JP3738686B2

JP3738686B2 - Shift control device for toroidal type continuously variable transmission

Info

Publication number: JP3738686B2
Application number: JP2000358651A
Authority: JP
Inventors: 秀剛東; 俊一忍足
Original assignee: Nissan Motor Co Ltd
Current assignee: Nissan Motor Co Ltd
Priority date: 2000-11-27
Filing date: 2000-11-27
Publication date: 2006-01-25
Anticipated expiration: 2020-11-27
Also published as: JP2002161958A

Description

【０００１】
【発明の属する技術分野】
本発明は、車両等に適用され、変速比を無段階に変えることができるトロイダル型無段変速機の変速制御装置の技術分野に属する。
【０００２】
【従来の技術】
従来、トロイダル型無段変速機の変速制御装置としては、例えば、特開平１０−１３２０６６号公報に記載のものが知られている。
【０００３】
この公報には、図１２に示すように、相互に対向する面をトロイド曲面に形成すると共に、同軸上に対向配置された入出力ディスクの対向面に挟持されて傾転自在なパワーローラと、該パワーローラを回転自在に支持すると共に、傾転軸まわりに回動可能、かつ、傾転軸方向に変位可能なトラニオン（パワーローラ支持部材）と、該トラニオンを傾転軸方向へ駆動する油圧シリンダと、バルブボディに収装され、前記油圧シリンダのシリンダ室への油圧を制御する変速制御弁と、該変速制御弁を駆動する変速アクチュエータと、前記トラニオンに設けられたプリセスカムに応動してトラニオンの回動運動を往復運動に変換するフィードバックリンクと、該フィードバックリンクと前記変速アクチュエータと前記変速制御弁とを互いに連結した図外の変速リンクとを備え、トラニオンの回動量（実変速比）と変速アクチュエータの駆動量（目標変速比）とを、変速リンクを介して変速制御弁に伝え、実変速比が目標変速比になるよう変速比フィードバック制御を行う装置が記載されている。
【０００４】
このようなトロイダル型無段変速機では、所定の強度を確保しながら軽量化を図るため、構成要素毎に異なる材料を採用しており、例えば、変速機ケースとバルブボディをアルミ合金（図１２の白抜きで示す）で構成し、その他の変速機構要素（トラニオン、ピストン、プリセスカム、フィードバックリンク、スプール、スリーブ等）を鉄（図１２のハッチングで示す）で構成している。
【０００５】
このように固定要素と変速機構要素とが熱膨張係数の異なる素材により製造されているため、運転状態に応じて作動油や各部品の温度が無段変速機始動時の温度から変化すると、パワーローラを支持するトラニオンがＹ軸方向へ膨張または収縮し、この温度変化に伴ってアルミ合金で構成された変速機ケースは、鉄とアルミの熱膨張係数の違いから、トラニオン以上に膨張または収縮するので、ディスク軸中心とパワーローラの中心を一致させた際、プリセスカムからこのディスク軸中心までのトラニオンの長さＬが相対的に変化し、この熱膨張による変位が倣い機構を介してフィードバックリンクに入力される。ちなみに、アルミの熱膨張係数は、２３．０×１０^−６／℃であるのに対し、鉄の熱膨張係数は、１１．７６×１０^−６／℃である。
【０００６】
そこで、この熱膨張による変速比のずれ量だけ変速比変更手段への制御量を変更する温度補償制御を行うトロイダル型無段変速機の変速制御装置が記載されている。
【０００７】
【発明が解決しようとする課題】
しかしながら、従来のトロイダル型無段変速機の変速制御装置にあっては、変速制御の電子制御側で温度補償を行う構成となっているため、変速機の温度を検出または推定する温度検出手段を要するし、また、変速制御プログラム中に温度補償制御部やフェールセーフ部を追加しなければならない。また、温度センサを用いた場合、センサが故障すると温度補償効果が得られなかったり、誤った温度情報により温度補償制御が行われることで、変速制御精度が、温度補償無しの場合の変速制御精度より低下してしまう場合もあるという問題がある。
【０００８】
そこで、無段変速機内の部品の熱膨張差による変速制御弁の調圧位置からの移動で起こる変速比のズレを補正するために温度補償部材をフィードバック系の構成要素に組み込むことが容易に想定できる。
【０００９】
しかし、フィードバックリンクで温度補償部材を揺動軸からプリセスカムとの接触点までの間に組み込むと、下記の問題が発生する。
【００１０】
フィードバックリンクは、トラニオンの軸方向移動量を変速制御弁の移動量に変換して変速を収束させるためフィードバックしているが、これはプリセスカムの斜面も同様のフィードバックゲインになるように設計している。
これに対し、フィードバックリンクの揺動軸からプリセスカムとの接触点までの間に温度補償部材を設置すると、極低温始動時、定常運転での熱膨張差によるコントロールバルブボディとプリセスカムの距離の変化を温度補償部材の縮小で補正することはできる。
しかし、この縮小によりトラニオンの軸方向移動量が常温時よりも少なく変速制御弁移動量に変換される。つまり、フィードバックゲインが変化するため、プリセスカムの斜面によるフィードバックゲインと合わなくなり、変速フィードバック系が成立しなくなるおそれがある。
【００１１】
また、油圧シリンダ部に温度補償部材を設けると、比較的暖まりやすい油の温度に影響されやすくなるため、極低温始動時からある程度の時間が経過してユニット内が不均一に暖機された場合、温度補償部材の温度補償量が変速フィードバック系での必要温度補償量よりも小さくなり、変速制御弁の調圧位置に達しないため、変速フィードバック系が成立しなくなるおそれがある。
【００１２】
これを克服するため、変速機の構成要素を全て同じ材料を使うという解決手段があり、この解決手段によると、温度補償の原因そのものが取り除かれ、確実に問題を解決できるが、例えば、全ての構成要素を鉄にすると重量増を招くし、また、全ての構成要素をアルミ合金とすると強度や耐久性の面で劣る。
【００１３】
本発明は、上記問題点に着目してなされたもので、その目的とするところは、無段変速機の強度と軽量化の両立を図りながら、パワーローラ支持部材から変速制御弁へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができるトロイダル型無段変速機の変速制御装置を提供することにある。
【００１４】
【課題を解決するための手段】
上記目的を達成するため、請求項１記載の発明では、相互に対向する面をトロイド曲面に形成すると共に、同軸上に対向配置された入力ディスク及び出力ディスクと、
前記入出力ディスクの対向面に挟持されて傾転自在なパワーローラと、
前記パワーローラを回転自在に支持すると共に、傾転軸まわりに回動可能、かつ、傾転軸方向に変位可能なパワーローラ支持部材と、
前記パワーローラ支持部材を傾転軸方向へ駆動する油圧シリンダと、
バルブボディに収装され、前記油圧シリンダのシリンダ室への油圧を制御する変速制御弁と、
前記変速制御弁を駆動する変速アクチュエータと、
前記パワーローラ支持部材に設けられたプリセスカムに応動してパワーローラ支持部材の回動運動を往復運動に変換するフィードバックリンクと、
前記フィードバックリンクと、前記変速制御弁とを互いに連結し、実変速比が目標変速比になるように、パワーローラ支持部材の回動量を前記変速制御弁に伝えて変速比フィードバック制御を行う変速リンクとを備え、
変速機の構成要素のうち、変速機ケースや前記バルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されたトロイダル型無段変速機の変速制御装置において、
前記変速制御弁は、変速アクチュエータの駆動量を伝える第１の部材と、パワーローラ支持部材の回動量を伝える第２の部材を有し、
前記変速制御弁の第１の部材もしくは第２の部材と、変速制御弁と前記変速リンクとの連結部材との間に、前記固定要素と前記変速機構要素の熱膨張係数の違いにより生じる変速制御弁のストロークを吸収する温度補償部材を設けたことを特徴とする。
【００１５】
請求項２記載の発明では、請求項１に記載のトロイダル型無段変速機の変速制御装置において、
前記変速制御弁の第１の部材と第２の部材を兼用するスプールには、その一端面に段付き円筒部と段付きネジ部とが一体に連設され、
前記連結部材には、前記段付きネジ部が挿通される挿通穴が形成され、
前記温度補償部材は、スプール端面と前記段付き円筒部との段差面と連結部材の一端面との間にスプール軸と同軸上に介装され、かつ、前記段付きネジ部に螺合されるナットと連結部材の他端面との間に弾性体を介装させることで、収縮方向に予圧を設定した部材であることを特徴とする。
【００１６】
請求項３記載の発明では、請求項１または請求項２に記載のトロイダル型無段変速機の変速制御装置において、
前記温度補償部材は、互いに摺動可能に嵌合され、一体的に伸縮する保持器及び従動部材を有し、雰囲気温度が常温から低温になることで保持器と従動部材による軸長を短くする部材であることを特徴とする。
【００１７】
請求項４記載の発明では、相互に対向する面をトロイド曲面に形成すると共に、同軸上に対向配置された入力ディスク及び出力ディスクと、
前記入出力ディスクの対向面に挟持されて傾転自在なパワーローラと、
前記パワーローラを回転自在に支持すると共に、傾転軸まわりに回動可能、かつ、傾転軸方向に変位可能なパワーローラ支持部材と、
前記パワーローラ支持部材を傾転軸方向へ駆動する油圧シリンダと、
バルブボディに収装され、前記油圧シリンダのシリンダ室への油圧を制御する変速制御弁と、
前記変速制御弁を駆動する変速アクチュエータと、
前記パワーローラ支持部材に設けられたプリセスカムに応動してパワーローラ支持部材の回動運動を往復運動に変換するフィードバックリンクと、
前記フィードバックリンクと、前記変速制御弁とを互いに連結し、実変速比が目標変速比になるように、パワーローラ支持部材の回動量を前記変速制御弁に伝えて変速比フィードバック制御を行う変速リンクとを備え、
変速機の構成要素のうち、変速機ケースや前記バルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されたトロイダル型無段変速機の変速制御装置において、
前記パワーローラ支持部材と前記プリセスカムとの間であって、前記油圧シリンダ部を除く軸部に、前記固定要素と前記変速機構要素の熱膨張係数の違いにより生じる変速制御弁のストロークを吸収する温度補償部材を設けたことを特徴とする。
【００１８】
請求項５記載の発明では、相互に対向する面をトロイド曲面に形成すると共に、同軸上に対向配置された入力ディスク及び出力ディスクと、
前記入出力ディスクの対向面に挟持されて傾転自在なパワーローラと、
前記パワーローラを回転自在に支持すると共に、傾転軸まわりに回動可能、かつ、傾転軸方向に変位可能なパワーローラ支持部材と、
前記パワーローラ支持部材を傾転軸方向へ駆動する油圧シリンダと、
バルブボディに収装され、前記油圧シリンダのシリンダ室への油圧を制御する変速制御弁と、
前記変速制御弁を駆動する変速アクチュエータと、
前記パワーローラ支持部材に設けられたプリセスカムに応動してパワーローラ支持部材の回動運動を往復運動に変換するフィードバックリンクと、
前記フィードバックリンクと、前記変速アクチュエータと、前記変速制御弁とを互いに連結し、実変速比が目標変速比になるように、パワーローラ支持部材の回動量を前記変速制御弁に伝えて変速比フィードバック制御を行う変速リンクとを備え、
変速機の構成要素のうち、変速機ケースや前記バルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されたトロイダル型無段変速機の変速制御装置において、
前記変速アクチュエータと、該変速アクチュエータと前記変速リンクとの連結部材との間に、前記固定要素と前記変速機構要素の熱膨張係数の違いにより生じる変速制御弁のストロークを吸収する温度補償部材を設けたことを特徴とする。
【００１９】
請求項６記載の発明では、請求項５に記載のトロイダル型無段変速機の変速制御装置において、
前記温度補償部材は、互いに摺動可能に嵌合され、一体的に伸縮する保持器及び従動部材を有し、雰囲気温度が常温から低温になることで保持器と従動部材による軸長を長くする部材であることを特徴とする。
