JP3730638B2

JP3730638B2 - Torque milita

Info

Publication number: JP3730638B2
Application number: JP2003176758A
Authority: JP
Inventors: 茂實日高
Original assignee: Yanma Agricultural Equipment Co Ltd
Current assignee: Yanma Agricultural Equipment Co Ltd
Priority date: 2003-06-20
Filing date: 2003-06-20
Publication date: 2006-01-05
Anticipated expiration: 2023-02-25
Also published as: JP2004257550A

Description

【０００１】
【発明の属する技術分野】
本発明は例えば左右一対の走行クローラを装設して移動するコンバインまたはトラクタまたは建設車輌などに用いるトルクリミッタに関する。
【０００２】
【従来の技術】
従来、トルクリミッタとしてトルクローラを設ける技術がある。（例えば、特許文献１参照）
【０００３】
【特許文献１】
特開２００２−６１６６６号公報
【０００４】
【発明が解決しようとする課題】
前記従来技術は、トルクローラを転動させながら滑り摩擦を発生させる一方、入出力の回転トルク差が増大してトルクローラの摩擦抵抗力よりも大きくなることにより、トルクローラが摺動して伝達動力を遮断させていたが、複数のトルクローラに対して潤滑油が不均一に供給されることによってトルクローラの伝達トルクが変動したり、潤滑油の不足によってトルクローラが焼損する等の不具合がある。
【０００５】
【課題を解決するための手段】
そこで、本発明では、筒形のアウタケース内において、同アウタケース中に挿通した伝動軸に、複数のドーナツ板形の内板とトルク板と外板とを多層状にして同軸的に配置し、トルク板には、同一円周上に複数のトルクローラを配列すると共に、同トルク板の両側面にトルクローラの外周面を突出させて内板と外板に摺接させ、内板は伝動軸に係合させる一方、外板はアウタケースに係合させて、トルクローラを転動させながら滑り摩擦を発生させるようにし、伝動軸に油穴を形成すると共に、同油穴の一端を伝動軸の周面に開口させ、かつ、前記内板の内孔に油通し用の切欠を形成して、伝動軸の回転によって発生する遠心力により、上記油孔及び油通し用の切欠を通して油を多層状に配置した各トルク板のトルクローラ方向に移動させ、遠心力によってトルクローラを強制潤滑することを特徴とするトルクリミッタを提供するものである。
【０００６】
【発明の実施の形態】
以下、本発明の実施例を図面に基づいて詳述する。図１はコンバインの全体の斜視図、図２は同右側面図であり、図中１は左右一対の走行クローラ２を装設する左右一対のトラックフレーム、３は前記の左右トラックフレーム１に架設する機台、４はフィードチェン５を左側に張架し扱胴６及び処理胴を内蔵している脱穀機である脱穀部、７は引起機構８及び刈刃９及び穀稈搬送機構１０などを備える刈取部、１１は刈取フレーム１２を介して刈取部７を昇降させる油圧昇降シリンダ、１３は排藁チェン１４終端を臨ませる排藁処理部、１５は脱穀部４からの穀粒を揚穀筒を介して搬入する穀物タンク、１６・１７は前記タンク１５の穀粒を機外に搬出する排出オーガ、１８は運転操作ハンドル１９及び運転席２０を備える運転キャビン、２１は運転キャビン１８下方に設けるエンジンであり、連続的に穀稈を刈取って脱穀するように構成している。
【０００７】
さらに、図３乃至図７に示す如く、機台３前側で左右の走行クローラ２の間にミッションケース２２を配設させ、ミッションケース２２とエンジン２１を略直列に前後に設け、ミッションケース２２を介して走行クローラ２にエンジン２１の駆動力を伝えると共に、脱穀部４前側の機台３上面に左右の支持台２３・２４を立設させ、支持台２３・２４に刈取フレーム１２を介して刈取部７を昇降自在及び横移動可能に設ける。また、支持台２３・２４後側の機台３上面にカウンタケース２５を設け、脱穀部４及び刈取部７にカウンタケース２５を介してエンジン２１の駆動力を伝える。
【０００８】
さらに、ミッションケース２２側方の機台３にキャビン前フレーム２６を立設させ、キャビン１８のステップフレーム２７前部を前フレーム２６上部に回動支点軸２８を介して設け、支点軸２８回りにキャビン１８を前方に回動自在に支持させると共に、右の支持台２４に左のキャビン後フレーム２９を立設させ、機台３に立設させる右のキャビン後フレーム３０との間の機台３上面にエンジン２１を設け、エンジン２１をエンジンルームカバー３１で覆う。また、前記カバー３１の上方で左右の後フレーム２９・３０上部をキャビン横フレーム３２によって連結させ、キャビン横フレーム３２にフックレバー３３を設け、キャビン１８のステップフレーム２７後部を横フレーム３２に上載させてフックレバー３３により係脱自在に固定させると共に、右の支持台２４と前フレーム２６の間に水平連結フレーム３４を固定させ、水平連結フレーム３４中間と横フレーム３２中間に傾斜連結フレーム３５を固定させ、連結フレーム３４・３５によってフレーム剛性を確保する。また、左の後フレーム２９にオーガ支柱３６を連結させて上側にオーガレスト３７を設け、昇降及び旋回自在に設ける排出オーガ１７をオーガレスト３７の本機収納位置に支持させる。
【０００９】
さらに、図８乃至図１２に示す如く、前記走行クローラ２を駆動するミッションケース２２は、１対の油圧走行ポンプ３８及び油圧走行モータ３９を設けて走行主変速用の油圧式無段変速機構を形成する走行変速部材４０と、１対の油圧旋回ポンプ４１及び油圧旋回モータ４２を設けて旋回用の油圧式無段変速機構を形成する旋回部材４３とを備え、前記エンジン２１の出力軸４４にミッションケース２２の入力軸４５を介して連結させて前記各ポンプ３８・４１を駆動するように構成している。
【００１０】
また、前記走行モータ３９のモータ軸４６に、副変速機構４７及び差動機構４８を介して左右走行クローラ２の各駆動輪４９を連動連結させるもので、前記差動機構４８は左右対称の１対の遊星ギヤ機構５０を有し、各遊星ギヤ機構５０は１つのサンギヤ５１と、該サンギヤ５１の外周で噛合う３つのプラネタリギヤ５２と、これらプラネタリギヤ５２に噛合うリングギヤ５３などで形成している。
