIG. 10), and the outward flange-like flange 20 prevents movement away from the input side disk 2. ing. The loading cam 10 and the rollers 12 and 12 constitute a loading cam device 9 that rotates the input side disk 2 while pressing the input side disk 2 against the output side disk 4 based on the rotation of the input shaft 15. Yes. An output gear 21 is coupled to the output side disk 4 by keys 22 and 22 so that the output side disk 4 and the output gear 21 rotate in synchronization.
[0008]
Both ends of the pair of trunnions 6 and 6 are supported on the pair of support plates 23 and 23 so as to be freely swingable and displaceable in the axial direction (front and back direction in FIG. 10, left and right direction in FIG. 11). The displacement shafts 7 and 7 are supported in the circular holes 24 and 24 formed in the intermediate portions of the trunnions 6 and 6. Each of these displacement shafts 7 and 7 has support shaft portions 25 and 25 and pivot shaft portions 26 and 26 that are parallel to each other and eccentric, respectively. Of these, the support shaft portions 25 and 25 are rotatably supported inside the circular holes 24 and 24 via radial needle bearings 27 and 27. Further, the power rollers 8 and 8 are rotatably supported around the pivot shafts 26 and 26 via other radial needle bearings 28 and 28, respectively.
[0009]
The pair of displacement shafts 7 and 7 are provided at positions opposite to the input shaft 15 by 180 degrees. The direction in which the pivot shafts 26 and 26 of the displacement shafts 7 and 7 are eccentric with respect to the support shafts 25 and 25 is the same with respect to the rotation direction of the input side and output side disks 2 and 4. It is set as the direction (left-right reverse direction in FIG. 11). The eccentric direction is a direction substantially perpendicular to the direction in which the input shaft 15 is disposed. Accordingly, the power rollers 8 and 8 are supported so as to be slightly displaceable in the direction in which the input shaft 15 is disposed. As a result, due to the elastic deformation of the constituent members based on the large load applied to the constituent members in the state of transmission of the rotational force, the power rollers 8 and 8 are moved in the axial direction of the input shaft 15 (see FIG. 10). Even when it tends to be displaced in the left-right direction (the front-back direction in FIG. 11), this displacement can be absorbed without applying an excessive force to each component.
[0010]
In addition, between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6 and 6, the thrust ball bearings 29 and 29 and the thrust are sequentially arranged from the outer surface side of the power rollers 8 and 8. Needle bearings 30 and 30 are provided. Of these, the thrust ball bearings 29 and 29 support the rotation of the power rollers 8 and 8 while supporting the load in the thrust direction applied to the power rollers 8 and 8. The thrust needle bearings 30 and 30 support the pivot shafts while supporting thrust loads applied to the outer rings 31 and 31 constituting the thrust ball bearings 29 and 29 from the power rollers 8 and 8. 26 and 26 and the outer rings 31 and 31 are allowed to swing around the support shaft portions 25 and 25.
[0011]
Further, driving rods 32 and 32 are coupled to one end portions (the left end portion in FIG. 11) of the trunnions 6 and 6, respectively, and driving pistons 33 and 33 are fixed to the outer peripheral surfaces of the intermediate portions of the driving rods 32 and 32, respectively. Has been established. These drive pistons 33 and 33 are oil-tightly fitted in the drive cylinders 34 and 34, respectively.
[0012]
In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the loading cam device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 through a pair of power rollers 8 and 8, and the rotation of the output side disk 4 is further taken out from the output gear 21. When changing the rotational speed ratio between the input shaft 15 and the output gear 21, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 6 and 6 are displaced in opposite directions. For example, the lower power roller 8 in FIG. The power rollers 8 are displaced to the left in the figure. As a result, the direction of the tangential force acting on the contact portion between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. To do. The trunnions 6 and 6 swing in opposite directions around the pivots 5 and 5 pivotally supported by the support plates 23 and 23 as the force changes. As a result, as shown in FIGS. 8 to 9 described above, the contact position between the peripheral surfaces 8a and 8a of the power rollers 8 and 8 and the inner surfaces 2a and 4a is changed. The rotational speed ratio with the output gear 21 changes.
[0013]
When the rotational force is transmitted between the input shaft 15 and the output gear 21 in this way, the power rollers 8 and 8 are connected to the input shaft 15 based on the elastic deformation of the constituent members. The displacement shafts 7 and 7 that are displaced in the axial direction and pivotally support the power rollers 8 and 8 are slightly rotated around the support shaft portions 25 and 25. As a result of this rotation, the outer side surfaces of the outer rings 31, 31 of the thrust ball bearings 29, 29 and the inner side surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 30, 30 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 7, 7 can be small.