【００２０】
請求項７記載の発明では、相互に対向する面をトロイド曲面に形成すると共に、同軸上に対向配置された入力ディスク及び出力ディスクと、
前記入出力ディスクの対向面に挟持されて傾転自在なパワーローラと、
前記パワーローラを回転自在に支持すると共に、傾転軸まわりに回動可能、かつ、傾転軸方向に変位可能なパワーローラ支持部材と、
前記パワーローラ支持部材を傾転軸方向へ駆動する油圧シリンダと、
バルブボディに収装され、前記油圧シリンダのシリンダ室への油圧を制御する変速制御弁と、
前記変速制御弁を駆動する変速アクチュエータと、
前記パワーローラ支持部材に設けられたプリセスカムに応動してパワーローラ支持部材の回動運動を往復運動に変換するフィードバックリンクと、
前記フィードバックリンクと、前記変速制御弁とを互いに連結し、実変速比が目標変速比になるように、パワーローラ支持部材の回動量を前記変速制御弁に伝えて変速比フィードバック制御を行う変速リンクとを備え、
変速機の構成要素のうち、変速機ケースや前記バルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されたトロイダル型無段変速機の変速制御装置において、
前記フィードバックリンクの揺動軸と、該フィードバックリンクと前記変速リンクまたは前記変速制御弁との当接部との間に、前記固定要素と前記変速機構要素の熱膨張係数の違いにより生じる変速制御弁のストロークを吸収する温度補償部材を設けたことを特徴とする。
【００２１】
【発明の作用および効果】
請求項１記載の発明にあっては、変速時、目標変速比（或いは、目標入力回転数）が得られる指令が変速アクチュエータに出力され、この変速アクチュエータの駆動量が、変速リンクを介して変速制御弁に伝えられる。これにより油圧シリンダのシリンダ室に変速制御弁から油圧が供給され、油圧シリンダのピストンがストロークすることでパワーローラ支持部材が傾転軸方向に変位する。このパワーローラ支持部材の変位によりパワーローラは入出力ディスクの中心軸位置からオフセットし、このオフセットによりパワーローラと入出力ディスクとの接触点において傾転力が作用し、パワーローラは傾転軸を中心とする傾転角が変化する。この傾転運動は、パワーローラ支持部材に設けられたプリセスカムと、該プリセスカムに一端部が連結されたフィードバックリンクと、該フィードバックリンクの他端部が連結された変速リンクを介して変速制御弁に伝えられ、変速制御弁が釣り合う位置で油圧シリンダのピストンを中立位置に戻すことで、パワーローラとディスクの中心軸が一致し、そのときの傾転角位置（変速比）にパワーローラが設定される。つまり、実変速比（パワーローラ支持部材の回動量）が目標変速比（変速アクチュエータの駆動量）になるよう変速比フィードバック制御される。
【００２２】
この変速制御動作において、変速機の構成要素のうち、変速機ケースやバルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりフィードバックリンクがストロークし、このストロークにより変速制御弁の第１の部材もしくは第２の部材がストロークする。
【００２３】
しかし、変速制御弁の第１の部材もしくは第２の部材と、変速制御弁と変速リンクとの連結部材との間に温度補償部材を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じる変速制御弁のストロークが吸収される。しかも、温度補償部材が設けられる位置は、変速制御弁と変速リンクとの連結部材との間の位置であるため、温度補償部材が伸縮してもパワーローラ支持部材から変速制御弁へのフィードバックゲインを変化させることがない。
【００２４】
よって、無段変速機の強度と軽量化の両立を図りながら、パワーローラ支持部材から変速制御弁へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００２５】
請求項２記載の発明にあっては、温度補償部材が、変速制御弁のスプール端面と段付き円筒部との段差面と、連結部材の一端面との間にスプール軸と同軸上に介装され、かつ、段付きネジ部に螺合されるナットと連結部材の他端面との間に弾性体を介装させることで、収縮方向に予圧が設定される。
【００２６】
よって、温度補償部材には常に収縮方向に予圧が設定されているため、変速制御弁のスプールと変速リンクとの連結位置を、温度補償部材の伸縮量の分だけ確実に変化させることができるし、また、温度補償部材の軸心ズレと軸方向のクリアランスを容易に管理することができる。
【００２７】
請求項３記載の発明にあっては、温度補償部材が、互いに摺動可能に嵌合され、一体的に伸縮する保持器及び従動部材を有し、雰囲気温度が常温から低温になることで保持器と従動部材による軸長を短くする部材とされる。
【００２８】
よって、温度補償部材が、雰囲気温度が常温から低温になることで軸長を短くする部材とされているため、変速リンクにより連結される変速フィードバック機構のいずれかの部位で、軸方向長さを短くする方向が必要補償方向であるレイアウトの場合、温度補償部材として適用することができる。
【００２９】
請求項４記載の発明にあっては、上記変速制御動作において、変速機の構成要素のうち、変速機ケースやバルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりパワーローラ支持部材が伸縮し、この伸縮によりプリセスカムとフィードバックリンクと変速リンクを介し、変速制御弁がストロークする。
【００３０】
しかし、パワーローラ支持部材とプリセスカムとの間であって、油圧シリンダ部を除く軸部に温度補償部材を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じるパワーローラ支持部材の伸縮が吸収される。しかも、温度補償部材が設けられる位置は、油圧シリンダ部を除く軸部であるため、温度補償部材が伸縮してもパワーローラ支持部材から変速制御弁へのフィードバックゲインを変化させることがない。
【００３１】
よって、無段変速機の強度と軽量化の両立を図りながら、パワーローラ支持部材から変速制御弁へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００３２】
請求項５記載の発明にあっては、上記変速制御動作において、変速機の構成要素のうち、変速機ケースやバルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いにより変速アクチュエータが伸縮し、この伸縮により変速リンクを介して変速制御弁がストロークする。
【００３３】
しかし、変速アクチュエータと、該変速アクチュエータを固定するアクチュエータ位置規制部材との間に温度補償部材を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じる変速アクチュエータの伸縮が吸収される。しかも、温度補償部材が設けられる位置は、変速アクチュエータと、該変速アクチュエータを固定するアクチュエータ位置規制部材との間であるため、温度補償部材が伸縮してもパワーローラ支持部材から変速制御弁へのフィードバックゲインを変化させることがない。
【００３４】
よって、無段変速機の強度と軽量化の両立を図りながら、パワーローラ支持部材から変速制御弁へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００３５】
請求項６記載の発明にあっては、温度補償部材が、互いに摺動可能に嵌合され、一体的に伸縮する保持器及び従動部材を有し、雰囲気温度が常温から低温になることで保持器と従動部材による軸長を長くする部材とされる。
【００３６】
よって、温度補償部材が、雰囲気温度が常温から低温になることで軸長を長くする部材とされているため、変速リンクにより連結される変速フィードバック機構のいずれかの部位で、軸方向長さを長くする方向が必要補償方向であるレイアウトの場合、温度補償部材として適用することができる。
【００３７】
請求項７記載の発明にあっては、上記変速制御動作において、変速機の構成要素のうち、変速機ケースやバルブボディの固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なる素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりフィードバックリンクが伸縮し、この伸縮により変速制御弁のスプールもしくはスリーブがストロークする。
【００３８】
しかし、フィードバックリンクの揺動軸と、該フィードバックリンクと変速リンクまたは変速制御弁との当接部との間に温度補償部材を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じるフィードバックリンクの伸縮が吸収される。しかも、温度補償部材が設けられる位置は、フィードバックリンクの揺動軸より変速リンク側または変速制御弁側であるため、温度補償部材が伸縮してもパワーローラ支持部材から変速制御弁へのフィードバックゲインを変化させることがない。
【００３９】
よって、無段変速機の強度と軽量化の両立を図りながら、パワーローラ支持部材から変速制御弁へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００４０】
【発明の実施の形態】
以下、本発明の実施の形態におけるトロイダル型無段変速機の変速制御装置を、実施例１〜実施例４に基づいて説明する。
【００４１】
（実施例１）
実施例１は請求項１，２，３に記載の発明に対応するトロイダル型無段変速機の変速制御装置である。
【００４２】
図１は実施例１におけるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示す斜視図であり、図２は実施例１におけるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示すレイアウト図であり、１は入力ディスク、２は出力ディスク、３はパワーローラ、４はトラニオン（パワーローラ支持部材）、５は油圧シリンダ、６は変速制御弁、７はバルブボディ、８は変速アクチュエータ、９はプリセスカム、１０はフィードバックリンク、１１は変速リンク、１２は温度補償部材、１３は連結部材である。
【００４３】
前記入力ディスク１及び出力ディスク２は、図２に示すように、相互に対向する面がトロイド曲面に形成されると共に、同軸上に対向配置されている。
【００４４】
前記パワーローラ３，３は、図２に示すように、入出力ディスク１，２の対向面に、傾転軸Ｘを中心として傾転自在に挟持されている。
【００４５】
前記トラニオン４は、図１に示すように、前記パワーローラ３を回転自在に支持すると共に、傾転軸Ｘまわりに回動可能、かつ、傾転軸Ｘ方向に変位可能である。
【００４６】
前記油圧シリンダ５は、図１に示すように、トラニオン４の軸部の途中位置に設けられ、トラニオン４を傾転軸Ｘ方向へ駆動する部材で、トラニオン４に固定されるピストン５ａと、該ピストン５ａの上下面の位置に形成されるシリンダ室５ｂ，５ｃを有する。
【００４７】
前記変速制御弁６は、図１及び図２に示すように、バルブボディ７に収装され、油圧シリンダ５のシリンダ室５ｂ，５ｃへの油圧を制御する弁で、スプール６ａ及びスリーブ６ｂを有している。ここで、スプール６ａは、請求項１の第１の部材と第２の部材とを兼用している。
【００４８】
前記変速アクチュエータ８は、図１及び図２に示すように、バルブボディ７に固定され、変速指令に従ってアクチュエータロッド８ａが進退動作するアクチュエータで、前記変速リンク１１を介して連結されている前記変速制御弁６のスプール６ａを駆動する。
【００４９】
前記フィードバックリンク１０は、図１及び図２に示すように、トラニオン４の下部に設けられたプリセスカム９に応動してトラニオン４の傾転軸Ｘまわりの回動運動を往復運動に変換するＬ形リンクで、揺動軸１０ａと、該揺動軸１０ａよりトラニオン４側のカム倣い腕部１０ｂと、揺動軸１０ａより変速リンク１１側の連結腕部１０ｃとを有する。
【００５０】
前記変速リンク１１は、図１及び図２に示すように、前記フィードバックリンク１０の連結腕部１０ｃと、前記変速アクチュエータ８のアクチュエータロッド８ａと、前記変速制御弁６の連結軸部６ｃとを互いに連結し、実変速比が目標変速比になるように、トラニオン４の回動量を前記変速制御弁６のスプール６ａに伝えて変速比フィードバック制御を行う。この変速フィードバック機構のレイアウトは、図２に示すように、中央位置に変速制御弁６を配置し、その両側位置にフィードバックリンク１０と変速アクチュエータ８が配置されている。なお、変速リンク１１とフィードバックリンク１０の連結部をＣＬとし、変速リンク１１と変速アクチュエータ８のの連結部をＣＡとし、変速リンク１１と変速制御弁６の連結部をＣＶとする。