【００１１】
前記プラネタリギヤ５２は、サンギヤ５１の遊転軸５４と同軸線上の車軸５５のキャリヤ５６にそれぞれ回転自在に軸支させ、左右のサンギヤ５１を挾んで左右のキャリヤ５６を対向配置させると共に、前記リングギヤ５３は各プラネタリギヤ５２に噛み合う内歯を有して車軸５５に回転自在に軸支させ、車軸５５を延設して駆動輪４９を軸支させている。
【００１２】
また、走行変速部材４０は、走行ポンプ３８の斜板角度の変更により走行モータ３９の正逆回転と回転数の制御を行うもので、走行モータ３９の回転を、モータ軸４６と副変速機構４７の低速及び高速ギヤ５７・５８とブレーキ軸５９と分岐軸６０を介して、左右のリングギヤ５３に伝達して左右のキャリヤ５６を回転させるように構成している。また前記ブレーキ軸５９に駐車ブレーキ６１を設けると共に、刈取部７に回転力を伝達する刈取駆動プーリ６２を前記モータ軸４６に設け、刈取部７を車速同調速度で駆動させる。
【００１３】
上記のように、前記分岐軸６０を介しリングギヤ５３に伝達された走行モータ３９の駆動力を、左右の遊星ギヤ機構５０を介して左右キャリヤ５６に伝達させると共に、左右キャリヤ５６に伝達された回転を左右の駆動輪４９にそれぞれ伝え、左右走行クローラ２を同一方向に同一速度で駆動するように構成している。
【００１４】
さらに、旋回用の油圧式無段変速機構で形成する旋回部材４３は、旋回ポンプ４１の斜板角度の変更により旋回モータ４２の正逆回転と回転数の制御を行うもので、操向出力ブレーキ６３を設けるモータ軸６４と、操向出力クラッチ６５を設けるクラッチ軸６６と、前記の左右サンギヤ５１に常時噛合させる左右入力ギヤ６７・６８を設け、旋回モータ４２の出力用の前記モータ軸６４及び操向出力クラッチ６５を介してクラッチ軸６６を連結させ、クラッチ軸６６に正転ギヤ６９及び逆転ギヤ７０を介して左右の入力ギヤ６７・６８を連結させる。そして、右側のサンギヤ５１に正転ギヤ６９を介してモータ４２回転力を伝え、また左側のサンギヤ５１に逆転ギヤ７０を介してモータ４２回転を伝え、旋回モータ４２を正転（逆転）時、左右同一回転数で、左サンギヤ５１を逆転（正転）させ、かつ右サンギヤ５１を正転（逆転）させ、左右走行クローラ２を逆方向に同一速度で駆動するように構成している。
【００１５】
而して、旋回モータ４２を停止させて左右サンギヤ５１を静止固定させた状態で、走行モータ３９を駆動すると、走行モータ３９の回転は左右のリングギヤ５３に同一回転数で伝達され、左右遊星ギヤ機構５０のキャリヤ５６を介して左右の走行クローラ２が左右同一回転方向で同一回転数によって駆動され、機体の前後方向直進走行が行われる。一方、走行モータ３９を停止させて左右のリングギヤ５３を静止固定させた状態で、旋回モータ４２を正逆回転駆動すると、左側の遊星ギヤ機構５０が正或いは逆回転、また右側の遊星ギヤ機構５０が逆或いは正回転し、左右走行クローラ２を逆方向に駆動し、機体を左或いは右に旋回させる。また、走行モータ３９を駆動させながら、旋回モータ４２を駆動することにより、機体が左右に旋回して進路が修正されるもので、機体の旋回半径は旋回モータ４２の出力回転数によって決定される。
【００１６】
また、前記入力軸４５にファン軸７１を連結させ、ファン軸７１によってエンジン２１水冷用のラジエータの冷却ファン７２を駆動させると共に、前記の走行及び旋回ポンプ３８・４１の各ポンプ軸７３・７４にギヤ群７５を介して前記ファン軸７１を連結させ、各ポンプ３８・４１に入力軸４５を連結させると共に、走行ポンプ３８のポンプ軸７３と、走行モータ３９のモータ軸４６を、車速定速クラッチ７６を介して連結させる定速軸７７を設け、車速定速クラッチ７６を入にしたとき、定速軸７７を介してポンプ軸７３とモータ軸４６をギヤ連結させ、走行変速部材４０を介することなく、入力軸４５の回転を副変速機構４７に伝え、エンジン２１の定速回転によって左右の走行クローラ２を駆動させ、略一定の車速で走行して収穫作業などを行わせる。なお、旋回ポンプ軸７４上にチャージポンプ７８を設けて駆動する。
【００１７】
さらに、図１２に示す如く、走行ポンプ３８の斜板７９角度を変更して出力調整する主変速シリンダ８０と、主変速レバー８１及び操向ハンドル１９に連結させて切換える変速バルブ８２と、走行ポンプ３８出力を一定量減速するバルブ８３を設け、前記チャージポンプ７８を各バルブ８２・８３を介して主変速シリンダ８０に油圧接続させるもので、主変速レバー８１によって変速バルブ８２を切換え、主変速シリンダ８０を作動させて走行ポンプ３８の斜板７９角度を変更させ、走行モータ３９のモータ軸４６の回転数を無段階に変化させたり、逆転させる走行変速動作を行わせ、また前記斜板７９の角度調節動作によって変速バルブ８２が中立復帰するフィードバック動作を行わせ、主変速レバー８１の操作量に比例させて前記斜板７９角度を変化させ、走行モータ３９の回転数を変化させて車速を変更させる。
【００１８】
また、走行モータ３９の斜板８４角度を変更して出力調整する副変速シリンダ８５を設け、前記チャージポンプ７８に電磁副変速バルブ８６を介して副変速シリンダ８５を油圧接続させ、副変速バルブ８６が中立のときに副変速シリンダ８５を油タンクであるミッションケース２２に短絡させ、走行モータ３９の斜板８４角度を主回路油圧によって変化させると共に、副変速バルブ８６の切換によって斜板８４角度を強制的に変化させ、走行モータ３９の出力を高速または低速に変更させる。
【００１９】
さらに、旋回ポンプ４１の斜板８７角度を変更して出力調整する旋回シリンダ８８を設け、操向ハンドル１９及び主変速レバー８１に連結させて切換える旋回バルブ８９並びに電磁自動操向バルブ９０を介してチャージポンプ７８を旋回シリンダ８８に油圧接続させ、操向ハンドル１９によって旋回バルブ８９を切換え、旋回シリンダ８８を作動させて旋回ポンプ４１の斜板８７角度を変更させ、旋回モータ４２のモータ軸６４の回転数を無段階に変化させたり、逆転させる左右旋回動作を行わせ、また前記斜板８７の角度調節動作によって旋回バルブ８９が中立復帰するフィードバック動作を行わせ、操向ハンドル１９の操作量に比例させて前記斜板８７角度を変化させ、旋回モータ４２の回転数を変化させて左右旋回角度を変更させる。
