JP3972652B2 - Pulley device - Google Patents

Pulley device Download PDF

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JP3972652B2
JP3972652B2 JP2001395295A JP2001395295A JP3972652B2 JP 3972652 B2 JP3972652 B2 JP 3972652B2 JP 2001395295 A JP2001395295 A JP 2001395295A JP 2001395295 A JP2001395295 A JP 2001395295A JP 3972652 B2 JP3972652 B2 JP 3972652B2
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sheave
fixed sheave
peripheral surface
shaft portion
inclined surface
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JP2003194191A (en
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誠 土橋
克守 藤井
和道 佃
義久 伊藤
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Aisin AW Co Ltd
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Aisin AW Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/0489—Friction gearings with endless flexible members, e.g. belt CVTs

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Pulleys (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、プーリ装置、特に自動車に搭載される無段変速機（ＣＶＴ）に適用して好適なプーリ装置に係り、詳しくはプーリ装置のベルト当接面に潤滑油を供給する油路構造に関する。
【０００２】
【従来の技術】
一般に、プーリ装置は、図４，図５に示すように、固定シーブ１の軸部１ａに可動シーブ２を摺動自在に支持すると共に、ボールスプライン等により両シーブ１，２が一体に回転するように構成されている。そして、上記固定シーブ軸部１ａに形成された縦油路３ａ及び横油路３ｂを介して、上記シーブ１，２のベルト当接面１ｃ，２ｃに潤滑油を供給している。
【０００３】
従来、上記潤滑油供給油路、特に横油路３ｂは、図４に示すように、固定シーブ１の傾斜面（ベルト当接面）１ｃの根本部１ｄに臨んで開口ａするように形成されている。また、図５に示すように、固定シーブ１の傾斜面根本部１ｄから所定間隔ｌだけ離した位置に、上記横油路３ｂの開口ａが位置するように配置されている。
【０００４】
【発明が解決しようとする課題】
プーリ装置は、シーブの傾斜面（ベルト当接面）１ｃ，２ｃとベルトの間に強い挟圧力を作用し、ベルトとシーブとの間の摩擦力によりトルクを伝達する関係上、油圧装置等によりシーブ１，２に強い軸力が付与されている。そして、上記軸力及びトルクは、シーブのベルト当接面及びベルトとの間で作用するので、シーブ、特に固定シーブ２の傾斜面１ｃの軸部根本部１ｄに大きな荷重が集中して作用する。
【０００５】
上記図４に示すように、横油路３ｂを、固定シーブ傾斜面根本部１ｄに臨んで配置するものは、上述したように大きな集中荷重が作用するシーブ根本部１ｄに複数の横油路３ｂが放射状に位置することになり、強度上不利な構造となっている。
【０００６】
更に、固定シーブ１のベルト当接面である傾斜面１ｃを形成する際、その根本部１ｄに切下げ用凹溝１ｅが形成されることが多く、この場合、上記横油路３ｂは上記凹溝１ｅに開口ａすることになり、更に強度上不利な構造となってしまう。
【０００７】
また、図５に示すように、上記固定シーブ傾斜面根本部１ｄから所定間隔ｌ離して横油路３ｂを配置したものは、上述したように、強度上の不利は解消されるが、可動シーブ２が固定シーブ１に近づいたベルト有効径が大となる状態において、上記所定間隔離れた横油路３ｂの開口ａ上に可動シーブ２の内周面ｉが被さると、該横油路３ｂが閉塞されてしまい、ベルト当接面が潤滑不良状態となってしまう。この種プーリ装置は、シーブの大きな挟圧力の基に、金属ベルトとシーブ当接面が接触してトルク伝達を行うものであって、上記金属同士の接触面は、常に潤滑油の介在を必要とし、従って、可動シーブ２が横油路３ｂの開口ａを塞がない範囲までに、可動シーブ２の移動量を規制する必要がある。