【００５１】
前記トロイダル型無段変速機の構成要素のうち、図外の変速機ケースや前記バルブボディ７の固定要素はアルミ合金を素材とし、変速時に動作する変速機構要素（トラニオン４、ピストン５ａ、プリセスカム９、フィードバックリンク１０、スプール６ａ、スリーブ６ｂ等）は、アルミ合金とは熱膨張係数の異なる鉄を素材として製造されている。
【００５２】
前記変速制御弁６のスプール６ａと、該スプール６ａと前記変速リンク１１との連結部材１３との間には、図１に示すように、前記固定要素と前記変速機構要素の熱膨張係数の違いにより生じる変速制御弁６のスプール６ａのストロークを吸収する温度補償部材１２が設けられている。
【００５３】
次に、図３により前記温度補償部材１２が設けられている連結部ＣＶの構成について説明する。
【００５４】
前記変速制御弁６のスプール６ａには、その一端面に連結軸部６ｃを構成する段付き円筒部６ｃ’と段付きネジ部６ｃ”とが一体に連設され、前記連結部材１３には、前記段付きネジ部６ｃ”が挿通される挿通穴１３ａが形成され、前記温度補償部材１２は、スプール端面と前記段付き円筒部６ｃ’との段差面と、連結部材１３の一端面との間にスプール軸と同軸上に介装され、かつ、前記段付きネジ部６ｃ”に螺合されるナット１４と連結部材１３の他端面との間に皿バネ等による弾性体１５を介装させることで、温度補償部材１２は、収縮方向に予圧が設定されている。なお、１６はナット１４を固定するためのピンである。
【００５５】
次に、図４及び図５により温度補償部材１２の構成について説明する。
【００５６】
前記温度補償部材１２は、複数のシリンダ穴２０ａを有する座金２０が嵌合されるシリンダ溝２１ａが形成された環状保持器２１と、該環状保持器２１とは一体的に摺動可能で複数のシリンダ穴２０ａに摺動可能な複数のピストン２２ａが形成された環状従動部材２２と、前記ピストン２２ａとシリンダ穴２０ａとのシール嵌合によって塞がれるシリンダ室２３に充填され、雰囲気温度が常温から低温になることで軸長を短くする充填材２４とを有して構成されている。つまり、充填材２４として、温度により体積変化する液体や半凝固体等が用いられ、充填材２４の温度変化による体積変化で変位量を稼ぐ構造となっている。なお、図４において、２５は座金２０をシリンダ溝２１ａの途中位置に止める止め輪、２６はピストン２２ａのシール部である。
【００５７】
次に、作用を説明する。
【００５８】
［変速制御作用］
変速時、目標変速比（或いは、目標入力回転数）が得られる指令が変速アクチュエータ８に出力され、この変速アクチュエータ８の駆動量が、変速リンク１１を介して変速制御弁６のスプール６ａに伝えられる。これにより油圧シリンダ５の一方のシリンダ室５ｂ又は５ｃに変速制御弁６から油圧が供給され、他方のシリンダ室５ｃ又は５ｂから油が抜かれ、差圧により油圧シリンダ５のピストン５ａがストロークすることでトラニオン４が傾転軸Ｘ方向に変位する。
【００５９】
このトラニオン４の変位によりパワーローラ３は入出力ディスク１，２の中心軸位置からオフセットし、このオフセットによりパワーローラ３と入出力ディスク１，２との接触点において傾転力が作用し、パワーローラ３は傾転軸Ｘを中心とする傾転角が変化する。
【００６０】
この傾転運動は、トラニオン４に設けられたプリセスカム９と、該プリセスカム９に一端部が連結されたフィードバックリンク１０と、該フィードバックリンク１０の他端部が連結された変速リンク１１を介して変速制御弁６のスプール６ａに伝えられ、変速制御弁６のスプール６ａが釣り合う位置で油圧シリンダ５のピストン５ａを中立位置に戻すことで、パワーローラ３の中心軸と両ディスク１，２の中心軸が一致し、そのときの傾転角位置（変速比）にパワーローラ３が設定される。
【００６１】
つまり、実変速比（トラニオン４の回動量）が目標変速比（変速アクチュエータ８の駆動量）になるよう変速比フィードバック制御される。
【００６２】
［熱膨張による変速比ズレ防止作用］
上記変速制御動作において、変速機の構成要素のうち、図外の変速機ケースやバルブボディ７の固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なるアルミ合金素材と鉄素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりフィードバックリンク１０がストロークし、このストロークにより変速制御弁６のスプール６ａがストロークする。
【００６３】
しかし、変速制御弁６のスプール６ａと、該スプール６ａと変速リンク１１との連結部材１３との間に温度補償部材１２を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じる変速制御弁６のスプール６ａのストロークが吸収される。例えば、図２に示すように、常温→低温で変速リンク１１が矢印で示す収縮方向に移動する場合、スプール６ａと連結部材１３との間に設けられている温度補償部材１２は、この収縮方向の移動に追従して収縮し、スプール６ａのストロークとなる直前の段階でスプールストロークが吸収される。
【００６４】
しかも、温度補償部材１２が設けられる位置は、変速制御弁６のスプール６ａと連結部材１３との間の位置であるため、温度補償部材１２が伸縮してもトラニオン４から変速制御弁６へのフィードバックゲインを変化させることがない。
【００６５】
さらに、温度補償部材１２には、弾性体１５により予圧が付与されているため、軸の芯ズレと軸方向のクリアランスの管理を容易に行うことができる。例えば、無段変速機内の温度が低下した場合に、温度補償部材１２が収縮するのに倣うように連結部材１３が移動し、温度補償部材１２とスプール６ａとの間や温度補償部材１２と連結部材１３と間に軸方向クリアランスが形成されることがない。
【００６６】
次に、効果を説明する。
【００６７】
(1) 変速制御弁６のスプール６ａと、該スプール６ａと変速リンク１１との連結部材１３との間に温度補償部材１２を設けたため、固定要素と変速機構要素を異なる素材とすることによる無段変速機の強度と軽量化の両立を図りながら、トラニオン４から変速制御弁６へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００６８】
(2) 温度補償部材１２には、弾性体１５により予圧が付与されているため、変速制御弁６のスプール６ａと変速リンク１１との連結位置ＣＶを、温度補償部材１２の伸縮量の分だけ確実に変化させることができるし、また、温度補償部材１２の軸心ズレと軸方向のクリアランスを容易に管理することができる。
【００６９】
(3) 温度補償部材１２が、雰囲気温度が常温から低温になることで軸長を短くする部材とされているため、変速リンク１１により連結される変速フィードバック機構のいずれかの部位で、軸方向長さを伸ばす方向が必要補償方向であるレイアウトの場合、温度補償部材として適用することができる。
【００７０】
（実施例２）
実施例２は請求項４に記載の発明に対応するトロイダル型無段変速機の変速制御装置である。
【００７１】
この実施例２は、実施例１で示した温度補償部材１２を、トラニオン４の外軸部４ｂとプリセスカム９との間であって、油圧シリンダ５のピストン部を除く軸部に設けた例である。
【００７２】
すなわち、図６に示すように、トラニオン４が、パワーローラ支持部４ａと外軸部４ｂと内軸部４ｃとで構成され、外軸部４ｂとプリセスカム９との間に温度補償部材１２が設定されている。ここで、実施例１と同様に、温度補償部材１２の伸縮に追従してプリセスカム９を移動させるため、内軸部４ｃの端部にナット３０が螺合されていると共に、このナット３０とプリセスカム９との間に、温度補償部材１２に予圧を付与する弾性体３１が介装されている。また、トラニオン４の内軸部４ｃとプリセスカム９とを一体で回動させるために、両者４ｃ，９の間には、ボールスプライン３２が配設してある。なお、図６において、３３はボールスプライン３２のボールの脱落を防止する止め輪、３４はナット３０を固定するためのピン、３５は内軸部４ｃに油路を確保するための栓である。
【００７３】
ここで、温度補償部材１２を、油圧シリンダ５のピストン部を除く軸部位置に設定した理由は、トラニオン４から変速制御弁６へのフィードバックゲインを変えないためと、温度変化した場合、温度補償部材１２の伸縮によりピストン５ａとシリンダ室５ｂ，５ｃとの干渉を防止するためである。尚、他の構成は、実施例１と同様であるので、図示並びに説明を省略する。
【００７４】
次に、作用を説明する。
【００７５】
上記実施例１の作用で述べた変速制御動作において、変速機の構成要素のうち、図外の変速機ケースやバルブボディ７の固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なるアルミ合金素材と鉄素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりトラニオン４が伸縮し、このトラニオン４の伸縮に伴って、プリセスカム９を介して動作するフィードバックリンク１０及び変速リンク１１がストロークし、この変速リンク１１のストロークにより変速制御弁６のスプール６ａがストロークする。
【００７６】
しかし、トラニオン４の外軸部４ｂとプリセスカム９との間であって、油圧シリンダ５のピストン部を除く軸部に温度補償部材１２を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じるトラニオン４の伸縮が温度補償部材１２により吸収され、結果的に、変速制御弁６のスプール６ａのストロークが吸収される。
【００７７】
しかも、温度補償部材１２が設けられる位置は、油圧シリンダ５部を除く軸部であるため、温度補償部材１２が伸縮してもトラニオン４から変速制御弁６へのフィードバックゲインを変化させることがない。
【００７８】
よって、この実施例２にあっては、温度補償部材１２を、トラニオン４の外軸部４ｂとプリセスカム９との間であって、油圧シリンダ５のピストン部を除く軸部に設けたため、固定要素と変速機構要素を異なる素材とすることによる無段変速機の強度と軽量化の両立を図りながら、トラニオン４から変速制御弁６へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００７９】
（実施例３）
実施例３は請求項５，６に記載の発明に対応するトロイダル型無段変速機の変速制御装置である。
【００８０】
この実施例３は、図８に示す温度補償部材４０を、変速アクチュエータ８と、該変速アクチュエータ８を固定するアクチュエータ位置規制部材４１との間に設けた例である。
【００８１】
すなわち、図７に示すように、バルブボディ７にアクチュエータ位置規制部材４１を固定し、アクチュエータ位置規制部材４１と変速アクチュエータ８との間に変速アクチュエータ８を軸方向に移動可能に支持するボールスプライン４２を設け、アクチュエータ位置規制部材４１の内側端面と、変速アクチュエータ８の連結側端面との間に温度補償部材４０が設定されている。なお、図７の４３はボールスプライン４２のボールの脱落を防止する止め輪である。
【００８２】
図８に温度補償部材４０を示している。この温度補償部材４０は、実施例１，２とは異なり、常温→低温への温度変化により軸長が伸びる部材である。すなわち、温度補償部材４０は、シリンダ穴４４ａが形成された保持器４４と、該保持器４４とは一体的に摺動可能で、ピストン部４５ａが形成された従動部材４５と、シリンダ穴４４ａと従動部材４５によって画成されるシリンダ室のうち、ピストン部４５ａの延長部以外の空間と第２充填材４７の上下位置に充填され、常温→低温で熱収縮する第１充填材４６と、第１充填材４６に取り囲まれて充填され、常温→低温でほとんど熱収縮しない第２充填材４７とにより構成され、常温→低温で第１充填材４６を熱収縮させ、中の第２充填材４７の有効体積を少なくして押し出すことで、常温→低温で軸長が伸びる。なお、図８は軸形状の温度補償部材４０を示したが、図４及び図５に示すように、ワッシャ形状の温度補償部材４０とすることもでき、ワッシャ形状の温度補償部材４０を図７の変速アクチュエータ８に採用している。また、他の構成は、実施例１と同様であるので、図示並びに説明を省略する。
【００８３】
次に、作用を説明する。
【００８４】