【００２０】
また、主変速レバー８１が中立以外の位置に操作され、操向ハンドル１９が直進以外に操作されることにより、主変速レバー８１の操作方向と操作量に比例させて走行ポンプ３８の油圧出力を増減させ、油圧モータ３９を正逆転または増減速させて前後進速度（車速）を変更させると共に、主変速レバー８１の操作量に比例させて旋回ポンプ４１出力を変化させるもので、高速側走行変速によって旋回半径を自動的に小さくし、かつ低速側走行変速によって旋回半径を自動的に大きくし、操向ハンドル１９の一定操作によって走行速度に関係なく左右走行クローラ２の旋回半径を略一定に維持させ、作業走行速度の変更並びに未刈り穀稈列などに機体を沿わせる進路修正などを行わせる。一方、操向ハンドル１９の操作量に比例させて各バルブ８２・８９の制御により旋回ポンプ４１出力と走行ポンプ３８出力を変化させ、旋回半径（操舵角）を小さく（大きく）したとき、走行速度（車速）を比例させて減速させ乍ら、左右の走行クローラ２の速度差を大きくし、左右に旋回させるもので、左右走行クローラ２の駆動速度を変更して条合せ進路修正並びに圃場枕地でのスピンターンによる方向転換を行い、連続的に穀稈を刈取って脱穀する収穫作業を行う。なお、主変速レバー８１が中立のとき、操向ハンドル１９の操作に関係なく、旋回バルブ８９が中立維持され、旋回ポンプ４１の油圧出力が略零に保たれ、旋回モータ４２を停止させる。
【００２１】
さらに、図１１乃至図１８に示す如く、前記エンジン２１の出力軸４４を前側及び後側に突設させ、出力軸４４の前側に前記入力軸４５を連結させ、出力軸４４の後側に作業出力プーリ９１を設けると共に、エンジン２１の左側で脱穀部４前側の機台３上面にカウンタケース２５を設け、入力プーリ９２、車速同調プーリ９３、脱穀プーリ９４、刈取プーリ９５、選別プーリ９６をカウンタケース２５に軸支させ、ケース２５後側の入力プーリ９２を作業出力プーリ９１にテンション脱穀クラッチ９７を介してベルト９８連結させ、エンジン２１の駆動力をカウンタケース２５に伝える。また、右支持台２４前側のアイドルプーリ９９を介してミッションケース２２の刈取駆動プーリ６２に前記カウンタケース２５右側の車速同調プーリ９３をベルト１００連結させると共に、機台３の前側上面に立設させる支持台２３・２４に刈取入力ケース１０１を回転自在に軸支させ、前記ケース１０１に刈取フレーム１２を連結させてケース１０１回りに刈取部７を回転させて昇降させるもので、前記ケース１０１左側に刈取入力軸１０２を介して刈取入力プーリ１０３を軸支させ、前記カウンタケース２５左側の刈取プーリ９５を刈取入力プーリ１０３にベルト１０４連結させ、刈取部７の各部に駆動力を伝える。
【００２２】
また、前記扱胴６の駆動入力プーリ１０５にカウンタケース２５前側の脱穀プーリ９４をベルト１０６連結させ、扱胴６下側の選別唐箕及び揺動選別機構に選別プーリ９６から駆動力を伝え、脱穀部６の各部を駆動すると共に、前記カウンタケース２５の左側面にフィードチェン入力軸１０７を設け、外側に移動可能な前記フィードチェン５の駆動スプロケット１０８に入力軸１０７から動力を伝える。また、前記穀物タンク１５の前側に排出駆動プーリ１０９を設け、該プーリ１０９を前記作業出力プーリ９１に排出クラッチ１１０を介してベルト連結させ、排出オーガ１７にエンジン２１出力を伝えてタンク１５の穀粒を排出させる。
【００２３】
さらに、前記カウンタケース２５に扱胴入力軸１１１を軸支させ、該軸１１１を前後方向に延設させ、カウンタケース２５前面外側の前記軸１１１前側に脱穀プーリ９４を設け、カウンタケース２５の後面外側の前記軸１１１後側に入力プーリ９２を設け、扱胴入力軸１１１にエンジン２１の一定回転動力を入力させて定速回転させる。また、前記カウンタケース２５の右側に同調入力軸１１２を軸支させ、カウンタケース２５の右側外側の前記軸１１２右側に車速同調プーリ９３を設け、アイドルプーリ９９を介してプーリ６２・９３間にベルト１００を緊張させ、ミッションケース２２からカウンタケース２５に車速同調動力を入力させる。
【００２４】
さらに、前記扱胴入力軸１１１に右側をベベルギヤ１１３連結させるカウンタ軸または選別入力軸である定速軸１１４と、該軸１１４の前側に略平行に設ける車速同調軸１１５とを、カウンタケース２５に軸支させると共に、同調入力軸１１２の車速同調回転力を伝える一方向クラッチ１２０を同調入力軸１１２上に設け、車速同調プーリ９３からの動力を一方向クラッチ１２０によって伝えるギヤ１１７及び刈取クラッチ１１８を介して車速同調軸１１５を回転させるように構成する。
【００２５】
さらに、刈取定速機構１２１を形成する刈取定速クラッチ１２２と高速カットギヤ１２３を前記各軸１１４・１１５の間に設け、刈取部７を車速同調または高速カット駆動させる切換シフタ１２４によって前記各ギヤクラッチ１１８・１２２を択一的に係合させ、刈取部７を車速同調駆動して走行速度に連動した速度で刈取部７を駆動する一方、刈取部７を高速カット駆動して車速同調の最高速よりも早い一定回転速度で刈取部７を駆動して倒伏穀稈を刈取る。
【００２６】
また、前記カウンタケース２５の左側で下部後側に定速軸１１４の左側端を突出させ、該軸１１４左側端部に選別プーリ９６を軸支させる。さらに、カウンタケース２５の左側で下部前側に刈取伝動軸１２５を軸支させ、該軸１２５右側を車速同調軸１１５にトルクリミッタ１２６を介して連結させ、カウンタケース２５左側に突出させる前記軸１２５の左側端部に刈取プーリ９５を軸支させると共に、前記刈取入力軸１０２に刈取駆動軸１２７をギヤ１２８連結させ、刈取駆動軸１２７に刈取入力プーリ１０３を軸支させるもので、トルクリミッタ１２６に伝える車速同調入力の入切と、定速駆動入力の入切とを、同一のシフタ１２４によって行い、トルクリミッタ１２６に伝える車速同調入力と定速駆動入力が同時に入になる不具合をなくし、車速同調と定速駆動の各入力がシフタ１２４によって択一選択されて伝えられ、伝動切換の制御を不要にして取扱い性の向上を図る。さらに、前記の左の支持台２３に支点軸１２９を介してギヤ１２８のケースを縦軸回りに回転自在に設け、刈取入力ケース１０１の左側をギヤ１２８のケースに固定させ、各ケース１０１に前記ギヤ１２８を内設させ、刈取入力軸１０２の左端側から刈取り動力を入力させ、前記ケース１０１右端側の刈取フレーム１２に内挿させる刈取伝動軸１３０を介して刈取部７の駆動を行わせる一方、支点軸１２９回りに機体左側に略水平に刈取部７を回転移動させ、機体内側の各ケース２２・２５付近のメンテナンス等を行う。