【０００８】
このため、該図５に示すプーリ装置は、ベルトの最大有効半径が規制され、プーリ装置の変速比が制限されることになる。
【０００９】
そこで、本発明は、潤滑油供給用横油路を固定シーブ根本部から所定間隔離して配置したものでありながら、可動シーブを固定シーブに近づけた状態においても潤滑油の供給を可能とし、もって上述した課題を解決したプーリ装置を提供することを目的とするものである。
【００１０】
【課題を解決するための手段】
本発明は、固定シーブ（１）と、該固定シーブの軸部（１ａ）に摺動自在に支持された可動シーブ（２）と、を備え、前記固定シーブ及び可動シーブの両傾斜面（１ｃ，２ｃ）にベルト（２０）を当接して挟持すると共に、該ベルトの当接部分に潤滑油を供給すべく、前記固定シーブの軸部（１ａ）に形成された油路（３ａ，３ｂ）が該軸部の外周面に開口（ａ）してなるプーリ装置において、
前記可動シーブ（２）が前記固定シーブ（１）に接近した状態で、前記油路の開口（ａ）を、前記可動シーブがオーバラップする位置に配置し、
該オーバラップする状態において、前記固定シーブ軸部（１ａ）の外周面（ｓ）と前記可動シーブの内周面（ｉ）との間に所定間隙（ｃ）を形成して、潤滑油を、前記開口から該所定間隙（ｃ）を通って前記当接部分に導くことを特徴とする、
プーリ装置にある。
【００１１】
なお、上記オーバラップとは、少なくとも開口の一部が可動シーブと軸方向にオーバラップする状態を含むものである。
【００１２】
そして、前記可動シーブの固定シーブ側内周面（ｉ）は、前記固定シーブの軸部の外周面（ｐ）と対接する直線状の面にて形成され、
前記固定シーブ（１）の前記傾斜面（１ｃ）の根本部（１ｄ）に凹部（ｕ）を有すると共に該凹部を所定長さ可動シーブ側に延長して、該延長部分（ｓ）に前記開口（ａ）を配置してなる。
【００１３】
更に、前記固定シーブの前記傾斜面（１ｃ）の根本部（１ｄ）に例えばアール形状（ｒ）からなる凹部（ｕ）を全周に亘り形成し、該凹部の底面（ｕ１）から前記可動シーブの内周面に対接する固定シーブ軸部外周面（ｐ）に向かう傾斜面（ｓ）を全周に亘って形成し、
該傾斜面（ｓ）の途中に前記開口（ａ）を配置してなる。
【００１４】
なお、上記カッコ内の符号は、図面と対照するためのものであるが、これにより特許請求の範囲の構成に何等影響を及ぼすものではない。
【００１５】
【発明の効果】
本発明によると、潤滑油供給用油路は、その開口が可動シーブにオーバラップする位置に配置されて、固定シーブの傾斜面根本部から所定間隔離れて配置されるので、強度上有利な構造となっており、かつ可動シーブが開口をオーバラップしても、該開口からの潤滑油は、所定間隙を通ってベルト当接部分に導かれるので、該ベルト当接部分が潤滑不良となることなく、可動シーブを固定シーブに近接するまでスライド可能となり、ベルト最大有効径を確保することができ、これらが相俟って、軸部の所定強度及びベルト最大有効径を確保しつつ、コンパクトな構成のプーリ装置を得ることができる。
【００１６】
また、固定シーブの傾斜面の根本部に凹部を有し、該傾斜面を軸部延長部（図３のｑ参照）近傍まで正確に形成することが可能となり、かつ可動シーブの固定シーブ側内周面を直線状の面としたので、ベルトは固定シーブ軸部に接する近傍まで移動可能になり、ベルト最小有効径をも確保して、変速比を拡大することが可能となるものでありながら、上記凹部の延長部に開口を形成して、潤滑油の供給を簡単な構成で確実に行うことができる。
【００１７】
更に、例えば凹部をアール形状にて形成すると共に、該凹部底面から傾斜面を形成したので、上記凹部及び傾斜面が全体に滑らかに形成されて、切欠き効果を減少して、強度上の不利を更に解消すると共に、全周に亘る傾斜面の途中に開口を設けたので、該傾斜面と可動シーブ内周面との間の間隙が小さくても、全周に亘りかつ傾斜面にて末広がりとなる流路を確保して、潤滑油路からの油量を実質的に絞ることなく流して、ベルト最大有効径となって多くの潤滑油が必要になることに対応した充分な量の潤滑油を供給することができる。
【００１８】
【発明の実施の形態】
以下、図面に沿って、本発明の実施の形態について説明する。図１は、本発明を適用したベルト伝動装置（ＣＶＴ）のプーリ装置、詳しくはプライマリ側（エンジン等の駆動源側）のプーリ装置を示す断面図であり、該プーリ装置Ｐは、固定シーブ１及び可動シーブ２からなる。固定シーブ及び可動シーブは、それぞれ対向する面が外径方向に向かって拡がる方向に傾斜した傾斜面１ｃ，２ｃを有するフランジ形状からなり、かつ固定シーブ１は、可動シーブ方向に延びる軸部１ａを有している。