上記実施例１の作用で述べた変速制御動作において、変速機の構成要素のうち、図外の変速機ケースやバルブボディ７の固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なるアルミ合金素材と鉄素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いにより変速アクチュエータ８のアクチュエータロッド８ａが伸縮し、このアクチュエータロッド８ａの伸縮に伴って、変速リンク１１により連結されている変速制御弁６のスプール６ａがストロークする。
【００８５】
しかし、変速アクチュエータ８と、該変速アクチュエータ８を固定するアクチュエータ位置規制部材４１との間に温度補償部材４０を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じる変速アクチュエータ８のアクチュエータロッド８ａの伸縮が吸収され、変速リンク１１により連結されている変速制御弁６のスプール６ａのストロークが吸収される。
【００８６】
しかも、温度補償部材４０が設けられる位置は、変速アクチュエータ８と、該変速アクチュエータ８を固定するアクチュエータ位置規制部材４１との間であるため、温度補償部材４０が伸縮してもトラニオン４から変速制御弁６へのフィードバックゲインを変化させることがない。
【００８７】
よって、実施例３にあっては、変速アクチュエータ８と、該変速アクチュエータ８を固定するアクチュエータ位置規制部材４１との間に温度補償部材４０を設けたため、固定要素と変速機構要素を異なる素材とすることによる無段変速機の強度と軽量化の両立を図りながら、トラニオン４から変速制御弁６へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００８８】
さらに、温度補償部材４０が、雰囲気温度が常温から低温になることで軸長を長くする部材とされているため、変速リンク１１により連結される変速フィードバック機構のいずれかの部位で、軸方向長さを伸ばす方向が必要補償方向であるレイアウトの場合、温度補償部材として適用することができる。
【００８９】
（実施例４）
実施例４は請求項７に記載の発明に対応するトロイダル型無段変速機の変速制御装置である。
【００９０】
この実施例４は、実施例１で示した温度補償部材１２を、フィードバックリンク１０の揺動軸１０ａと、該フィードバックリンク１０と変速リンク１１との当接部１０ｄとの間に設けた例である。
【００９１】
すなわち、図９に示すように、フィードバックリンク１０の連結腕部１０ｃの変速リンク１１側を切断し、連結腕部１０ｃに端部にネジが切られたピン５０を固定し、このピン５０を挿通してボール状の当接部１０ｄを設け、この当接部１０ｄと連結腕部１０ｃの切断端面との間に温度補償部材１２を介装させている。なお、ピン５０の端部にはナット５１が螺合され、ナット５１と当接部１０ｄとの間に介装させた弾性体５２により、実施例１，２と同様に、温度補償部材１２に対し予圧を付与している。なお、他の構成は、実施例１と同様であるので、図示並びに説明を省略する。
【００９２】
次に、作用を説明する。
【００９３】
上記実施例１の作用で述べた変速制御動作において、変速機の構成要素のうち、図外の変速機ケースやバルブボディ７の固定要素と、変速時に動作する変速機構要素とが熱膨張係数の異なるアルミ合金素材と鉄素材により製造されていることで、例えば、エンジン始動時と走行時とで温度が変化する場合、固定要素と変速機構要素の熱膨張係数の違いによりフィードバックリンク１０が伸縮し、この伸縮により変速リンク１１を介して変速制御弁６のスプール６ａがストロークする。
【００９４】
しかし、フィードバックリンク１０の揺動軸１０ａと、該フィードバックリンク１０と変速リンク１１との当接部１０ｄとの間に温度補償部材１２を設けているため、固定要素と変速機構要素の熱膨張係数の違いにより生じるフィードバックリンク１０の伸縮が吸収される。
【００９５】
しかも、温度補償部材１２が設けられる位置は、フィードバックリンク１０の揺動軸１０ａより変速リンク１１側であるため、温度補償部材１２が伸縮してもトラニオン４から変速制御弁６へのフィードバックゲインを変化させることがない。
【００９６】
よって、実施例３にあっては、温度補償部材１２を、フィードバックリンク１０の揺動軸１０ａと、該フィードバックリンク１０と変速リンク１１との当接部１０ｄとの間に設けたため、固定要素と変速機構要素を異なる素材とすることによる無段変速機の強度と軽量化の両立を図りながら、トラニオン４から変速制御弁６へのフィードバックゲインを変えることなく、変速機内部品の熱膨張差による変速比のズレを補正することができる。
【００９７】
（他の実施例）
実施例１〜実施例４では、変速フィードバック機構として、図２の変速制御弁６が中央に配置されたレイアウトを持つ機構を示したが、これ以外に、例えば、図１０に示すように、変速制御弁６が端部に配置され、変速制御弁６に近い位置にフィードバックリンク１０が配置され、変速制御弁６から遠い位置に変速アクチュエータ８が配置されたレイアウトや、図１１に示すように、変速制御弁６が端部に配置され、変速制御弁６に近い位置に変速アクチュエータ８が配置され、変速制御弁６から遠い位置にフィードバックリンク１０が配置されたレイアウトのものにも適用することができる。
但し、レイアウトを異ならせた場合、必要補償方向が異なり、例えば、図１０に示すレイアウトの場合には、実施例１及び実施例３は共に温度補償部材１２を用いることになり、図１１に示すレイアウトの場合には、実施例１には温度補償部材４０を用い、実施例３の場合は温度補償部材１２を用いる。
【００９８】
また、実施例１〜実施例４では、温度補償部材１２，４０として図４，５や図８に示すものを示したが、具体的な構成はこれに限られず、温度変化により軸長が変化する部材であれば、他の様々な構成のものを適用することもできる。
【００９９】
さらに、実施例１〜実施例４では、フィードバックリンク１０と変速制御弁６と変速アクチュエータ８の３つの構成要素を互いに連結する変速リンク１１の例を示したが、フィードバックリンク１０と変速制御弁６のスプール６ａもしくはスリーブ６ｂとが直接接触もしくは連結され、この共通連結点と変速アクチュエータ８とを連結する変速リンク１１であっても良いし、また、フィードバックリンク１０と変速制御弁６の２つの構成要素を互いに連結する変速リンクとし、変速アクチュエータ８は変速リンクを介在させることなく変速制御弁６を駆動する構成としても良い。
【０１００】
加えて、実施例１〜実施例４では、変速制御弁６のスプール６ａが変速アクチュエータの駆動量を伝える第１の部材と、パワーローラ支持部材の回動量を伝える第２の部材を兼用する例を示したが、第１の部材がスプールで第２部材がスリーブ、あるいは、第１の部材がスリーブで第２部材がスプールというように、２つの部材によりそれぞれの機能をなす変速制御弁であっても適用することができる。
【図面の簡単な説明】
【図１】実施例１におけるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示す斜視図である。
【図２】実施例１におけるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示すレイアウト図である。
【図３】実施例１におけるトロイダル型無段変速機の変速制御装置の温度補償部材取付部を示す断面図である。
【図４】実施例１において採用された温度補償部材を示す断面図である。
【図５】実施例１において採用された温度補償部材を構成する環状保持器、環状従動部材及び座金示す平面図である。
【図６】実施例２におけるトロイダル型無段変速機の変速制御装置の温度補償部材取付部を示す断面図である。
【図７】実施例３におけるトロイダル型無段変速機の変速制御装置の温度補償部材取付部を示す断面図である。
【図８】実施例３において採用された温度補償部材を示す断面図である。
【図９】実施例４におけるトロイダル型無段変速機の変速制御装置の温度補償部材取付部を示す断面図である。
【図１０】実施例１〜４とは異なるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示すレイアウト図である。
【図１１】実施例１〜４とも図１０とも異なるトロイダル型無段変速機の変速制御装置の変速フィードバック機構を示すレイアウト図である。
【図１２】従来のトロイダル型無段変速機の変速制御装置を示す図である。
【符号の説明】
１入力ディスク
２出力ディスク
３パワーローラ
４トラニオン（パワーローラ支持部材）
５油圧シリンダ
６変速制御弁
７バルブボディ
８変速アクチュエータ
９プリセスカム
１０フィードバックリンク
１１変速リンク
１２温度補償部材
１３連結部材[0001]
BACKGROUND OF THE INVENTION
The present invention is applied to a vehicle or the like, and belongs to the technical field of a transmission control device for a toroidal continuously variable transmission that can change a transmission gear ratio steplessly.
[0002]
[Prior art]
Conventionally, as a shift control device for a toroidal-type continuously variable transmission, for example, the one described in Japanese Patent Laid-Open No. 10-132066 is known.
[0003]
In this publication, as shown in FIG. 12, a power roller that forms a toroidal surface facing each other and is tilted by being sandwiched between opposing surfaces of an input / output disk that are coaxially disposed opposite to each other, A trunnion (power roller support member) that supports the power roller in a rotatable manner, can rotate around the tilt axis, and can be displaced in the tilt axis direction, and hydraulic pressure that drives the trunnion in the tilt axis direction A trunnion that is accommodated in a cylinder, a shift control valve that is housed in the valve body, controls the hydraulic pressure to the cylinder chamber of the hydraulic cylinder, a shift actuator that drives the shift control valve, and a recess cam provided in the trunnion A feedback link for converting the rotational motion of the motor to a reciprocating motion, and the feedback link, the speed change actuator, and the speed change control valve connected An outer speed change link, and the rotation amount of the trunnion (actual speed change ratio) and the drive amount of the speed change actuator (target speed change ratio) are transmitted to the speed change control valve via the speed change link so that the actual speed change ratio becomes the target speed change ratio. An apparatus that performs gear ratio feedback control is described.