【００２７】
さらに、前記カウンタケース２５の左側上部に前記フィードチェン入力軸１０７を軸支させ、フィードチェンクラッチ１３１を設けるフィードチェン駆動軸１３２に前記入力軸１０７をチェン１３３連結させると共に、定速軸１１４の回転を車速同調軸１１５の回転数変化によって変速して伝えるフィードチェン変速機構１３４を設け、サンギヤ１３５とプラネタリギヤ１３６とリングギヤ１３７を備える遊星ギヤ機構１３８によって無段変速可能に前記機構１３４を形成するもので、定速軸１１４にサンギヤ１３５を係合軸支させ、定速軸１１４に遊転支持させるリングギヤ１３７を車速同調軸１１５にギヤ１３９連結させると共に、プラネタリギヤ１３６を遊転支持させる軸受体１４０を定速軸１１４に遊転支持させ、前記フィードチェンクラッチ１３１を介して前記フィードチェン駆動軸１３２に軸受体１４０をギヤ１４１連結させ、穀稈の搬送に必要な最低回転を確保し乍ら、低い一定回転から高回転にフィードチェン５速度を車速と同調させて変更可能に構成している。
【００２８】
また、切換シフタ１２４を作動させる油圧刈取定速シリンダ１４３と、脱穀クラッチ９７を入にする油圧脱穀シリンダ１４４を、前記カウンタケース２５の上面蓋である油路ベース１４５に固定させると共に、前記車速定速クラッチ７６を入にする車速定速シリンダ１４６を作動させる車速定速バルブ１４７と、刈取定速シリンダ１４３を作動させる刈取定速バルブ１４９と、脱穀シリンダ１４４を作動させる脱穀バルブ１５０とを、前記チャージポンプ７８に並列に油圧接続させる。
【００２９】
さらに、図１２、図２３、図２４に示す如く、前記脱穀クラッチ９７をテンションアーム１５１に軸支させ、カウンタケース２５の支軸１５２にテンションアーム１５１を回転自在に軸支させ、折曲自在な２本のリンク１５３・１５４を介して脱穀シリンダ１４４のピストンロッド１５５をテンションアーム１５１に連結させ、ピストンロッド１５５の押し（進出）動作により、脱穀クラッチ９７を入動作させてベルト９８を緊張させる一方、ピストンロッド１５５の引き（退入）動作により、脱穀クラッチ９７を切動作させてベルト９８を弛める。また、脱穀クラッチ９７を切り側に弾圧させるバネ１５６をリンク１５４に連結させる。
【００３０】
さらに、図１７、図１８に示す如く、前記カウンタケース２５に形成する締結座１８５を機台３にボルト１８６止め固定させると共に、カウンタケース２５の機外側に分離ケース１８７を着脱自在にボルト１８８止め固定させ、カウンタケース２５の一部を分離ケース１８７によって形成し、分離ケース１８７の脱着によってカウンタケース２５の機外側面を開閉自在に形成するもので、カウンタケース２５と分離ケース１８７とに、前記各軸１０７・１１４・１１５・１２５・１３２を軸支させ、カウンタケース２５上面の油路ベース１４５開口に比べ、分離ケース１８７を外したときのケース２５機外側面の開口面積を大きくし、各軸１０７・１１４・１１５・１２５・１３２の脱着及びギヤ交換などを行えるように構成している。
【００３１】
さらに、図３３に示す如く、作業レバー１８９の脱穀操作を検出する脱穀スイッチ１９０と、作業レバー１８９の刈取操作を検出する刈取スイッチ１９１と、主変速レバー８１の高速前進及び後進の切換を検出する高速運転スイッチ１９３及び後進スイッチ１９４と、低速・高速の副変速切換を行う副変速スイッチ１９７とを、マイクロコンピュータで構成する作業コントローラ１９８に接続させる。
【００３２】
また、エンジン２１の一定回転出力によって刈取部７を駆動する動作に手動で切換える直接駆動スイッチ１９９と、該スイッチ１９９の手動入力を入切する自動スイッチ２００と、左右の走行クローラ２の速度（車速）を検出する左及び右車速センサ２０１・２０２と、刈取部７の搬送穀稈の有無を検出する穀稈センサ２０３と、刈取部７に車速同調の駆動力を入力する同調入力軸１１２の入力回転数を低速ギヤ１１７を介して検出する刈取入力センサ２０４と、フィードチェンクラッチ１３１を切にするようにフィードチェンクラッチシリンダを作動させるフィードチェンソレノイド１９１と、定速シリンダ１４３により切換シフタ１２４を高速カットギヤ１２３係合動作させる高速カットソレノイド２０９と、刈取クラッチ１１８を入にする刈取クラッチソレノイド２１０とを、作業コントローラ１９８に接続させ、図２２のフローチャートのように、刈取部７を、高速カット速度または車速同調速度で作動させる。
【００３３】
また、前記の自動スイッチ２００がオンの状態下で高速運転スイッチ１９３がオンになったときに定速クラッチ７６を入にする高速運転ソレノイド２１１と、前記の副変速スイッチ１９７の切換によって副変速シリンダ８５を作動させて走行モータ３９を低速または高速出力にする副変速用低速及び高速ソレノイド２１２・２１３と、前記脱穀スイッチ１９０のオンによって脱穀クラッチ９７を入にする脱穀クラッチソレノイド２１４とを、作業コントローラ１９８に接続させる。
【００３４】
さらに、図２２のフローチャートに示す如く、作業レバー１８９の操作により脱穀スイッチ１９０がオンになると、フィードチェンソレノイド２０７をオフにしてフィードチェンクラッチ１３１を入にし、フィードチェン５の駆動を開始し、かつ脱穀クラッチソレノイド２１４を作動させて脱穀クラッチ９７を入にし、脱穀部４とフィードチェン５を駆動する。また、作業レバー１８９の操作により刈取スイッチ１９１がオンになると、刈取クラッチ１１８が入になり、車速同調プーリ９３を介して主変速駆動力が刈取部７に伝達される。
【００３５】
また、後進スイッチ１９４がオフのときで、車速センサ２０１・２０２によって検出する車軸５５が駆動されていると、走行モータ３９の副変速出力が低速のときで、刈取入力センサ２０４が検出する刈取部７の車速同調の入力回転が高速カットギヤ１２３による回転設定以上のとき、高速カットソレノイド２０９を作動させ、高速カットギヤ１２３を介して刈取部７を最高速で定速駆動する高速カット動作を行わせる。