【００１９】
該軸部１ａの外周面には可動シーブ２のボス部２ａが摺動自在に支持されており、かつ固定シーブ軸部１ａの外周面及び可動シーブボス部２ａの内周面には、軸方向に延びる３個の凹溝５，６がそれぞれ形成されており、これら相対向する凹溝に複数のボール７が充填されて、ボールスプライン８が形成されており、上記可動シーブ２は、これらボールスプライン８を介して固定シーブ１に軸方向に移動自在にかつ相対回転不能に支持されている。また、上記ボス部側凹部５の外方端部及び上記軸部側凹溝６の内方端部分には、それぞれ周方向にスナップリング９，１０が装着されており、上記ボール７が抜け落ちることを防止している。
【００２０】
また、可動シーブ２の背面には、シリンダとなるフランジ１１が配置されており、該フランジ１１と可動シーブ２の先端２ｅとの間がオイルシール１２にて軸封され、油圧室１３を構成している。上記フランジ１１は、固定シーブ軸部１ａの先端に形成されたネジ部にナット１５が螺合することにより、ベアリング１６及びワッシャ１７を介して該軸部１ａに固定されている。なお、本プーリ装置Ｐは、その後部側を上記ベアリング１６により、また先端側を固定シーブ背面の鍔部１ｅ外周面に装着されたベアリング（図示せず）によりケースに支持されている。
【００２１】
また、固定シーブ軸部１ａには、後端側から油孔１７が形成されており、該油孔は、軸部１ａ及びボス部２ａに形成された横油孔１７ａ，１７ｂを介して上記油圧室１３に連通されており、コントロールバルブに切換えられる油圧が、ケースから上記油孔１７，１７ａ，１７ｂを介して油圧室１３に供給され、可動シーブ２の軸方向位置を制御する。セカンダリプーリ装置にも、油圧装置により伝達トルクに応じた油圧が供給されており、これら両プーリ装置Ｐの間に金属ベルト２０が挟持されて、両プーリ装置間に、該金属ベルト２０を介してトルクが伝達される。また、上記可動シーブ２が、スライドすることにより、金属ベルト２０の有効径が変化して、変速される。
【００２２】
一方、固定シーブ軸部１ａの前端側に開口して潤滑油用縦油路３ａが形成されており、該油路３ａの先端部分には、直径等の放射状に横油路３ｂが形成されて、これら横油路は、軸部１ａの外周面に開口ａしている。また、該固定シーブ１の背面側には、図示しない前後進切換え装置等が配置されており、該前後進切換え装置を介在して、エンジン等の駆動源から上記背面鍔部１ｅの内径スプラインを介して動力が伝達されている。また、前記縦油路３ａには入力軸等が油密状に嵌合して、該入力軸の油路を介して潤滑油が供給されている。
【００２３】
そして、図２及び図３に詳示するように、固定シーブ１の傾斜面１ｃと軸部１ａとの交差部分、即ち固定シーブの傾斜面側根本部分１ｄは、アール形状ｒにより凹部ｕが形成されており、更に該凹部ｕの底部ｕ1 から軸部１ａの外周面ｐに向かって所定傾斜角θの傾斜面ｓが延びて凹部延長部を構成している。従って、固定シーブ１の傾斜面根本部分は、ベルト当接面となる傾斜面１ｃが軸部１ａの外周面延長部分ｑまで延びており、そこからアール形状ｒ等による滑らかな形状にて凹んでおり、更に該凹部ｕの底部ｕ1 から傾斜面ｓ等の滑らかな形状により可動シーブ側に所定間隔ｖ離れた位置において軸部１ａの外周面ｐに接続している。
【００２４】
上記傾斜面ｓの途中において、前記潤滑油用横油路３ｂが開口ａしており、該横油路３ｂは、上記延長部となる傾斜面ｓの接点までの長さｖより短い間隔（ｌ＜ｖ）にて形成されており、かつ上記固定シーブ傾斜面１ｃの根本部１ｄから所定間隔ｌ離れた位置に配置されている。従って、可動シーブ２が、図２及び図３に示すように、固定シーブ１に近接してベルト有効径が最大又は最大に近い状態になった場合、可動シーブ２は、上記横油路３ｂとオーバラップする状態になる。なお、可動シーブ２のボス部の固定シーブ側内周面ｉは、固定シーブ軸部１ａの径より僅かに大きい直線状の面からなり、軸部外周面ｐと対接する形状からなる。
【００２５】
ついで、上記プーリ装置Ｐの作用について説明するに、固定シーブ１の傾斜面１ｃは、凹部ｕの存在により、略々根本部１ｄ（ｑ）まで正確に形成することが可能となり、金属ベルト２０が固定シーブ軸部１ａに略々接触するまで移動でき、ベルト最小有効径を限度近傍まで設定し得ると共に、図２及び図３に示すように、可動シーブ２を固定シーブの傾斜面１ｃに略々接触するまで移動して、ベルト最大有効径を限定近傍まで設定して、最大の変速比を得ることが可能となる。
【００２６】