[0014]
During operation of the toroidal type continuously variable transmission configured and operated as described above, the power rollers 8 and 8 rotate at a high speed while receiving a large thrust load. Accordingly, it is necessary to supply a sufficient amount of lubricating oil (traction oil) to the thrust ball bearing 29 provided between each of the power rollers 8 and 8 and the inner surface of each trunnion 6 and 6. Therefore, conventionally, as described in, for example, JP-A-7-174146, JP-A-7-35847, etc., an oil supply hole is formed in an outer ring constituting a thrust ball bearing for supporting a power roller. In addition, it has been considered to form a groove for oil supply in the cage constituting the thrust ball bearing.
[0015]
[Problems to be solved by the invention]
In the case of the conventional structure, it is not considered to supply oil to a specific portion of the thrust ball bearing 29 for allowing the rotation of the power roller 8 while supporting the thrust load applied to the power roller 8. In other words, it has been thought that if any part of the entire circumference of the thrust ball bearing 29 is supplied with oil, the lubricating oil will flow from the part to the other part and the necessary lubrication can be performed.
[0016]
However, the thrust load applied to the thrust ball bearing 29 during operation of the toroidal-type continuously variable transmission is not uniform over the entire circumference, and is large in the length direction of the trunnion 6 and small in the direction perpendicular thereto. Become. That is, as shown in FIG. 12, when considering the points (1) to (8) existing at equidistant positions in the circumferential direction on the raceway surface of the thrust ball bearing 29, the magnitude of the thrust load at each point is As shown in FIG. FIG. 13 shows that a larger thrust load is applied to the outer diameter side. The reason why the magnitudes of the thrust loads are different in this way is that the trunnion 6 is curved in a direction in which the inner surface becomes concave based on a large thrust load applied to the power roller 8 during operation.
[0017]
In view of the fact that the magnitude of the thrust load applied to the thrust ball bearing 29 differs in a specific phase with respect to the circumferential direction as described above, if the oil supply state to the thrust ball bearing 29 is devised, a small oil supply amount is sufficient. Lubrication is performed to reduce the rolling resistance of the thrust ball bearing 29 (preventing an increase in torque due to excessive supply of lubricating oil) and to secure a rolling fatigue life (preventing a decrease in rolling fatigue life due to insufficient supply of lubricating oil). I can plan. However, the conventional toroidal-type continuously variable transmission has not taken this into consideration.
[0018]
In particular, in order to feed the lubricating oil into the thrust ball bearing 29, it is preferable to form an oil supply hole in a part of the outer ring 31 constituting the thrust ball bearing 29. This part is fitted and supported so as to be rotatable with respect to the displacement shaft 7. For this reason, the phase over the circumferential direction of the oil supply hole formed in the outer ring 31 cannot be regulated in relation to the magnitude of the thrust load applied to the thrust ball bearing 29.
In view of the circumstances as described above, the toroidal continuously variable transmission according to the present invention realizes a structure in which oil is supplied to a specific portion of the thrust ball bearing 29 to reduce the rolling resistance of the thrust ball bearing 29 and to cause rolling fatigue. The present invention was invented to achieve both a long life.
[0019]
[Means for Solving the Problems]
The toroidal type continuously variable transmission of the present invention is the same as the above-described conventional toroidal type continuously variable transmission, in which the inner surfaces of the toroidal type continuously variable transmission are opposed to each other and supported concentrically and rotatably. Oscillates around the pivot axis that does not intersect the center axes of the second disk and the first and second disks but is at a right angle to the direction of the center axes of both disks A trunnion, a circular hole formed in an intermediate portion of the trunnion in a direction orthogonal to the pivot axis, a displacement shaft having a support shaft portion and a pivot shaft portion that are parallel and eccentric to each other, and a support shaft portion of these A radial needle bearing which is provided between the outer peripheral surface of the circular hole and the inner peripheral surface of the circular hole and rotatably supports the displacement shaft with respect to the trunnion, and protrudes from the inner surface of the trunnion among the displacement shafts The above pivot axis And a power roller sandwiched between the first and second discs and rotatably attached to the outer surface of the power roller in a state of being supported rotatably around the power roller. A thrust ball bearing that supports the rotation of the power roller while supporting a load in the thrust direction, and is provided between the outer surface of the outer ring of the thrust ball bearing constituting the thrust ball bearing and the inner surface of the trunnion, A thrust bearing that supports a thrust load applied to the thrust ball bearing outer ring from a power roller and that allows the pivot shaft and the thrust ball bearing outer ring to swing around the support shaft. The inner surfaces of the first and second disks are concave surfaces each having a circular cross section, and the peripheral surface of the power roller is a spherical convex surface, and the peripheral surface and the inner surfaces of the two disks are They are in contact with each other.