【００３６】
また、走行モータ３９の副変速出力が低速のときで、刈取部７の入力回転が設定以下のときで、自動スイッチ２００がオンのとき、直接駆動スイッチ１９９がオン操作されると、高速運転ソレノイド２１１を作動させて車速定速クラッチ７６を入にし、走行変速部材４０を介することなく、エンジン２１の駆動力を定速クラッチ７６から副変速機構４７に直接伝達させ、高速運転動作させる。
【００３７】
さらに、図１３、図１４、図２３乃至図２８に示す如く、前記刈取伝動軸１２５にトルクリミッタ１２６を設けるもので、前記カウンタケース２５の側壁の一部を形成する着脱自在な分離ケース１８７にトルクリミッタ取付け孔２１９を開設させ、前記取付け孔２１９に軸受蓋２２０を外側から嵌合させて着脱自在にボルト２２１止め固定させ、カウンタケース２５の一部を形成する着脱自在な軸受蓋２２０に刈取伝動軸１２５の中間をベアリング軸受２２２により回転及び摺動自在に軸支させる。
【００３８】
また、前記カウンタケース２５の外側に突出させる刈取伝動軸１２５の一端側に刈取プーリ９５をキー嵌合固定させると共に、カウンタケース２５の内側に挿入させる刈取伝動軸１２５の他端側に、軸受段部２２４と、スプライン２２５と、ネジ２２６を形成し、平ギヤ形のリミッタ伝動ギヤ２２７を軸受段部２２４にベアリング軸受２２８を介して回転自在に軸支させる。なお、前記プーリ９５の外径を軸受蓋２２０の外形よりも大きく形成し、プーリ９５を軸１２５から取外した状態で軸受蓋２２０及びボルト２２１の着脱を行うと共に、前記ギヤ２２７の外径を取付け孔２１９よりも小さく形成し、ギヤ２２７を軸１２５に取付けた状態で、取付け孔２１９に軸１２５と軸受蓋２２０の嵌合部を出入させるもので、前記ギヤ２２７を噛合させる平ギヤ２２９を前記車速同調軸１１５に係合軸支させ、車速同調軸１１５にリミッタ伝動ギヤ２２７を連結させる。
【００３９】
さらに、前記リミッタ伝動ギヤ２２７の側面に一体形成する円筒形のアウタケース２３０と、刈取伝動軸１２５上で対向させるドーナツ板形の受板２３１及び押板２３２と、同一円周上に複数のトルクローラ２３３を略等間隔に配列させるドーナツ板形のトルク板２３４と、刈取伝動軸１２５の軸芯方向の対向する両側方からトルク板２３４のトルクローラ２３３を挾持させるドーナツ平板形の内板２３５及び外板２３６と、前記ネジ２２６に螺着させて押板２３２に圧接させる着脱自在なナット２２３及び座金１８１とを、前記トルクリミッタ１２６に備え、カウンタケース２５内部にトルクリミッタ１２６本体側のアウタケース２３０などを配設させて油浴させる。
【００４０】
そして、軸受蓋２２０に刈取伝動軸１２５を軸支させ、該軸１２５の軸受段部２２４にリミッタ伝動ギヤ２２７を抜出し自在に軸支させ、アウタケース２３０の内孔２４０に受板２３１を内挿させ、複数組の内板２３５とトルク板２３４と外板２３６をアウタケース２３０に内挿させ、刈取伝動軸１２５のスプライン２２５に内板２３５の内孔を係合軸支させ、略１２０度間隔に設けるアウタケース２３０のキー溝２４１に外板２３６外周の突起形キー２４２を係合させる。また、トルクバネ２３９を支持させた座板２３８を刈取伝動軸１２５の機外側端部に回転自在に軸支させ、前記軸１２５のネジ１８２にトルクナット２３７を螺着させ、トルクリミッタ１２６を軸受蓋２２０及び刈取伝動軸１２５とユニット構造に組立てるもので、トルクナット２３７を締付けてトルクバネ２３９力を調節し、トルクローラ２３３の伝達トルクを設定する。また、前記刈取プーリ９５とこのプーリボス１８３とを各別に形成し、プーリ９５とボス１８３を着脱自在にボルト１８４止め固定させ、プーリボス１８３を刈取伝動軸１２５にキー嵌合させ、プーリボス１８３の機外側面にトルクバネ２３９を圧接させ、カウンタケース２５の外側にトルクナット２３７及びバネ２３９を設ける。
【００４１】
また、刈取伝動軸１２５の軸芯部にＬ形の油穴２４３を形成し、油穴２４３の一端側をカウンタケース２５の内部に軸１２５端面で開口させ、油穴２４３の他端側を刈取伝動軸１２５のスプライン２２５形成部の周面に開口させると共に、スプライン２２５に嵌合させる内板２３５の内孔に油通し用の切欠２４４を形成し、多層形の各トルク板２３４のトルクローラ２３３に、油穴２４３及び切欠２４４を介し、刈取伝動軸１２５の回転によって発生する遠心力により油穴２４３からトルクローラ２３３方向にケース２５の油を移動させ、遠心力によって強制的にトルクローラ２３３に油を送って強制潤滑する。
【００４２】
さらに、前記トルクローラ２３３の円柱形に対して平面視で相似する長方形の支持孔２４５をトルク板２３４に形成し、トルクローラ２３３を支持孔２４５に回転自在に内挿させると共に、支持孔２４５の対向する長辺側の開口縁に一対の舌片２４６を対向させて設け、トルクローラ２３３の外周に舌片２４６を摺接させる。また、トルク板２３４の外周に形成する折曲げ縁２４７と同一方向に舌片２４６を突設させ、トルク板２３４の軸芯方向の幅をトルクローラ２３３の外径よりも小さく形成し、トルク板２３４の両側面にトルクローラ２３３の外周側を突出させて内板２３５と外板２３６に摺接させると共に、ホルダを形成する一対の舌片２４６の先端側をトルクローラ２３３の円周方向に折曲げ、トルクローラ２３３の外周を一対の舌片２４６によって回転自在に挾持させる。
【００４３】
さらに、前記トルク板２３４の回転中心２４７を通過する放射線２４８に対してトルクローラ２３３の軸芯線２４９をトルク板２３４の回転下手側に一定の傾斜角度θで傾斜させるもので、転動軸芯線２４９がトルク板２３４の回転中心を含む平面（放射線２４８）に対して角度θだけ傾斜するようにトルクローラ２３３を配置させる構成において、車速同調軸１１４の平ギヤ２２９を介してアウタケース２３０を回転駆動させると、各トルクローラ２３３が内板２３５と外板２３６に接しながら転動してトルク板２３４も回転する。このとき、各トルクローラ２３３は、外板２３６の回転軌道に対して前記角度θだけ傾斜した方向に転動しようとするのを、トルク板２３４で規制されながら外板２３６の回転軌道の方向に移動するため、前記トルクバネ２３９圧に比例した摩擦抵抗が発生し、しかも、各トルクローラ２３３は転動しながら滑り摩擦を発生させるので、静摩擦は発生せず、常に動摩擦による安定した摩擦抵抗力が得られる。また、刈取伝動軸１２５側の刈取駆動負荷が増加したとき、または平ギヤ２２９側の入力速度の変更によりアウタケース２３０の回転速度が高速側に急変したとき、内板２３５と外板２３６の各回転トルク差が増大してトルクローラ２３３の摩擦抵抗力よりも大きくなることにより、内板２３５と外板２３６がトルクローラ２３３に対して摺動して伝達動力が遮断される。