そして、ベルト最大有効径近傍にあっては、ベルトとシーブ当接面の周長も長くなり、かつ高速回転状態となるので、潤滑油の供給量も必要量も多くなり、かつこの状態では、所定間隔ｌ離れて設置されている潤滑油用横油路３ｂの開口ａは、可動シーブ２がオーバラップした位置となる。この状態にあっても、横油路３ｂからの潤滑油は、開口ａから、軸部１ａの傾斜ｓとボス部内周面ｉとの所定間隔ｃを通って、シーブ傾斜面１ｃ，２ｃに導かれ、プーリ装置の回転に基づく遠心力により、金属ベルト２０とシーブ傾斜面１ｃ，２ｃとの当接・挟持面に供給される。これにより、金属同士でありかつ大きな挟圧力の作用するベルトとシーブ傾斜面との当接面に、確実に潤滑油が介在されて、支障なく動力伝達が行われる。
【００２７】
また、フランジ形状の両シーブ１，２は、油圧室１３からの大きな軸力が作用して、ベルト２０を挟圧しているため、シーブ、特に固定シーブ１の傾斜面１ｃの根本部分から１ｄに大きな荷重が集中して作用するが、該根本部分から所定間隔ｌ離れて上記潤滑油用油路３ｂが配置されているので、該横油路３ｂが、上記荷重集中部分から離れて配置されることになり、強度上有利な構成となっている。更に、上記根本部１ｄに隣接して軸部に形成される凹部は、アール形状ｒ及び傾斜面ｓからなる滑らかな形状からなるので、切欠き効果を抑えて、強度上有利な構造になっている。
【００２８】
また、上記凹部ｕ及び傾斜面ｓは、軸部１ａの全周に亘り形成されており、可動シーブ２が固定シーブ１に近接して、ボス部内周面ｉと上記傾斜面ｓとの間隙ｃが小さくなっても、横油路３ｂからの潤滑油流量は、全周に亘りかつ末広がり状態となる上記間隙ｃにより絞られることなく流されて、上述したように供給量及び必要量も多くなっている潤滑油量を確実にベルト当接面に供給し得る。
【００２９】
なお、上記傾斜面ｓは、全周に形成されていなくとも、上記横油路３ｂの流量にみあった所定幅からなる凹溝が、上記開口ａを中心に所定周方向幅で配置され、残りは、軸部１ａの外周面ｐとなるようにしてもよい。更に、上記傾斜面ｓを、可動シーブ２の内周面ｉ部分に形成してもよく、要は、可動シーブ２が横油路３ｂの開口ａにオーバラップした状態で、該開口ａから、ベルト当接面である両シーブ傾斜面１ｃ，２ｃに導かれる間隙ｃが形成されるような構成であればよい。
【図面の簡単な説明】
【図１】本発明を適用したプーリ装置を示す正面断面図。
【図２】その固定シーブ及び可動シーブを示す正面断面図。
【図３】本発明の要部を示す拡大断面図。
【図４】従来の技術による図２と同様な図。
【図５】他の従来の技術による図２と同様な図。
【符号の説明】
１ 固定シーブ
１ａ 軸部
１ｃ 傾斜面
１ｄ 根本部
２ 可動シーブ
２ｃ 傾斜面
３ａ，３ｂ 潤滑油用油路
ａ 開口
ｃ 所定間隙
ｕ 凹部
ｕ1 底面
ｓ 傾斜面
ｐ 固定シーブ外周面
ｉ 可動シーブ内周面
ｌ 所定間隔
Ｐ プーリ装置[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pulley apparatus, and more particularly to a pulley apparatus suitable for application to a continuously variable transmission (CVT) mounted on an automobile, and more particularly to an oil passage structure for supplying lubricating oil to a belt contact surface of the pulley apparatus. .
[0002]
[Prior art]
In general, as shown in FIGS. 4 and 5, the pulley device supports the movable sheave 2 slidably on the shaft portion 1 a of the fixed sheave 1, and the sheaves 1 and 2 rotate together by a ball spline or the like. It is configured as follows. Lubricating oil is supplied to the belt contact surfaces 1c and 2c of the sheaves 1 and 2 through the vertical oil passage 3a and the lateral oil passage 3b formed in the fixed sheave shaft portion 1a.