In particular, in the toroidal type continuously variable transmission of the present invention, the thrust ball bearing outer ring is supported in a state in which relative rotation is prevented with respect to the displacement shaft, and a part of the thrust ball bearing outer ring is supported. And at least a portion corresponding to a portion where the thrust load received by the thrust ball bearing is large is provided with an oil supply hole for supplying lubricating oil to this portion.
In order to prevent the relative rotation, in the case of the invention described in claim 1, the thrust ball bearing outer ring is attached to the flange portion formed at the base end portion of the pivot shaft portion constituting the displacement shaft. A key is provided between the outer peripheral edge of the flange and the inner peripheral edge of the thrust ball bearing outer ring.
Further, in the case of the invention described in claim 2, the thrust ball bearing outer ring having an inner peripheral surface shape of an oval shape is formed in an intermediate portion of the displacement shaft, and the outer peripheral surface shape is an oval flange portion. It is fitted. Furthermore, in the case of the invention described in claim 3, the thrust ball bearing outer ring and the displacement shaft are spline engaged.
[0020]
[Action]
With the toroidal-type continuously variable transmission of the present invention configured as described above, the action of transmitting rotational force between the first and second disks and the gear ratio between the two disks are changed. The operation is the same as that of the conventional toroidal type continuously variable transmission as described above.
In particular, in the case of the toroidal type continuously variable transmission according to the present invention, among the thrust ball bearings that support the power roller, the lubricating oil is supplied to the entire thrust ball bearing in the portion where the thrust load received by the thrust ball bearing is large. It is possible to supply enough without excessive amount of lubricating oil.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
1 and 2 show a first example of an embodiment of the present invention corresponding to claim 1 . The feature of the present invention lies in the structure of the portion for supplying the lubricating oil to the thrust ball bearing 29 for supporting the power roller 8 on the trunnion 6. Since the structure and operation of other parts are the same as those of various toroidal type continuously variable transmissions that are conventionally known or considered, including the conventional structure described above, the illustration and explanation of equivalent parts are omitted or omitted. For simplicity, the following description will focus on the features of the present invention.
[0022]
An annular outer ring 31 constituting the thrust ball bearing 29 is fitted on a flange 35 formed at the proximal end of the pivot shaft 26 constituting the displacement shaft 7. A key 17 is spanned between the outer peripheral edge of the flange 35 and the inner peripheral edge of the outer ring 31 to prevent the outer ring 31 from rotating with respect to the displacement shaft 7. Since the swing displacement amount of the displacement shaft 7 with respect to the trunnion 6 is limited, the extent to which the length direction of the trunnion 6 and the phase of the outer ring 31 in the circumferential direction are shifted is limited.
[0023]
Also, oil supply holes 38 and 38 for communicating both surfaces of the outer ring 31 at equal intervals in the circumferential direction at four locations on the inner diameter side of the outer ring raceway 37 formed in the outer ring 31 are provided as central axes of the outer ring 31. Are provided in parallel with each other. Of these four oil supply holes 38, two oil supply holes 38, 38 are arranged in the length direction of the trunnion 6. Further, oil supply grooves 40 and 40 are formed on both surfaces of the cage 39 constituting the thrust ball bearing 29.
[0024]
During operation of the toroidal continuously variable transmission, the lubricating oil supplied through the drive rod 32 (FIG. 11) and the oil supply passage 41 provided inside the trunnion 6 and discharged to the inner side surface of the trunnion 6 is the displacement shaft 7. In addition to supplying to the inner diameter side of the thrust ball bearing 29 and the radial needle bearing 28 through a second oil supply passage 42 provided in the pivot shaft 26, the oil supply holes 38, 38 and the oil supply grooves 40, 40 are provided. Then, the balls 43 and 43 constituting the thrust ball bearing 29 are fed into contact portions between the rolling surfaces of the balls 43 and 43 and the inner ring raceway 44 formed on the inner raceway 37 and the inner end face of the power roller 8.