[0004]
In such a toroidal-type continuously variable transmission, in order to reduce the weight while ensuring a predetermined strength, different materials are adopted for each component. For example, the transmission case and the valve body are made of an aluminum alloy (see FIG. 12). The other speed change mechanism elements (trunnion, piston, precess cam, feedback link, spool, sleeve, etc.) are made of iron (shown by hatching in FIG. 12).
[0005]
Since the fixed element and the speed change mechanism element are made of materials having different thermal expansion coefficients in this way, if the temperature of the hydraulic oil or each part changes from the temperature at the time of starting the continuously variable transmission according to the operating state, the power The trunnion that supports the roller expands or contracts in the Y-axis direction, and the transmission case made of aluminum alloy expands or contracts more than the trunnion due to the difference in thermal expansion coefficient between iron and aluminum. Therefore, when the center of the disk shaft and the center of the power roller are made to coincide, the trunnion length L from the recess cam to the center of the disk shaft changes relatively, and the displacement due to this thermal expansion is transferred to the feedback link via the copying mechanism. Entered. Incidentally, the coefficient of thermal expansion of aluminum is 23.0 × 10 ^-6 / ℃, whereas the thermal expansion coefficient of iron is 11.76 × 10 ^-6 / ° C.
[0006]
Therefore, a shift control device for a toroidal continuously variable transmission is described in which temperature compensation control is performed to change the control amount to the gear ratio changing means by the shift amount of the gear ratio due to thermal expansion.
[0007]
[Problems to be solved by the invention]
However, since the conventional shift control device for a toroidal type continuously variable transmission is configured to perform temperature compensation on the electronic control side of the shift control, a temperature detection means for detecting or estimating the temperature of the transmission is provided. In addition, a temperature compensation control unit and a fail safe unit must be added to the shift control program. Also, when a temperature sensor is used, if the sensor fails, the temperature compensation effect cannot be obtained, or the temperature compensation control is performed based on incorrect temperature information. There is a problem that it may be further lowered.
[0008]
Therefore, it is easily assumed that the temperature compensation member is incorporated in the feedback system component in order to correct the shift in the gear ratio caused by the movement of the shift control valve from the pressure adjustment position due to the difference in thermal expansion of the components in the continuously variable transmission. it can.
[0009]
However, if the temperature compensation member is incorporated between the swing shaft and the contact point with the recess cam by the feedback link, the following problem occurs.
[0010]
The feedback link feeds back in order to convert the trunnion movement in the axial direction into the movement of the shift control valve to converge the shift, but this is designed so that the slope of the precess cam also has the same feedback gain. .
On the other hand, if a temperature compensation member is installed between the feedback link swing shaft and the contact point with the process cam, the change in the distance between the control valve body and the process cam due to the difference in thermal expansion during steady-state operation during cryogenic start-up. Correction can be made by reducing the temperature compensation member.
However, due to this reduction, the movement amount of the trunnion in the axial direction is converted to the movement amount of the shift control valve less than that at normal temperature. That is, since the feedback gain changes, it does not match the feedback gain due to the slope of the recess cam, and the shift feedback system may not be established.
[0011]
Also, if a temperature compensation member is provided in the hydraulic cylinder, it will be easily affected by the temperature of oil that is relatively easy to warm, so when a certain amount of time has passed since the start of cryogenic temperature and the unit has been warmed up unevenly Since the temperature compensation amount of the temperature compensation member becomes smaller than the necessary temperature compensation amount in the shift feedback system and does not reach the pressure adjustment position of the shift control valve, the shift feedback system may not be established.
[0012]
In order to overcome this problem, there is a solution that uses the same material for all components of the transmission. According to this solution, the cause of temperature compensation itself is removed, and the problem can be solved reliably. If the component is made of iron, the weight is increased, and if all the components are made of an aluminum alloy, the strength and durability are inferior.
[0013]
The present invention has been made paying attention to the above problems, and its purpose is to provide a feedback gain from the power roller support member to the transmission control valve while achieving both strength and weight reduction of the continuously variable transmission. It is an object of the present invention to provide a shift control device for a toroidal continuously variable transmission that can correct a shift in a gear ratio due to a difference in thermal expansion of components in the transmission without changing the speed.
[0014]
[Means for Solving the Problems]
In order to achieve the above object, in the invention according to claim 1, an input disk and an output disk that are coaxially arranged to be opposed to each other are formed in a toroidal curved surface,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
The shift control valve includes a first member that transmits a drive amount of the shift actuator, and a second member that transmits a rotation amount of the power roller support member,
Speed change control caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element between the first member or the second member of the speed change control valve and the connection member of the speed change control valve and the speed change link A temperature compensation member that absorbs the stroke of the valve is provided.
[0015]
According to a second aspect of the present invention, in the shift control device for the toroidal type continuously variable transmission according to the first aspect,
The spool that serves as both the first member and the second member of the speed change control valve is integrally provided with a stepped cylindrical portion and a stepped screw portion at one end surface thereof,
The connecting member is formed with an insertion hole through which the stepped screw portion is inserted,
The temperature compensation member is interposed coaxially with the spool shaft between the step surface of the spool end surface and the stepped cylindrical portion and one end surface of the connecting member, and is screwed to the stepped screw portion. The elastic member is interposed between the nut and the other end surface of the connecting member, so that the preload is set in the contraction direction.
[0016]
According to a third aspect of the present invention, in the shift control device for the toroidal type continuously variable transmission according to the first or second aspect,
The temperature compensation member has a cage and a follower member that are slidably fitted to each other and integrally extend and contract, and the axial length of the cage and the follower member is shortened when the ambient temperature is lowered from room temperature. It is a member.
[0017]
In invention of Claim 4, while forming the mutually opposing surface in a toroidal curved surface, the input disk and output disk which are coaxially arranged oppositely,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A temperature between the power roller support member and the recess cam that absorbs a stroke of the speed change control valve caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element in the shaft part excluding the hydraulic cylinder part. A compensation member is provided.
[0018]
In invention of Claim 5, while forming the mutually opposing surface in a toroidal curved surface, the input disk and the output disk which are coaxially arranged oppositely,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
The feedback link, the speed change actuator, and the speed change control valve are connected to each other, and the rotation amount of the power roller support member is transmitted to the speed change control valve so that the actual speed change ratio becomes the target speed change ratio. A shift link for performing control,
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A temperature compensation member that absorbs a stroke of a shift control valve caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element is provided between the speed change actuator and a connecting member of the speed change actuator and the speed change link. It is characterized by that.
[0019]
According to a sixth aspect of the present invention, in the shift control device for the toroidal continuously variable transmission according to the fifth aspect,
The temperature compensation member includes a cage and a follower member that are slidably fitted to each other and integrally extend and contract, and the axial length of the cage and the follower member is increased when the ambient temperature is lowered from room temperature. It is a member.
[0020]
In the invention of claim 7, the surfaces facing each other are formed in a toroidal curved surface, and the input disk and the output disk are disposed so as to be coaxially opposed to each other;
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A speed change control valve generated by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element between a swing shaft of the feedback link and a contact portion between the feedback link and the speed change link or the speed change control valve. A temperature compensation member that absorbs the stroke is provided.
[0021]
Operation and effect of the invention
In the first aspect of the invention, at the time of shifting, a command for obtaining a target speed ratio (or target input rotation speed) is output to the speed change actuator, and the drive amount of the speed change actuator is changed via the speed change link. It is transmitted to the control valve. As a result, the hydraulic pressure is supplied from the speed change control valve to the cylinder chamber of the hydraulic cylinder, and the power roller support member is displaced in the tilt axis direction by the stroke of the piston of the hydraulic cylinder. Due to the displacement of the power roller support member, the power roller is offset from the center axis position of the input / output disk, and this offset causes a tilting force to act at the contact point between the power roller and the input / output disk, and the power roller moves the tilting shaft. The tilt angle around the center changes. This tilting motion is applied to the shift control valve via a recess cam provided on the power roller support member, a feedback link connected to the recess cam at one end, and a shift link connected to the other end of the feedback link. Then, by returning the piston of the hydraulic cylinder to the neutral position at the position where the speed change control valve is balanced, the center axis of the power roller and the disk coincide, and the power roller is set at the tilt angle position (speed ratio) at that time The That is, gear ratio feedback control is performed so that the actual gear ratio (the amount of rotation of the power roller support member) becomes the target gear ratio (the driving amount of the gear shift actuator).
[0022]
In this transmission control operation, among the components of the transmission, the transmission case and the valve body fixing element and the transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients. When the temperature changes between when the engine is started and when the vehicle is running, the feedback link strokes due to the difference in the thermal expansion coefficient between the fixed element and the transmission mechanism element, and this stroke causes the first member or the second member of the transmission control valve to move. Stroke.
[0023]
However, since the temperature compensation member is provided between the first member or the second member of the transmission control valve and the connection member of the transmission control valve and the transmission link, the thermal expansion coefficient of the fixed element and the transmission mechanism element The stroke of the shift control valve caused by the difference is absorbed. Moreover, since the position where the temperature compensation member is provided is the position between the transmission control valve and the connecting member of the transmission link, the feedback gain from the power roller support member to the transmission control valve even if the temperature compensation member expands and contracts. Will not change.
[0024]
Therefore, the shift in the gear ratio due to the difference in thermal expansion of the parts in the transmission can be corrected without changing the feedback gain from the power roller support member to the transmission control valve while achieving both strength and weight reduction of the continuously variable transmission. Can do.
[0025]
In the invention according to claim 2, the temperature compensation member is disposed coaxially with the spool shaft between the step surface of the spool end surface of the speed change control valve and the stepped cylindrical portion and the one end surface of the connecting member. In addition, the preload is set in the contraction direction by interposing an elastic body between the nut screwed into the stepped screw portion and the other end surface of the connecting member.
[0026]
Therefore, since the preload is always set in the contraction direction of the temperature compensation member, the connection position between the spool of the speed change control valve and the speed change link can be reliably changed by the amount of expansion and contraction of the temperature compensation member. Also, the axial misalignment of the temperature compensation member and the axial clearance can be easily managed.
[0027]
In the invention according to claim 3, the temperature compensating member has a cage and a follower member that are slidably fitted to each other and expand and contract integrally, and is held when the ambient temperature is lowered from room temperature. This is a member that shortens the axial length of the container and the driven member.
[0028]
Therefore, since the temperature compensation member is a member that shortens the shaft length by changing the ambient temperature from room temperature to a low temperature, the axial length is set at any part of the shift feedback mechanism connected by the shift link. In the case of a layout in which the direction to be shortened is the necessary compensation direction, it can be applied as a temperature compensation member.