[0003]
Conventionally, the lubricating oil supply oil passage, in particular the lateral oil passage 3b, is formed so as to open toward the root portion 1d of the inclined surface (belt contact surface) 1c of the fixed sheave 1 as shown in FIG. ing. Further, as shown in FIG. 5, the opening a of the lateral oil passage 3b is disposed at a position separated from the inclined surface root portion 1d of the fixed sheave 1 by a predetermined distance l.
[0004]
[Problems to be solved by the invention]
In the pulley device, a strong clamping force acts between the inclined surfaces (belt contact surfaces) 1c, 2c of the sheave and the belt, and torque is transmitted by the frictional force between the belt and the sheave. A strong axial force is applied to the sheaves 1 and 2. And since the said axial force and torque act between the belt contact surface and belt of a sheave, a big load acts on the sheave, especially the shaft root part 1d of the inclined surface 1c of the fixed sheave 2. .
[0005]
As shown in FIG. 4 described above, the horizontal oil passage 3b that faces the fixed sheave inclined surface root portion 1d has a plurality of horizontal oil passages 3b on the sheave root portion 1d on which a large concentrated load acts as described above. Will be located radially, which is a disadvantageous structure.
[0006]
Further, when the inclined surface 1c that is the belt contact surface of the fixed sheave 1 is formed, a groove 1e for lowering is often formed in the root portion 1d. In this case, the horizontal oil passage 3b is formed by the groove The opening a is formed at 1e, and the structure is further disadvantageous in terms of strength.
[0007]
Further, as shown in FIG. 5, in the case where the horizontal oil passage 3b is arranged at a predetermined interval l from the fixed sheave inclined surface root portion 1d, as described above, the disadvantage in strength is eliminated, but the movable sheave When the effective diameter of the belt 2 is approaching the fixed sheave 1 and the effective diameter of the belt is large, if the inner peripheral surface i of the movable sheave 2 covers the opening a of the lateral oil passage 3b separated by the predetermined distance, the lateral oil passage 3b As a result, the belt contact surface becomes poorly lubricated. In this type of pulley device, the metal belt and the sheave contact surface come into contact with each other on the basis of the large clamping pressure of the sheave to transmit torque, and the contact surface between the metals always requires the intervention of lubricating oil. Therefore, it is necessary to regulate the amount of movement of the movable sheave 2 to the extent that the movable sheave 2 does not block the opening a of the lateral oil passage 3b.
[0008]
Therefore, in the pulley apparatus shown in FIG. 5, the maximum effective radius of the belt is restricted, and the speed ratio of the pulley apparatus is limited.
[0009]
Therefore, the present invention enables the supply of lubricating oil even when the movable sheave is brought close to the fixed sheave while the lubricating oil supply lateral oil passage is arranged at a predetermined distance from the fixed sheave root. An object of the present invention is to provide a pulley apparatus that solves the above-described problems.
[0010]
[Means for Solving the Problems]
The present invention includes a fixed sheave (1) and a movable sheave (2) slidably supported on a shaft portion (1a) of the fixed sheave, and both inclined surfaces (1c) of the fixed sheave and the movable sheave. , 2c) and an oil passage (3a, 3b) formed in the shaft portion (1a) of the fixed sheave so as to supply the lubricating oil to the contact portion of the belt. In the pulley apparatus formed by opening (a) in the outer peripheral surface of the shaft portion,
With the movable sheave (2) approaching the fixed sheave (1), the oil passage opening (a) is arranged at a position where the movable sheave overlaps,
In the overlapping state, a predetermined gap (c) is formed between the outer peripheral surface (s) of the fixed sheave shaft portion (1a) and the inner peripheral surface (i) of the movable sheave, Led from the opening through the predetermined gap (c) to the contact portion,
In the pulley device.
[0011]
The overlap includes a state in which at least a part of the opening overlaps the movable sheave in the axial direction.
[0012]
And the fixed sheave side inner peripheral surface (i) of the movable sheave is formed by a linear surface that contacts the outer peripheral surface (p) of the shaft portion of the fixed sheave,
The root portion (1d) of the inclined surface (1c) of the fixed sheave (1) has a concave portion (u) and the concave portion is extended to the movable sheave side by a predetermined length, and the opening is formed in the extended portion (s). (A) is arranged.
[0013]
Further, a concave portion (u) made of, for example, a round shape (r) is formed over the entire circumference in the root portion (1d) of the inclined surface (1c) of the fixed sheave, and the movable portion is moved from the bottom surface (u 1 ) of the concave portion. An inclined surface (s) that faces the outer peripheral surface (p) of the fixed sheave shaft that is in contact with the inner peripheral surface of the sheave is formed over the entire circumference.
The opening (a) is arranged in the middle of the inclined surface (s).
[0014]
In addition, although the code | symbol in the said parenthesis is for contrast with drawing, it does not have any influence on the structure of a claim by this.