[0025]
Thus, in the case of the toroidal type continuously variable transmission according to the present invention, the trunnion 6 is a portion of the thrust ball bearing 29 that supports the power roller 8 and that has a large thrust load received by the thrust ball bearing 29. Lubricating oil is fed directly to both ends in the length direction without passing through other parts. Therefore, the lubricating oil can be sufficiently supplied to both ends of the trunnion 6 in the longitudinal direction without excessive amount of the lubricating oil supplied to the entire thrust ball bearing 29.
[0026]
Next, FIGS. 3 to 4 show a first example of a reference example related to the present invention, which corresponds to the structure described in claim 4 . In the case of this reference example, of the four oil supply holes 38, 38 formed in the outer ring 31, the downstream ends of the two oil supply holes 38, 38 positioned in the length direction of the trunnion 6 are used as the inner peripheral edge of the outer ring 31. And the inside of the concave grooves 45, 45 provided between the outer ring raceway 37 and the outer ring raceway 37. Further, the outer ring 31 is externally fixed to the flange 35 provided on the displacement shaft 7 by an interference fit to prevent relative rotation with respect to the displacement shaft 7.
[0027]
In the case of this reference example , the lubricating oil discharged from the two oil supply holes 38, 38 positioned in the length direction of the trunnion 6 is the most among the thrust ball bearings 29 through the concave grooves 45, 45. It is efficiently fed into the part where a large thrust load is applied. Since the configuration and operation of the other parts are the same as in the case of the first example of the embodiment of the present invention described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0028]
Next, FIG. 5 shows a second example of an embodiment of the present invention corresponding to claim 2 . In the case of this example, the inner peripheral surface shape of the outer ring 31 constituting the thrust ball bearing is an oval shape, and the outer ring 31 is formed in the middle portion of the displacement shaft 7 and is fitted on a flange portion having an outer peripheral surface shape. By doing so, relative rotation between the outer ring 31 and the displacement shaft 7 is prevented. Since other configurations and operations are the same as those in the case of the first example described above, illustration and description regarding equivalent parts are omitted.
[0029]
Next, FIGS. 6 to 7 show a second example of a reference example related to the present invention corresponding to the structure described in claim 5 . In the case of this reference example, of the four oil supply holes 38, 38 a formed in the outer ring 31, the two oil supply holes 38 a, 38 a positioned in the length direction of the trunnion 6 are inclined with respect to the central axis of the outer ring 31. The downstream end of each of these oil supply holes 38a, 38a is opened at the inner diameter side end portion of the outer ring raceway 37 formed in the outer ring 31 at a portion that does not contact the rolling surface of the balls 43, 43. Yes.
[0030]
In the case of this reference example , the lubricating oil discharged from the two oil supply holes 38a, 38a positioned in the length direction of the trunnion 6 is directly applied to the portion of the outer ring raceway 37 where the largest thrust load is applied. It is sent. Also in the case of this reference example, as in the case of the first example of the reference example described above, the outer ring 31 is externally fixed to the flange portion 35 provided on the displacement shaft 7 by an interference fit, and relative to the displacement shaft 7. Prevents rotation. Since the configuration and operation of the other parts are the same as in the case of the first example of the embodiment of the present invention described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0031]
In carrying out the present invention, the structure for preventing the relative rotation between the outer ring 31 and the displacement shaft 7 and the structure for feeding the lubricating oil to the thrust ball bearing 29 are appropriately changed in combination. You can also do things. Furthermore, as a structure for preventing the relative rotation between the outer ring 31 and the displacement shaft 7, spline engagement can be adopted .
[0032]
【The invention's effect】
Since the toroidal type continuously variable transmission of the present invention is configured and operates as described above, the durability of the thrust ball bearing can be improved without supplying excessive lubricating oil to the thrust ball bearing for supporting the power roller. It can be secured. Further, by eliminating the need to feed in excess lubricating oil, it is possible to prevent an increase in resistance due to the lubricating oil at the thrust ball bearing portion and to reduce power loss at the pump portion for supplying the lubricating oil. As a result, a toroidal-type continuously variable transmission having excellent efficiency and durability can be realized, thereby contributing to the practical use of the toroidal-type continuously variable transmission.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a power roller support portion for a trunnion, showing a first example of an embodiment of the present invention.
FIG. 2 is a view seen from below in FIG. 1 with the power roller, the cage, and the balls removed, and a part of the displacement shaft omitted.