【００４４】
上記のように、油圧変速機構４０と定速機構１２１のいずれか一方によって作業部である刈取部７に駆動力を伝えると共に、刈取部７を定速回転させる刈取伝動軸１２５にトルクリミッタ１２６を設けるもので、油圧変速機構４０と定速機構１２１を切換えるときの駆動トルク差によって生じるショックをトルクリミッタ１２６によって吸収させ、前記の各機構４０・１２１を切換えるときのショックを低減させ、取扱い性を向上させると共に、トルクリミッタ１２６を内設させるカウンタケース２５内部の作動油面をトルクリミッタ１２６の軸１２５の設置位置よりも高くするもので、トルクリミッタ１２６に対して充分に潤滑を行わせ、耐久性を向上させ、安定したトルクを得る。
【００４５】
上記から明らかなように、アウタケース２３０と、トルクローラ２３３を配列させるトルク板２３４と、トルク板２３４のトルクローラ２３３を挾持させる内板２３５及び外板２３６とを備え、内板２３５とトルク板２３４と外板２３６をアウタケース２３０に内挿させ、伝動軸１２５に内板２３５を係合させ、アウタケース２３０に外板２３６を係合させ、トルクローラ２３３を転動させながら滑り摩擦を発生させる一方、内板２３５と外板２３６の各回転トルク差が増大してトルクローラ２３３の摩擦抵抗力よりも大きくなることにより、内板２３５と外板２３６がトルクローラ２３３に対して摺動して伝達動力が遮断されるトルクリミッタにおいて、伝動軸１２５の回転によって発生する遠心力によりトルクローラ２３３方向に油を移動させる油穴２４３を設け、遠心力によってトルクローラ２３３を強制潤滑するもので、トルクローラ２３３に対して潤滑油を充分に供給させ、トルクローラ２３３の伝達トルク維持並びに伝達動力の遮断を適正に行わせる。
【００４６】
また、伝動軸１２５の軸芯部にＬ形の油穴２４３を形成し、油穴２４３の一端側をギヤケースであるカウンタケース２５の内部に軸１２５端面で開口させ、油穴２４３の他端側を伝動軸１２５の周面に開口させ、伝動軸１２５の回転によって発生する遠心力により油穴２４３からトルクローラ２３３方向にギヤケースであるカウタケース２５油を移動させ、油穴２４３をＬ形に形成し、伝動軸１２５の回転を利用して遠心力によって潤滑油を移動させ、全てのトルクローラ２３３を油の中に入れる必要がなく、伝動軸１２５の油穴２４３の開口部が油の中に位置するように設ければよく、トルクローラ２３３などの設置場所の確保などを行うと共に、伝動軸１２５のスプライン２２５に嵌合させる内板２３５の内孔に油通し用の切欠２４４を形成し、油穴２４３及び欠切２４４を介してトルクローラ２３３方向に油を移動させ、複数組のトルク板２３４と内板２３５と外板２３６を重合させるように伝動軸１２５上に設けても、各組の内板２３５と外板２３６の間に油穴２４３から欠切２４４を介して油を移動させ、油穴２４３形状の簡略化並びに潤滑機能の向上などを行う。
【００４７】
さらに、トルクリミッタ１２６の本体側を伝動ケースであるカウンタケース２５内部に設けて油浴させると共に、カウンタケース２５外側の伝動プーリである刈取プーリ９５のプーリボス１８３外側にトルクリミッタ１２６のトルクセット部材であるトルクナット２３７及びトルクバネ２３９を設け、トルクリミッタ１２６の本体側を油浴させることによって耐久性を向上させることによって耐久性を向上させると共に、プーリボス１８３の外側にトルクナット２３７及びトルクバネ２３９を設け、トルクリミッタ１２６のトルクセットを機外から行い、メンテナンスなど取扱い性の向上を容易に図ると共に、刈取プーリ９５とプーリボス１８３を別体で形成し、刈取プーリ９５とプーリボス１８３をボルト１８４止め固定させ、プリーボス１８３を取付けた状態で刈取プーリ９５を取外し、トルクリミッタ１２６のセットトルクを一定に保った状態で刈取プーリ９５を取外してベルト交換作業などを行い、取扱い性の向上などを図る。
【００４８】
また、伝動軸１２５にベアリング軸受２２８を介して伝動ギヤ２２７を回転自在に軸支させ前記伝動ギヤ２２７の一側にアウタケース２３０を一体形成するもので、トルクリミッタ１２６の構成部品数の削減並びにコンパクト化を行い、かつ伝動軸１２５に対してトルクリミッタ１２６の本体側をユニット構成して組立性及びメンテナンス性などを向上させる。また、伝動軸１２５の中間を伝動ケースである軸受蓋２２０に軸受２２２を介して回転及び摺動自在に軸支させ、軸受蓋２２０の内部に突設させる伝動軸１２５の一端側にトルクリミッタ１２６の本体側を設け、軸受蓋２２０の外部に突設させる伝動軸１２５の他端側に伝動輪であるプーリ９５とトルクナット２３７などのトルクセット部材とを設けるもので、例えば分離自在な軸受蓋２２０に伝動軸１２５を軸支させることにより、分離する側の軸受蓋２２０と一体的にトルクリミッタ１２６を着脱させる一方、カウンタケース２５にトルクリミッタ１２６及びプーリボス１８３を設けた状態でプーリ９５だけを取外すことが可能で、組立性及びメンテナンス性などを向上させる。
【００４９】
【発明の効果】
本発明では、筒形のアウタケース内において、同アウタケース中に挿通した伝動軸に、複数のドーナツ板形の内板とトルク板と外板とを多層状にして同軸的に配置し、トルク板には、同一円周上に複数のトルクローラを配列すると共に、同トルク板の両側面にトルクローラの外周面を突出させて内板と外板に摺接させ、内板は伝動軸に係合させる一方、外板はアウタケースに係合させて、トルクローラを転動させながら滑り摩擦を発生させるようにし、伝動軸に油穴を形成すると共に、同油穴の一端を伝動軸の周面に開口させ、かつ、前記内板の内孔に油通し用の切欠を形成して、伝動軸の回転によって発生する遠心力により、上記油孔及び油通し用の切欠を通して油を多層状に配置した各トルク板のトルクローラ方向に移動させ、遠心力によってトルクローラを強制潤滑するようにしている。