[0029]
According to a fourth aspect of the present invention, in the shift control operation, among the components of the transmission, the fixing element of the transmission case and the valve body and the transmission mechanism element that operates at the time of shifting differ in thermal expansion coefficient. For example, when the temperature changes between when the engine is started and when the engine is running, the power roller support member expands and contracts due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element. The shift control valve strokes through the feedback link and the shift link.
[0030]
However, since the temperature compensation member is provided between the power roller support member and the recess cam and in the shaft portion excluding the hydraulic cylinder portion, the power roller support member is generated due to the difference in thermal expansion coefficient between the fixed element and the transmission mechanism element. The expansion and contraction of is absorbed. In addition, since the position where the temperature compensation member is provided is the shaft portion excluding the hydraulic cylinder portion, the feedback gain from the power roller support member to the transmission control valve does not change even if the temperature compensation member expands and contracts.
[0031]
Therefore, the shift in the gear ratio due to the difference in thermal expansion of the parts in the transmission can be corrected without changing the feedback gain from the power roller support member to the transmission control valve while achieving both strength and weight reduction of the continuously variable transmission. Can do.
[0032]
According to the fifth aspect of the present invention, in the shift control operation, among the components of the transmission, the fixing element of the transmission case and the valve body and the transmission mechanism element that operates at the time of shifting differ in thermal expansion coefficient. For example, when the temperature changes between when the engine is started and when the vehicle is running, the speed change actuator expands and contracts due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element. The speed change control valve strokes through.
[0033]
However, since the temperature compensation member is provided between the speed change actuator and the actuator position regulating member that fixes the speed change actuator, the expansion and contraction of the speed change actuator caused by the difference in the thermal expansion coefficient between the fixed element and the speed change mechanism element is absorbed. The In addition, since the position where the temperature compensation member is provided is between the speed change actuator and the actuator position restricting member that fixes the speed change actuator, even if the temperature compensation member expands and contracts, the power roller support member moves to the speed change control valve. The feedback gain is not changed.
[0034]
Therefore, the shift in the gear ratio due to the difference in thermal expansion of the parts in the transmission can be corrected without changing the feedback gain from the power roller support member to the transmission control valve while achieving both strength and weight reduction of the continuously variable transmission. Can do.
[0035]
In the invention according to claim 6, the temperature compensation member has a cage and a follower member that are slidably fitted to each other and integrally extend and contract, and is held when the ambient temperature is lowered from normal temperature. The shaft length of the container and the driven member is increased.
[0036]
Therefore, since the temperature compensation member is a member that lengthens the shaft length by changing the ambient temperature from room temperature to a low temperature, the axial length is set at any part of the shift feedback mechanism connected by the shift link. In the case of a layout in which the lengthening direction is the necessary compensation direction, it can be applied as a temperature compensation member.
[0037]
In the invention according to claim 7, in the shift control operation, among the components of the transmission, the fixing element of the transmission case and the valve body and the transmission mechanism element that operates at the time of shifting are different in thermal expansion coefficient. For example, when the temperature changes between when the engine is started and when the vehicle is running, the feedback link expands and contracts due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element. The spool or sleeve strokes.
[0038]
However, since a temperature compensation member is provided between the swing shaft of the feedback link and the contact portion between the feedback link and the speed change link or the speed change control valve, the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element The expansion and contraction of the feedback link caused by is absorbed. In addition, since the position where the temperature compensation member is provided is the shift link side or the shift control valve side from the oscillation shaft of the feedback link, the feedback gain from the power roller support member to the shift control valve even if the temperature compensation member expands or contracts Will not change.
[0039]
Therefore, the shift in the gear ratio due to the difference in thermal expansion of the parts in the transmission can be corrected without changing the feedback gain from the power roller support member to the transmission control valve while achieving both strength and weight reduction of the continuously variable transmission. Can do.
[0040]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a shift control device for a toroidal type continuously variable transmission according to an embodiment of the present invention will be described based on Examples 1 to 4.
[0041]
Example 1
The first embodiment is a transmission control device for a toroidal-type continuously variable transmission corresponding to the first, second, and third aspects of the invention.
[0042]
FIG. 1 is a perspective view showing a shift feedback mechanism of a shift control device for a toroidal continuously variable transmission according to a first embodiment. FIG. 2 shows a shift feedback mechanism for a shift control device for a toroidal continuously variable transmission according to a first embodiment. 1 is an input disk, 2 is an output disk, 3 is a power roller, 4 is a trunnion (power roller support member), 5 is a hydraulic cylinder, 6 is a shift control valve, 7 is a valve body, and 8 is a shift. An actuator, 9 is a recess cam, 10 is a feedback link, 11 is a speed change link, 12 is a temperature compensation member, and 13 is a connecting member.
[0043]
As shown in FIG. 2, the input disk 1 and the output disk 2 are formed so that the surfaces facing each other are formed as toroidal curved surfaces, and are disposed coaxially and opposed to each other.
[0044]
As shown in FIG. 2, the power rollers 3 and 3 are sandwiched between opposed surfaces of the input / output disks 1 and 2 so as to be tiltable about the tilt axis X.
[0045]
As shown in FIG. 1, the trunnion 4 rotatably supports the power roller 3, can rotate about the tilt axis X, and can be displaced in the direction of the tilt axis X.
[0046]
As shown in FIG. 1, the hydraulic cylinder 5 is a member provided in the middle of the shaft portion of the trunnion 4, and is a member for driving the trunnion 4 in the direction of the tilt axis X, and a piston 5 a fixed to the trunnion 4, Cylinder chambers 5b and 5c are formed at positions on the upper and lower surfaces of the piston 5a.
[0047]
As shown in FIGS. 1 and 2, the shift control valve 6 is a valve that is housed in the valve body 7 and controls the hydraulic pressure to the cylinder chambers 5b and 5c of the hydraulic cylinder 5, and has a spool 6a and a sleeve 6b. is doing. Here, the spool 6a serves as both the first member and the second member of the first aspect.
[0048]
As shown in FIGS. 1 and 2, the speed change actuator 8 is an actuator that is fixed to the valve body 7 and in which an actuator rod 8 a moves forward and backward according to a speed change command, and is connected via the speed change link 11. The spool 6a of the valve 6 is driven.
[0049]
As shown in FIGS. 1 and 2, the feedback link 10 is an L shape that converts a rotational motion around the tilt axis X of the trunnion 4 into a reciprocating motion in response to a recess cam 9 provided at the lower portion of the trunnion 4. The link includes a swing shaft 10a, a cam follower arm portion 10b closer to the trunnion 4 than the swing shaft 10a, and a connecting arm portion 10c closer to the speed change link 11 than the swing shaft 10a.
[0050]
As shown in FIGS. 1 and 2, the speed change link 11 connects the connection arm portion 10 c of the feedback link 10, the actuator rod 8 a of the speed change actuator 8, and the connection shaft portion 6 c of the speed change control valve 6 to each other. By connecting, the rotation amount of the trunnion 4 is transmitted to the spool 6a of the transmission control valve 6 so that the actual transmission ratio becomes the target transmission ratio, and transmission ratio feedback control is performed. As shown in FIG. 2, the shift feedback mechanism has a shift control valve 6 disposed at a central position, and feedback links 10 and shift actuators 8 disposed at both side positions thereof. The connecting portion between the transmission link 11 and the feedback link 10 is CL, the connecting portion between the transmission link 11 and the transmission actuator 8 is CA, and the connecting portion between the transmission link 11 and the transmission control valve 6 is CV.
[0051]
Of the components of the toroidal-type continuously variable transmission, the transmission case (not shown) and the fixing element of the valve body 7 are made of aluminum alloy, and the speed change mechanism elements (trunnion 4, piston 5a, precess cam 9) that operate at the time of shifting. The feedback link 10, the spool 6a, the sleeve 6b, etc.) are manufactured from iron having a different thermal expansion coefficient from that of the aluminum alloy.
[0052]
As shown in FIG. 1, there is a difference in thermal expansion coefficient between the fixed element and the transmission mechanism element between the spool 6a of the transmission control valve 6 and the connecting member 13 of the spool 6a and the transmission link 11. A temperature compensation member 12 that absorbs the stroke of the spool 6a of the speed change control valve 6 caused by the above is provided.
[0053]
Next, the configuration of the connecting portion CV provided with the temperature compensation member 12 will be described with reference to FIG.
[0054]
The spool 6a of the speed change control valve 6 is integrally provided with a stepped cylindrical portion 6c ′ and a stepped screw portion 6c ″ constituting a connecting shaft portion 6c on one end surface thereof. An insertion hole 13 a through which the stepped screw portion 6 c ″ is inserted is formed, and the temperature compensation member 12 is formed between a step surface of the spool end surface and the stepped cylindrical portion 6 c ′, and one end surface of the connecting member 13. And an elastic body 15 such as a disc spring is interposed between the nut 14 and the other end face of the connecting member 13 which are inserted coaxially with the spool shaft and screwed into the stepped screw portion 6c ″. Thus, a preload is set in the contraction direction of the temperature compensation member 12. Note that 16 is a pin for fixing the nut 14.
[0055]
Next, the configuration of the temperature compensation member 12 will be described with reference to FIGS.
[0056]
The temperature compensation member 12 includes an annular cage 21 formed with a cylinder groove 21a into which a washer 20 having a plurality of cylinder holes 20a is fitted, and the annular cage 21 is slidable integrally. An annular driven member 22 having a plurality of pistons 22a slidable in the cylinder hole 20a and a cylinder chamber 23 that is closed by a seal fit between the piston 22a and the cylinder hole 20a are filled, and the ambient temperature is from room temperature. And a filler 24 that shortens the axial length by lowering the temperature. That is, as the filler 24, a liquid that changes in volume according to temperature, a semi-solid body, or the like is used, and the displacement is increased by the volume change caused by the temperature change of the filler 24. In FIG. 4, reference numeral 25 denotes a retaining ring that stops the washer 20 at an intermediate position in the cylinder groove 21a, and 26 denotes a seal portion of the piston 22a.
[0057]
Next, the operation will be described.
[0058]
[Shift control action]
At the time of shifting, a command for obtaining a target speed ratio (or target input rotation speed) is output to the speed change actuator 8, and the drive amount of the speed change actuator 8 is transmitted to the spool 6 a of the speed change control valve 6 via the speed change link 11. It is done. As a result, the hydraulic pressure is supplied from the shift control valve 6 to one cylinder chamber 5b or 5c of the hydraulic cylinder 5, the oil is extracted from the other cylinder chamber 5c or 5b, and the piston 5a of the hydraulic cylinder 5 is stroked by the differential pressure. The trunnion 4 is displaced in the direction of the tilt axis X.
[0059]
Due to the displacement of the trunnion 4, the power roller 3 is offset from the center axis position of the input / output disks 1, 2, and by this offset, a tilting force acts at the contact point between the power roller 3 and the input / output disks 1, 2. The tilt angle of the roller 3 about the tilt axis X changes.