FIG. 3 is a view similar to FIG. 1, showing a first example of a reference example related to the present invention .
4 is a view as seen from the bottom of FIG. 3, excluding the power roller, the cage, and the balls, and omitting a part of the displacement shaft.
FIG. 5 is a view similar to FIG. 4, showing a second example of an embodiment of the present invention.
FIG. 6 is a view similar to FIG. 1, showing a second example of a reference example related to the present invention .
7 is a view seen from the lower side of FIG. 6 with the power roller, the cage, and the balls removed, and a part of the displacement shaft omitted.
FIG. 8 is a schematic side view showing the toroidal continuously variable transmission that is the subject of the present invention in a state of maximum deceleration.
FIG. 9 is a schematic side view showing the state of the maximum speed increase.
FIG. 10 is a sectional view showing an example of a specific structure of a toroidal-type continuously variable transmission.
11 is a cross-sectional view taken along line AA in FIG.
FIG. 12 is a schematic diagram for explaining a phase of a thrust ball bearing for supporting a power roller on a trunnion.
FIG. 13 is a diagram showing the relationship between the phase over the circumferential direction of the thrust ball bearing for supporting the power roller on the trunnion and the magnitude of the thrust load.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 2a Inner side surface 3 Output shaft 4 Output side disk 4a Inner side surface 5 Pivot 6 Trunnion 7 Displacement shaft 8 Power roller 8a Circumferential surface 9 Loading cam apparatus 10 Loading cam 11 Cage 12 Rollers 13, 14 Cam surface 15 Input shaft 16 Needle bearing 17 Through hole 18 Locking groove 19 Retaining ring 20 Reel 21 Output gear 22 Key 23 Support plate 24 Circular hole 25 Support shaft portion 26 Pivot shaft portion 27 Radial needle bearing 28 Radial needle bearing 29 Thrust ball Bearing 30 Thrust needle bearing 31 Outer ring 32 Drive rod 33 Drive piston 34 Drive cylinder 35 Ridge portion 36 Key 37 Outer ring raceway 38, 38a Oil supply hole 39 Cage 40 Oil supply groove 41 Oil supply passage 42 Second oil supply passage 43 Ball 44 Inner ring raceway 45 Ditch

Claims

The first and second discs supported concentrically and rotatably with the inner surfaces facing each other, and the central axes of these first and second discs do not intersect, but both A trunnion that swings about a pivot at a twist position that is a position perpendicular to the direction of the central axis of the disk, and a circular hole formed in a direction perpendicular to the pivot at the middle of the trunnion, A displacement shaft having a parallel and eccentric support shaft portion and a pivot shaft portion, and the displacement shaft is provided between the outer peripheral surface of the support shaft portion and the inner peripheral surface of the circular hole, and the displacement shaft serves as the trunnion. A radial needle bearing that is rotatably supported with respect to the pivot shaft portion that protrudes from the inner surface of the trunnion among the displacement shafts; Sandwiched between both discs A thrust roller bearing that is provided to be attached to the outer surface of the power roller, and that supports a thrust load applied to the power roller while allowing the power roller to rotate, and constitutes the thrust ball bearing The thrust ball bearing outer ring and the thrust ball bearing outer ring provided between the outer side surface of the thrust ball bearing outer ring and the inner side surface of the trunnion while supporting the thrust load applied from the power roller to the thrust ball bearing outer ring. A thrust bearing that allows the support shaft to swing around the support shaft, and the inner surfaces of the first and second disks are concave surfaces each having an arc shape in cross section, and the peripheral surface of the power roller is In a toroidal type continuously variable transmission which is a spherical convex surface, and whose peripheral surface and the inner side surfaces of the two disks are in contact with each other, the thrust ball bearing outer ring is Relative position axis, the flange portion formed on the proximal end of the pivot shaft portion which constitutes the displacement shaft with externally fitted to the thrust ball bearing outer ring, the outer peripheral edge and a thrust ball bearing outer ring of the flange portion It is supported in a state in which relative rotation is prevented by a key spanned between the inner peripheral edge portion , and corresponds to a portion where at least the thrust load received by the thrust ball bearing is a part of the thrust ball bearing outer ring. A toroidal-type continuously variable transmission characterized in that an oil supply hole for supplying lubricating oil to the part is provided in the part.