[0015]
【The invention's effect】
According to the present invention, the lubricating oil supply oil passage is disposed at a position where the opening thereof overlaps the movable sheave and is disposed at a predetermined distance from the root portion of the inclined surface of the fixed sheave. Even if the movable sheave overlaps the opening, the lubricating oil from the opening is guided to the belt contact portion through a predetermined gap, so that the belt contact portion becomes poorly lubricated. The movable sheave can be slid until it comes close to the fixed sheave, and the maximum effective diameter of the belt can be secured. Together, this ensures a predetermined strength of the shaft portion and the maximum effective diameter of the belt, and is compact. A pulley device having the configuration can be obtained.
[0016]
Further , a concave portion is provided at the base of the inclined surface of the fixed sheave, and the inclined surface can be accurately formed up to the vicinity of the shaft portion extension (see q in FIG. 3), and in the fixed sheave side of the movable sheave. Since the circumferential surface is a straight surface, the belt can be moved to the vicinity where it contacts the fixed sheave shaft portion, and the minimum effective diameter of the belt can be secured and the gear ratio can be increased. By forming an opening in the extension of the recess, the lubricating oil can be reliably supplied with a simple configuration.
[0017]
Further, for example, the concave portion is formed in a round shape and the inclined surface is formed from the bottom surface of the concave portion, so that the concave portion and the inclined surface are formed smoothly on the whole, reducing the notch effect, and disadvantageous in strength. In addition, since an opening is provided in the middle of the inclined surface over the entire circumference, even if the gap between the inclined surface and the inner surface of the movable sheave is small, the entire circumference is spread over the inclined surface. A sufficient amount of lubrication corresponding to the fact that the maximum effective diameter of the belt is required and a large amount of lubricating oil is required to flow without substantially reducing the amount of oil from the lubricating oil passage. Oil can be supplied.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing a pulley device of a belt transmission device (CVT) to which the present invention is applied, more specifically, a pulley device on a primary side (drive source side of an engine or the like), and the pulley device P is a fixed sheave 1 And a movable sheave 2. Each of the fixed sheave and the movable sheave has a flange shape having inclined surfaces 1c and 2c that are inclined in directions in which opposing surfaces expand in the outer diameter direction, and the fixed sheave 1 has a shaft portion 1a that extends in the movable sheave direction. Have.
[0019]
A boss portion 2a of the movable sheave 2 is slidably supported on the outer peripheral surface of the shaft portion 1a, and in the axial direction on the outer peripheral surface of the fixed sheave shaft portion 1a and the inner peripheral surface of the movable sheave boss portion 2a. Three extending concave grooves 5 and 6 are formed, and a plurality of balls 7 are filled in the opposing concave grooves to form a ball spline 8. The movable sheave 2 includes the ball splines. 8 is supported by the fixed sheave 1 so as to be movable in the axial direction and non-rotatable. In addition, snap rings 9 and 10 are attached to the outer end portion of the boss-side recess 5 and the inner end portion of the shaft-side recess 6 in the circumferential direction, so that the ball 7 falls off. Is preventing.
[0020]
Further, a flange 11 serving as a cylinder is disposed on the back surface of the movable sheave 2, and a shaft between the flange 11 and the distal end 2 e of the movable sheave 2 is sealed with an oil seal 12 to form a hydraulic chamber 13. ing. The flange 11 is fixed to the shaft portion 1a via a bearing 16 and a washer 17 by screwing a nut 15 into a screw portion formed at the tip of the fixed sheave shaft portion 1a. The pulley device P is supported by the case at the rear side thereof by the bearing 16 and at the front end side by a bearing (not shown) mounted on the outer peripheral surface of the flange 1e on the back of the fixed sheave.
[0021]
Further, the fixed sheave shaft portion 1a is formed with an oil hole 17 from the rear end side, and the oil hole is connected to the hydraulic pressure via the lateral oil holes 17a and 17b formed in the shaft portion 1a and the boss portion 2a. The hydraulic pressure communicated with the chamber 13 and switched to the control valve is supplied from the case to the hydraulic chamber 13 through the oil holes 17, 17a, 17b, and controls the axial position of the movable sheave 2. The secondary pulley device is also supplied with hydraulic pressure corresponding to the transmission torque by the hydraulic device, and the metal belt 20 is sandwiched between the two pulley devices P, and the pulley device P is interposed between the pulley devices via the metal belt 20. Torque is transmitted. Further, when the movable sheave 2 slides, the effective diameter of the metal belt 20 changes and the gear is shifted.