[0060]
This tilting motion is shifted through a recess cam 9 provided in the trunnion 4, a feedback link 10 having one end connected to the recess cam 9, and a speed change link 11 having the other end connected to the feedback link 10. By returning the piston 5a of the hydraulic cylinder 5 to the neutral position at the position where the spool 6a of the speed change control valve 6 is balanced, the center axis of the power roller 3 and the center axes of both disks 1 and 2 are transmitted to the spool 6a of the control valve 6. And the power roller 3 is set at the tilt angle position (transmission ratio) at that time.
[0061]
That is, the transmission ratio feedback control is performed so that the actual transmission ratio (the amount of rotation of the trunnion 4) becomes the target transmission ratio (the driving amount of the transmission actuator 8).
[0062]
[Gear ratio shift prevention action due to thermal expansion]
In the transmission control operation described above, among the components of the transmission, the transmission case and the valve body 7 fixing element (not shown) and the transmission mechanism element operating at the time of shifting are made of aluminum alloy material and iron material having different thermal expansion coefficients. For example, when the temperature changes between when the engine is started and when the engine is running, the feedback link 10 strokes due to the difference in thermal expansion coefficient between the fixed element and the transmission mechanism element. The spool 6a strokes.
[0063]
However, since the temperature compensation member 12 is provided between the spool 6a of the speed change control valve 6 and the connecting member 13 of the spool 6a and the speed change link 11, due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element. The generated stroke of the spool 6a of the speed change control valve 6 is absorbed. For example, as shown in FIG. 2, when the speed change link 11 moves in the contraction direction indicated by an arrow from normal temperature to low temperature, the temperature compensation member 12 provided between the spool 6 a and the connecting member 13 is in this contraction direction. The spool stroke is absorbed immediately before the stroke of the spool 6a is reached.
[0064]
Moreover, since the position where the temperature compensation member 12 is provided is the position between the spool 6a of the transmission control valve 6 and the connecting member 13, even if the temperature compensation member 12 expands and contracts, the trunnion 4 is connected to the transmission control valve 6. The feedback gain is not changed.
[0065]
Furthermore, since the pre-load is applied to the temperature compensation member 12 by the elastic body 15, the axial misalignment and the axial clearance can be easily managed. For example, when the temperature in the continuously variable transmission decreases, the connecting member 13 moves so as to follow the contraction of the temperature compensating member 12, and is connected between the temperature compensating member 12 and the spool 6a or with the temperature compensating member 12. No axial clearance is formed between the members 13.
[0066]
Next, the effect will be described.
[0067]
(1) Since the temperature compensation member 12 is provided between the spool 6a of the transmission control valve 6 and the connecting member 13 of the spool 6a and the transmission link 11, there is no need to use different materials for the fixed element and the transmission mechanism element. The shift in the gear ratio due to the difference in thermal expansion of the components in the transmission can be corrected without changing the feedback gain from the trunnion 4 to the transmission control valve 6 while achieving both strength and weight reduction of the step transmission.
[0068]
(2) Since the temperature compensation member 12 is preloaded by the elastic body 15, the connection position CV between the spool 6 a of the speed change control valve 6 and the speed change link 11 is set by the amount of expansion and contraction of the temperature compensation member 12. It can be changed reliably, and the axial misalignment of the temperature compensation member 12 and the axial clearance can be easily managed.
[0069]
(3) Since the temperature compensation member 12 is a member that shortens the shaft length by changing the ambient temperature from room temperature to a low temperature, the axial direction can be adjusted at any part of the shift feedback mechanism connected by the shift link 11. In the case of a layout in which the direction in which the length is extended is the necessary compensation direction, it can be applied as a temperature compensation member.
[0070]
(Example 2)
The second embodiment is a shift control device for a toroidal type continuously variable transmission corresponding to the invention described in claim 4.
[0071]
The second embodiment is an example in which the temperature compensating member 12 shown in the first embodiment is provided between the outer shaft portion 4b of the trunnion 4 and the recess cam 9 and on the shaft portion excluding the piston portion of the hydraulic cylinder 5. is there.
[0072]
That is, as shown in FIG. 6, the trunnion 4 is composed of a power roller support portion 4 a, an outer shaft portion 4 b, and an inner shaft portion 4 c, and a temperature compensation member 12 is set between the outer shaft portion 4 b and the recess cam 9. Has been. Here, as in the first embodiment, in order to move the recess cam 9 following the expansion and contraction of the temperature compensation member 12, a nut 30 is screwed to the end of the inner shaft portion 4c. 9, an elastic body 31 for applying a preload to the temperature compensation member 12 is interposed. Further, in order to rotate the inner shaft portion 4 c of the trunnion 4 and the recess cam 9 together, a ball spline 32 is disposed between the both 4 c and 9. In FIG. 6, 33 is a retaining ring for preventing the ball spline 32 from dropping off, 34 is a pin for fixing the nut 30, and 35 is a stopper for securing an oil passage in the inner shaft portion 4c.
[0073]
Here, the reason why the temperature compensation member 12 is set to a shaft portion position excluding the piston portion of the hydraulic cylinder 5 is that the feedback gain from the trunnion 4 to the transmission control valve 6 is not changed, and when the temperature changes, the temperature compensation is performed. This is because the expansion and contraction of the member 12 prevents interference between the piston 5a and the cylinder chambers 5b and 5c. Since other configurations are the same as those of the first embodiment, illustration and description thereof are omitted.
[0074]
Next, the operation will be described.
[0075]
In the transmission control operation described in the operation of the first embodiment, among the components of the transmission, the transmission case and the fixing element of the valve body 7 (not shown) and the transmission mechanism element that operates at the time of the transmission have a coefficient of thermal expansion. By being manufactured with different aluminum alloy materials and iron materials, for example, when the temperature changes between when the engine is started and when running, the trunnion 4 expands and contracts due to the difference in the thermal expansion coefficient between the fixed element and the transmission mechanism element, As the trunnion 4 expands and contracts, the feedback link 10 and the speed change link 11 that operate via the recess cam 9 stroke, and the stroke of the speed change link 11 causes the spool 6a of the speed change control valve 6 to stroke.
[0076]
However, since the temperature compensation member 12 is provided between the outer shaft portion 4b of the trunnion 4 and the recess cam 9, and the shaft portion excluding the piston portion of the hydraulic cylinder 5, the coefficient of thermal expansion of the fixed element and the transmission mechanism element. The expansion / contraction of the trunnion 4 caused by the difference is absorbed by the temperature compensation member 12, and as a result, the stroke of the spool 6a of the shift control valve 6 is absorbed.
[0077]
Moreover, since the position where the temperature compensation member 12 is provided is the shaft portion excluding the hydraulic cylinder 5 portion, the feedback gain from the trunnion 4 to the transmission control valve 6 does not change even if the temperature compensation member 12 expands and contracts. .
[0078]
Therefore, in the second embodiment, the temperature compensating member 12 is provided between the outer shaft portion 4b of the trunnion 4 and the recess cam 9 and on the shaft portion excluding the piston portion of the hydraulic cylinder 5, so that the fixed element By using different materials for the speed change mechanism elements, the strength and weight of the continuously variable transmission can be reduced, and without changing the feedback gain from the trunnion 4 to the speed change control valve 6, The shift in the gear ratio can be corrected.
[0079]
Example 3
The third embodiment is a shift control device for a toroidal-type continuously variable transmission corresponding to the fifth and sixth aspects of the invention.
[0080]
The third embodiment is an example in which the temperature compensation member 40 shown in FIG. 8 is provided between the speed change actuator 8 and the actuator position restricting member 41 that fixes the speed change actuator 8.
[0081]
That is, as shown in FIG. 7, a ball spline 42 that fixes an actuator position restricting member 41 to the valve body 7 and supports the speed change actuator 8 so as to be movable in the axial direction between the actuator position restricting member 41 and the speed change actuator 8. The temperature compensation member 40 is set between the inner end surface of the actuator position restricting member 41 and the connection side end surface of the speed change actuator 8. Reference numeral 43 in FIG. 7 denotes a retaining ring for preventing the ball spline 42 from dropping off.
[0082]
FIG. 8 shows the temperature compensation member 40. Unlike the first and second embodiments, the temperature compensation member 40 is a member whose axial length is extended by a temperature change from normal temperature to low temperature. That is, the temperature compensation member 40 includes a retainer 44 in which a cylinder hole 44a is formed, a follower member 45 in which the retainer 44 is slidable integrally, a piston portion 45a is formed, and a cylinder hole 44a. Of the cylinder chamber defined by the driven member 45, the first filler 46 is filled in the space other than the extension of the piston portion 45a and the upper and lower positions of the second filler 47, and thermally shrinks at normal temperature → low temperature, The first filler 46 is surrounded by and filled with the first filler 46 and is hardly heat-shrinked at room temperature → low temperature, and the first filler 46 is thermally shrunk at room temperature → low temperature, and the second filler 47 therein. By reducing the effective volume of and extruding, the shaft length increases from room temperature to low temperature. 8 shows the shaft-shaped temperature compensation member 40. However, as shown in FIGS. 4 and 5, the washer-shaped temperature compensation member 40 may be used, and the washer-shaped temperature compensation member 40 is shown in FIG. This is employed in the transmission actuator 8. Other configurations are the same as those of the first embodiment, and thus illustration and description thereof are omitted.
[0083]
Next, the operation will be described.
[0084]
In the transmission control operation described in the operation of the first embodiment, among the components of the transmission, the transmission case and the fixing element of the valve body 7 (not shown) and the transmission mechanism element that operates at the time of the transmission have a coefficient of thermal expansion. Manufactured with different aluminum alloy material and iron material, for example, when the temperature changes between engine start and running, the actuator rod of the speed change actuator 8 due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element As the actuator rod 8a expands and contracts, the spool 6a of the shift control valve 6 connected by the shift link 11 strokes.
[0085]
However, since the temperature compensation member 40 is provided between the speed change actuator 8 and the actuator position restricting member 41 that fixes the speed change actuator 8, the speed change actuator 8 caused by the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element. The expansion / contraction of the actuator rod 8a is absorbed, and the stroke of the spool 6a of the transmission control valve 6 connected by the transmission link 11 is absorbed.
[0086]
In addition, since the position where the temperature compensation member 40 is provided is between the speed change actuator 8 and the actuator position restricting member 41 that fixes the speed change actuator 8, speed change control is performed from the trunnion 4 even if the temperature compensation member 40 expands and contracts. The feedback gain to the valve 6 is not changed.
[0087]
Therefore, in the third embodiment, since the temperature compensation member 40 is provided between the speed change actuator 8 and the actuator position restricting member 41 that fixes the speed change actuator 8, the fixing element and the speed change mechanism element are made of different materials. The shift of the gear ratio due to the difference in thermal expansion of components in the transmission can be corrected without changing the feedback gain from the trunnion 4 to the transmission control valve 6 while achieving both strength and weight reduction of the continuously variable transmission. it can.