The first and second discs supported concentrically and rotatably with the inner surfaces facing each other, and the central axes of these first and second discs do not intersect, but both A trunnion that swings about a pivot at a twist position that is a position perpendicular to the direction of the central axis of the disk, and a circular hole formed in a direction perpendicular to the pivot at the middle of the trunnion, A displacement shaft having a parallel and eccentric support shaft portion and a pivot shaft portion, and the displacement shaft is provided between the outer peripheral surface of the support shaft portion and the inner peripheral surface of the circular hole, and the displacement shaft serves as the trunnion. A radial needle bearing that is rotatably supported with respect to the pivot shaft portion that protrudes from the inner surface of the trunnion among the displacement shafts; Sandwiched between both discs A thrust roller bearing that is provided to be attached to the outer surface of the power roller, and that supports a thrust load applied to the power roller while allowing the power roller to rotate, and constitutes the thrust ball bearing The thrust shaft bearing and the thrust ball bearing outer ring are provided between the outer side surface of the thrust ball bearing outer ring and the inner side surface of the trunnion, and support the thrust load applied from the power roller to the thrust ball bearing outer ring. A thrust bearing that allows the support shaft to swing around the support shaft, and the inner surfaces of the first and second disks are concave surfaces each having an arc shape in cross section, and the peripheral surface of the power roller is In the toroidal type continuously variable transmission which is a spherical convex surface, and the circumferential surface and the inner side surfaces of the two disks are in contact with each other, the inner circumferential surface shape is an oval shape A state in which the thrust ball bearing outer ring is prevented from rotating relative to the displacement shaft by externally fitting the outer ball of the last ball bearing to the flange portion having an outer peripheral shape formed in the middle portion of the displacement shaft. And at least a portion corresponding to the portion of the thrust ball bearing outer ring where the thrust load received by the thrust ball bearing is large is provided with an oil supply hole for supplying lubricating oil to this portion. A toroidal-type continuously variable transmission characterized by

The first and second discs supported concentrically and rotatably with the inner surfaces facing each other, and the central axes of these first and second discs do not intersect, but both A trunnion that swings about a pivot at a twist position that is perpendicular to the direction of the central axis of the disk, and a direction perpendicular to the pivot at the middle of the trunnion Between the outer peripheral surface of the support shaft portion and the inner peripheral surface of the circular hole, the circular shaft formed in the direction, the displacement shaft having the support shaft portion and the pivot shaft portion which are parallel and eccentric to each other. A radial needle bearing that is provided and rotatably supports the displacement shaft with respect to the trunnion, and is rotatably supported around the pivot shaft portion that protrudes from the inner surface of the trunnion among the displacement shafts. In a state, the power roller sandwiched between the first and second disks, and provided to be attached to the outer surface of the power roller, while supporting the load in the thrust direction applied to the power roller, A thrust ball bearing that allows the rotation of the power roller; and an outer surface of an outer ring of a thrust ball bearing that constitutes the thrust ball bearing and an inner surface of the trunnion; A thrust bearing that allows the pivot shaft and the thrust ball bearing outer ring to swing around the support shaft while supporting a thrust load applied to the first and second discs. Each inner surface is a concave surface having an arc-shaped cross section, and the circumferential surface of the power roller is a spherical convex surface, and this circumferential surface and the inner surfaces of the two disks are in contact with each other. The thrust ball bearing outer ring is supported in a state in which relative rotation is prevented by spline engagement with the displacement shaft, and at least a part of the thrust ball bearing outer ring receives the thrust ball bearing. A toroidal-type continuously variable transmission characterized in that an oil supply hole for supplying lubricating oil to a portion corresponding to a portion having a large thrust load is provided.

Out of the four oil supply holes formed in the thrust ball bearing outer ring at equal intervals in the circumferential direction, the downstream ends of the two oil supply holes located in the trunnion length direction are connected to the inner peripheral edge of the thrust ball bearing outer ring, The toroidal type according to any one of claims 1 to 3, wherein the thrust ball bearing is opened inside a pair of concave grooves provided between an outer ring raceway formed on an axial side surface of the outer ring. Continuously variable transmission.

Of the four oil supply holes formed in the thrust ball bearing outer ring at equal intervals in the circumferential direction, two oil supply holes positioned in the trunnion length direction are inclined with respect to the central axis of the thrust ball bearing outer ring. The downstream end of both oil supply holes formed in the inclined direction is formed at the inner diameter side end of the outer ring raceway formed on the axial side surface of the thrust ball bearing outer ring, and the rolling surface of the ball constituting the thrust ball bearing The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the toroidal continuously variable transmission is opened at a portion that does not contact.