[0022]
On the other hand, a vertical oil passage 3a for lubricating oil is formed to open to the front end side of the fixed sheave shaft portion 1a, and a transverse oil passage 3b is formed radially at the tip portion of the oil passage 3a. These lateral oil passages are opened a on the outer peripheral surface of the shaft portion 1a. Further, a forward / reverse switching device or the like (not shown) is disposed on the back side of the fixed sheave 1, and an inner diameter spline of the rear flange portion 1 e is supplied from a driving source such as an engine via the forward / backward switching device. The power is transmitted through. An input shaft or the like is fitted in the vertical oil passage 3a in an oil-tight manner, and lubricating oil is supplied through the oil passage of the input shaft.
[0023]
As shown in detail in FIGS. 2 and 3, the intersecting portion between the inclined surface 1 c of the fixed sheave 1 and the shaft portion 1 a, that is, the inclined surface side root portion 1 d of the fixed sheave is formed with a concave portion u due to the rounded shape r. Further, an inclined surface s having a predetermined inclination angle θ extends from the bottom u 1 of the concave portion u toward the outer peripheral surface p of the shaft portion 1 a to constitute a concave extension portion. Therefore, the inclined surface root portion of the fixed sheave 1 has an inclined surface 1c serving as a belt contact surface extending to an outer peripheral surface extending portion q of the shaft portion 1a, and is recessed from there with a smooth shape such as a round shape r. cage, connected to the outer peripheral surface p of the shaft portion 1a at the position further apart a predetermined distance v to the movable sheave side by the smooth shape such as the inclined surfaces s from the bottom u 1 of the recess u.
[0024]
In the middle of the inclined surface s, the lateral oil passage 3b for the lubricating oil has an opening a, and the lateral oil passage 3b has an interval (l shorter than the length v to the contact point of the inclined surface s serving as the extension portion. <V) and arranged at a position spaced apart from the root 1d of the fixed sheave inclined surface 1c by a predetermined distance l. Accordingly, as shown in FIGS. 2 and 3, when the movable sheave 2 comes close to the fixed sheave 1 and the effective belt diameter becomes maximum or close to the maximum, the movable sheave 2 is connected to the horizontal oil passage 3b. It will be in the state of overlapping. The fixed sheave side inner peripheral surface i of the boss portion of the movable sheave 2 is a straight surface slightly larger than the diameter of the fixed sheave shaft portion 1a, and has a shape in contact with the outer peripheral surface p of the shaft portion.
[0025]
Next, the operation of the pulley device P will be described. The inclined surface 1c of the fixed sheave 1 can be accurately formed up to substantially the root portion 1d (q) due to the presence of the concave portion u. The belt can move until it substantially contacts the fixed sheave shaft portion 1a, and the belt minimum effective diameter can be set up to the limit. It moves until it contacts, and it becomes possible to set the maximum effective diameter of the belt to the vicinity of the limit and obtain the maximum gear ratio.
[0026]
And in the vicinity of the maximum effective diameter of the belt, the circumference of the belt and the sheave contact surface also becomes longer and the high speed rotation state, so the amount of lubricating oil supplied and the required amount increase, and in this state, The opening a of the lubricating oil lateral oil passage 3b installed at a predetermined interval l is a position where the movable sheave 2 overlaps. Even in this state, the lubricating oil from the lateral oil passage 3b is guided from the opening a to the sheave inclined surfaces 1c and 2c through the predetermined interval c between the inclined portion s of the shaft portion 1a and the inner peripheral surface i of the boss portion. In addition, the metal belt 20 and the sheave inclined surfaces 1c and 2c are supplied to the abutting / clamping surfaces by centrifugal force based on the rotation of the pulley device. As a result, the lubricating oil is reliably interposed on the contact surface between the belt and the sheave inclined surface, which are made of metal and on which a large clamping pressure acts, and power transmission is performed without any trouble.
[0027]
Further, since both of the flange-shaped sheaves 1 and 2 are subjected to a large axial force from the hydraulic chamber 13 to pinch the belt 20, the sheave, particularly from the root portion of the inclined surface 1c of the fixed sheave 1 to 1d. Although a large load acts in a concentrated manner, since the lubricating oil passage 3b is disposed at a predetermined interval l from the root portion, the lateral oil passage 3b is disposed away from the load concentration portion. That is, the structure is advantageous in terms of strength. Further, the recess formed in the shaft portion adjacent to the root portion 1d has a smooth shape composed of the rounded shape r and the inclined surface s, so that the notch effect is suppressed and the structure is advantageous in terms of strength. Yes.