[0088]
Furthermore, since the temperature compensation member 40 is a member that increases the axial length by changing the ambient temperature from room temperature to a low temperature, the axial direction length can be increased at any part of the transmission feedback mechanism connected by the transmission link 11. In the case of a layout in which the direction of extending the length is the necessary compensation direction, it can be applied as a temperature compensation member.
[0089]
(Example 4)
The fourth embodiment is a shift control device for a toroidal-type continuously variable transmission corresponding to the seventh aspect of the present invention.
[0090]
In the fourth embodiment, the temperature compensation member 12 shown in the first embodiment is provided between the swing shaft 10a of the feedback link 10 and the contact portion 10d between the feedback link 10 and the transmission link 11. is there.
[0091]
That is, as shown in FIG. 9, the shift link 11 side of the connecting arm portion 10c of the feedback link 10 is cut, and a pin 50 having a threaded end is fixed to the connecting arm portion 10c, and the pin 50 is inserted. Thus, a ball-shaped contact portion 10d is provided, and the temperature compensation member 12 is interposed between the contact portion 10d and the cut end surface of the connecting arm portion 10c. A nut 51 is screwed onto the end of the pin 50, and the elastic member 52 interposed between the nut 51 and the contact portion 10d is attached to the temperature compensation member 12 as in the first and second embodiments. Preload is given to it. Since other configurations are the same as those of the first embodiment, illustration and description thereof are omitted.
[0092]
Next, the operation will be described.
[0093]
In the transmission control operation described in the operation of the first embodiment, among the components of the transmission, the transmission case and the fixing element of the valve body 7 (not shown) and the transmission mechanism element that operates at the time of the transmission have a coefficient of thermal expansion. The feedback link 10 expands and contracts due to the difference in thermal expansion coefficient between the fixed element and the speed change mechanism element when the temperature changes between when the engine is started and when the engine is running, for example, because it is manufactured from different aluminum alloy materials and iron materials. As a result of this expansion and contraction, the spool 6a of the transmission control valve 6 strokes through the transmission link 11.
[0094]
However, since the temperature compensation member 12 is provided between the rocking shaft 10a of the feedback link 10 and the contact portion 10d between the feedback link 10 and the transmission link 11, the thermal expansion coefficient of the fixed element and the transmission mechanism element. The expansion and contraction of the feedback link 10 caused by the difference is absorbed.
[0095]
Moreover, since the position where the temperature compensation member 12 is provided is closer to the speed change link 11 than the swing shaft 10a of the feedback link 10, the feedback gain from the trunnion 4 to the speed change control valve 6 is increased even if the temperature compensation member 12 expands and contracts. There is no change.
[0096]
Therefore, in the third embodiment, since the temperature compensation member 12 is provided between the swing shaft 10a of the feedback link 10 and the contact portion 10d between the feedback link 10 and the transmission link 11, Shifting due to the difference in thermal expansion of parts in the transmission without changing the feedback gain from the trunnion 4 to the transmission control valve 6 while achieving both strength and weight reduction of the continuously variable transmission by using different transmission mechanism elements. The deviation of the ratio can be corrected.
[0097]
(Other examples)
In the first to fourth embodiments, as the shift feedback mechanism, a mechanism having a layout in which the shift control valve 6 of FIG. 2 is arranged in the center is shown. However, for example, as shown in FIG. The layout in which the control valve 6 is arranged at the end, the feedback link 10 is arranged at a position close to the transmission control valve 6, and the transmission actuator 8 is arranged at a position far from the transmission control valve 6, or as shown in FIG. The present invention can also be applied to a layout in which the shift control valve 6 is disposed at the end, the shift actuator 8 is disposed at a position close to the shift control valve 6, and the feedback link 10 is disposed at a position far from the shift control valve 6. it can.
However, when the layouts are different, the necessary compensation directions are different. For example, in the case of the layout shown in FIG. 10, both the first and third embodiments use the temperature compensation member 12, as shown in FIG. In the case of the layout, the temperature compensation member 40 is used in the first embodiment, and the temperature compensation member 12 is used in the third embodiment.
[0098]
In the first to fourth embodiments, the temperature compensation members 12 and 40 shown in FIGS. 4 and 5 and FIG. 8 are shown. However, the specific configuration is not limited to this, and the shaft length changes due to a temperature change. As long as it is a member, other various configurations can also be applied.
[0099]
Further, in the first to fourth embodiments, the example of the speed change link 11 that connects the three components of the feedback link 10, the speed change control valve 6, and the speed change actuator 8 to each other is shown. The spool 6a or the sleeve 6b may be in direct contact with or connected to each other and may be a transmission link 11 that connects this common connection point to the transmission actuator 8, or two configurations of the feedback link 10 and the transmission control valve 6. The speed change actuator 8 may be configured to drive the speed change control valve 6 without interposing the speed change link.
[0100]
In addition, in the first to fourth embodiments, the spool 6a of the speed change control valve 6 serves as the first member for transmitting the drive amount of the speed change actuator and the second member for transmitting the rotation amount of the power roller support member. However, the first member is a spool and the second member is a sleeve, or the first member is a sleeve and the second member is a spool. Even can be applied.
[Brief description of the drawings]
FIG. 1 is a perspective view showing a shift feedback mechanism of a shift control device for a toroidal type continuously variable transmission according to a first embodiment.
FIG. 2 is a layout diagram illustrating a shift feedback mechanism of a shift control device for a toroidal-type continuously variable transmission according to the first embodiment.
FIG. 3 is a cross-sectional view illustrating a temperature compensation member mounting portion of the shift control device for the toroidal-type continuously variable transmission according to the first embodiment.
4 is a cross-sectional view showing a temperature compensation member employed in Example 1. FIG.
FIG. 5 is a plan view showing an annular cage, an annular driven member, and a washer constituting the temperature compensating member employed in the first embodiment.
6 is a cross-sectional view showing a temperature compensation member mounting portion of a shift control device for a toroidal-type continuously variable transmission according to Embodiment 2. FIG.
FIG. 7 is a cross-sectional view showing a temperature compensation member mounting portion of a shift control device for a toroidal-type continuously variable transmission according to a third embodiment.
8 is a cross-sectional view showing a temperature compensation member employed in Example 3. FIG.
FIG. 9 is a cross-sectional view illustrating a temperature compensation member mounting portion of a shift control device for a toroidal-type continuously variable transmission according to a fourth embodiment.
FIG. 10 is a layout diagram showing a shift feedback mechanism of a shift control device for a toroidal-type continuously variable transmission different from the first to fourth embodiments.
11 is a layout diagram showing a shift feedback mechanism of a shift control device for a toroidal-type continuously variable transmission different from FIGS.
FIG. 12 is a diagram showing a shift control device for a conventional toroidal-type continuously variable transmission.
[Explanation of symbols]
1 Input disk
2 Output disk
3 Power roller
4 Trunnion (Power roller support member)
5 Hydraulic cylinder
6 Shift control valve
7 Valve body
8 Variable speed actuator
9 Precess Cam
10 Feedback link
11 Shift link
12 Temperature compensation member
13 Connecting member

Claims

An input disk and an output disk that are arranged to face each other on the same axis while forming mutually opposing surfaces in a toroidal curved surface,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
The shift control valve includes a first member that transmits a drive amount of the shift actuator, and a second member that transmits a rotation amount of the power roller support member,
Speed change control caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element between the first member or the second member of the speed change control valve and the connection member of the speed change control valve and the speed change link A shift control device for a toroidal-type continuously variable transmission, characterized in that a temperature compensation member for absorbing the stroke of the valve is provided.

The shift control device for a toroidal type continuously variable transmission according to claim 1,
The spool that serves as both the first member and the second member of the speed change control valve is integrally provided with a stepped cylindrical portion and a stepped screw portion at one end surface thereof,
The connecting member is formed with an insertion hole through which the stepped screw portion is inserted,
The temperature compensation member is interposed coaxially with the spool shaft between the step surface of the spool end surface and the stepped cylindrical portion and one end surface of the connecting member, and is screwed to the stepped screw portion. A shift control device for a toroidal continuously variable transmission, characterized in that a preload is set in the contraction direction by interposing an elastic body between the nut and the other end surface of the connecting member.

In the shift control device for the toroidal continuously variable transmission according to claim 1 or 2,
The temperature compensation member has a cage and a follower member that are slidably fitted to each other and integrally extend and contract, and the axial length of the cage and the follower member is shortened when the ambient temperature is lowered from room temperature. A shift control device for a toroidal-type continuously variable transmission, characterized by being a member.

An input disk and an output disk that are arranged to face each other on the same axis while forming mutually opposing surfaces in a toroidal curved surface,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A temperature between the power roller support member and the recess cam that absorbs a stroke of the speed change control valve caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element in the shaft part excluding the hydraulic cylinder part. A shift control device for a toroidal-type continuously variable transmission, comprising a compensation member.

An input disk and an output disk that are arranged to face each other on the same axis while forming mutually opposing surfaces in a toroidal curved surface,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
The feedback link, the speed change actuator, and the speed change control valve are connected to each other, and the rotation amount of the power roller support member is transmitted to the speed change control valve so that the actual speed change ratio becomes the target speed change ratio. A shift link for performing control,
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A temperature compensation member that absorbs a stroke of a shift control valve caused by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element is provided between the speed change actuator and a connecting member of the speed change actuator and the speed change link. A transmission control device for a toroidal-type continuously variable transmission, characterized by the above.

In the shift control device for the toroidal type continuously variable transmission according to claim 5,
The temperature compensation member includes a cage and a follower member that are slidably fitted to each other and integrally extend and contract, and the axial length of the cage and the follower member is increased when the ambient temperature is lowered from room temperature. A shift control device for a toroidal-type continuously variable transmission, characterized by being a member.

An input disk and an output disk that are arranged to face each other on the same axis while forming mutually opposing surfaces in a toroidal curved surface,
A power roller that can be tilted and held between opposing surfaces of the input / output disk;
A power roller support member that rotatably supports the power roller, is rotatable around the tilt axis, and is displaceable in the tilt axis direction;
A hydraulic cylinder that drives the power roller support member in the direction of the tilt axis;
A shift control valve housed in the valve body and controlling the hydraulic pressure to the cylinder chamber of the hydraulic cylinder;
A speed change actuator for driving the speed change control valve;
A feedback link that converts a rotational motion of the power roller support member into a reciprocating motion in response to a recess cam provided on the power roller support member;
A transmission link that connects the feedback link and the transmission control valve to each other, and transmits the rotation amount of the power roller support member to the transmission control valve so that the actual transmission ratio becomes the target transmission ratio, thereby performing transmission ratio feedback control. And
In a transmission control device for a toroidal continuously variable transmission in which a transmission case and a fixed element of the valve body, and a transmission mechanism element that operates at the time of shifting are manufactured from materials having different thermal expansion coefficients among the components of the transmission ,
A speed change control valve generated by a difference in thermal expansion coefficient between the fixed element and the speed change mechanism element between a swing shaft of the feedback link and a contact portion between the feedback link and the speed change link or the speed change control valve. A speed change control device for a toroidal type continuously variable transmission, characterized in that a temperature compensation member for absorbing the stroke is provided.