従って、油穴及び油通し用の欠切を通してトルクローラ方向に油を移動させ、複数組のトルク板と内板と外板とを伝動軸に多層状にして同軸的に配置しても、各組の内板と外板の間に油穴から油通し用の欠切を通して油を移動させることができて、油穴形状の簡略化並びに潤滑機能の向上などを行うことができる。
しかも、各トルク板に配列した複数のトルクローラに対して潤滑油を充分に供給でき、各トルクローラの伝達トルク維持並びに伝達動力の遮断を適正に行わせることができる。
【図面の簡単な説明】
【図１】コンバインの斜視図。
【図２】同側面図。
【図３】前部機体の側面説明図。
【図４】同正面説明図。
【図５】駆動部の側面説明図。
【図６】同正面説明図。
【図７】同平面説明図。
【図８】同ミッションケースの駆動系統図。
【図９】同断面背面図。
【図１０】前図の拡大図。
【図１１】エンジン出力系統図。
【図１２】油圧回路図。
【図１３】カウンタケースの駆動系統図。
【図１４】同断面平面図。
【図１５】同拡大図。
【図１６】同外観正面図。
【図１７】同平面図。
【図１８】同側面図。
【図１９】脱穀クラッチ部の平面図。
【図２０】同背面図。
【図２１】制御回路図。
【図２２】前図のフローチャート。
【図２３】トルクリミッタ取付説明図。
【図２４】同拡大説明図。
【図２５】同分解説明図。
【図２６】同展開説明図。
【図２７】図２５の拡大説明図。
【図２８】刈取プーリの分解説明図。
【符号の説明】
２５カウンタケース（ギヤケース）
１２５伝動軸
２２５スプライン
２３０アウタケース
２３３トルクローラ
２３４トルク板
２３５内板
２３６外板
２４３油穴[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a torque limiter used for, for example, a combine, a tractor, a construction vehicle, or the like that moves by mounting a pair of left and right traveling crawlers.
[0002]
[Prior art]
Conventionally, there is a technique of providing a torque roller as a torque limiter. (For example, see Patent Document 1)
[0003]
[Patent Document 1]
JP 2002-61666 A
[0004]
[Problems to be solved by the invention]
The conventional technology generates sliding friction while rolling the torque roller, while the rotational torque difference between the input and output increases and becomes larger than the friction resistance force of the torque roller, so that the torque roller slides and transmits. Although the power was cut off, there was a problem such as the transmission torque of the torque roller fluctuated due to uneven supply of lubricating oil to multiple torque rollers, or the torque roller burned out due to lack of lubricating oil. is there.
[0005]
[Means for Solving the Problems]
Therefore, in the present invention, In the cylindrical outer case, a plurality of donut plate-shaped inner plates, torque plates, and outer plates are coaxially arranged on the transmission shaft inserted through the outer case, A plurality of torque rollers are arranged on the same circumference, and the outer peripheral surfaces of the torque rollers are projected on both side surfaces of the torque plate so as to be in sliding contact with the inner plate and the outer plate, and the inner plate is engaged with the transmission shaft. The outer plate is engaged with the outer case to generate sliding friction while rolling the torque roller, forming an oil hole in the transmission shaft, and opening one end of the oil hole on the peripheral surface of the transmission shaft Each torque plate in which oil notches are formed in the inner holes of the inner plate, and the oil is arranged in multiple layers through the oil holes and the notches for oil passing by the centrifugal force generated by the rotation of the transmission shaft. In the direction of the torque roller The present invention provides a torque limiter characterized in that a torque roller is forcibly lubricated by centrifugal force.