[0028]
Further, the concave portion u and the inclined surface s are formed over the entire circumference of the shaft portion 1a, and the movable sheave 2 is close to the fixed sheave 1 so that the gap c between the boss portion inner peripheral surface i and the inclined surface s. However, the flow rate of the lubricating oil from the lateral oil passage 3b flows without being throttled by the gap c that is in a divergent state over the entire circumference, and the supply amount and the necessary amount increase as described above. It is possible to reliably supply the lubricating oil amount to the belt contact surface.
[0029]
In addition, even if the inclined surface s is not formed on the entire circumference, a concave groove having a predetermined width corresponding to the flow rate of the lateral oil passage 3b is disposed with a predetermined circumferential width around the opening a, The remainder may be the outer peripheral surface p of the shaft portion 1a. Further, the inclined surface s may be formed on the inner peripheral surface i portion of the movable sheave 2. In short, in a state where the movable sheave 2 overlaps the opening a of the lateral oil passage 3b, from the opening a, Any structure may be used as long as the gap c guided to both the sheave inclined surfaces 1c and 2c, which are belt contact surfaces, is formed.
[Brief description of the drawings]
FIG. 1 is a front sectional view showing a pulley apparatus to which the present invention is applied.
FIG. 2 is a front sectional view showing the fixed sheave and the movable sheave.
FIG. 3 is an enlarged sectional view showing a main part of the present invention.
4 is a view similar to FIG. 2 according to the prior art.
FIG. 5 is a view similar to FIG. 2 according to another conventional technique.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Fixed sheave 1a Shaft part 1c Inclined surface 1d Root part 2 Movable sheave 2c Inclined surface 3a, 3b Oil passage a for lubricating oil Opening c Predetermined gap u Recess u 1 Bottom surface s Inclined surface p Fixed sheave outer peripheral surface i Movable sheave inner peripheral surface l Predetermined interval P Pulley device

Claims (2)

固定シーブと、該固定シーブの軸部に摺動自在に支持された可動シーブと、を備え、前記固定シーブ及び可動シーブの両傾斜面にベルトを当接して挟持すると共に、該ベルトの当接部分に潤滑油を供給すべく、前記固定シーブの軸部に形成された油路が該軸部の外周面に開口してなるプーリ装置において、
前記可動シーブの固定シーブ側内周面は、前記固定シーブの軸部の外周面と対接する直線状の面にて形成され、
前記可動シーブが前記固定シーブに接近した状態で、前記油路の開口を、前記可動シーブがオーバラップする位置に配置し、
前記固定シーブにおける前記傾斜面の根本部に凹部を全周に亘り形成し、該凹部の底面から前記可動シーブの内周面に対接する固定シーブ軸部外周面に向かう傾斜面を全周に亘って形成し、
該傾斜面の途中に前記開口を配置して、前記オーバラップする状態において、前記潤滑油を、前記開口から、前記固定シーブ軸部の外周面に形成された前記傾斜面及び前記凹部と前記可動シーブの内周面との間の所定間隙を通って前記当接部分に導くことを特徴とする、
プーリ装置。A fixed sheave and a movable sheave supported slidably on the shaft portion of the fixed sheave, and abutting and sandwiching the belt on both inclined surfaces of the fixed sheave and the movable sheave; In a pulley apparatus in which an oil passage formed in a shaft portion of the fixed sheave is opened on an outer peripheral surface of the shaft portion in order to supply lubricating oil to a portion,
The fixed sheave side inner peripheral surface of the movable sheave is formed by a linear surface that is in contact with the outer peripheral surface of the shaft portion of the fixed sheave,
With the movable sheave approaching the fixed sheave, the opening of the oil passage is arranged at a position where the movable sheave overlaps,
A concave portion is formed in the root portion of the inclined surface of the fixed sheave over the entire circumference, and an inclined surface extending from the bottom surface of the concave portion to the outer peripheral surface of the fixed sheave shaft portion that contacts the inner peripheral surface of the movable sheave is extended over the entire circumference. Formed,
In the state where the opening is arranged in the middle of the inclined surface and overlaps, the lubricating oil is moved from the opening to the inclined surface and the recess formed on the outer peripheral surface of the fixed sheave shaft portion and the movable member. and wherein the lead to the contact portion through the predetermined distance gap between the inner peripheral surface of the sheave,
Pulley device. 前記凹部が、アール形状からなる、
請求項１記載のプーリ装置。 The concave portion has a round shape,
The pulley apparatus according to claim 1.
JP2001395295A 2001-12-26 2001-12-26 Pulley device Expired - Fee Related JP3972652B2 (en)

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CN101868635A (en) 2007-11-21 2010-10-20 罗伯特·博世有限公司 Shaft-and-flange component for a pulley of a continuously variable transmission
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