[0006]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is an overall perspective view of the combine. FIG. 2 is a right side view of the combine. In FIG. 1, 1 is a pair of left and right track frames for mounting a pair of left and right traveling crawlers 2, and 3 is installed on the left and right track frames 1. The threshing unit 4 is a threshing unit that is a threshing machine that has a feed chain 5 stretched to the left and incorporates a handling cylinder 6 and a processing cylinder, and 7 includes a pulling mechanism 8, a cutting blade 9, and a culm conveying mechanism 10. A harvesting section 11, a hydraulic lifting cylinder 11 that raises and lowers the harvesting section 7 via the harvesting frame 12, a waste disposal processing section 13 that faces the terminal end of the waste chain 14, and 15 a milling cylinder that receives grains from the threshing section 4 Grain tanks to be carried in via 16, 16 and 17 are discharge augers for carrying the grains of the tank 15 out of the machine, 18 is a driving cabin provided with a driving operation handle 19 and a driver seat 20, and 21 is provided below the driving cabin 18. Engine Continuously harvests culms are configured to threshing.
[0007]
Further, as shown in FIGS. 3 to 7, a mission case 22 is disposed between the left and right traveling crawlers 2 on the front side of the machine base 3, the mission case 22 and the engine 21 are provided substantially in series, and the mission case 22 is provided. The driving force of the engine 21 is transmitted to the traveling crawler 2 via the left and right support bases 23 and 24 erected on the upper surface of the machine base 3 on the front side of the threshing unit 4, and the support bases 23 and 24 are cut through the cutting frame 12. The part 7 is provided so as to be movable up and down and laterally movable. Further, a counter case 25 is provided on the upper surface of the machine base 3 on the rear side of the support bases 23 and 24, and the driving force of the engine 21 is transmitted to the threshing unit 4 and the mowing unit 7 through the counter case 25.
[0008]
Further, the cabin front frame 26 is erected on the machine base 3 on the side of the transmission case 22, and the front portion of the step frame 27 of the cabin 18 is provided on the upper portion of the front frame 26 via the rotation fulcrum shaft 28. The cabin 18 is rotatably supported forward, and the left cabin rear frame 29 is erected on the right support 24 and the machine base 3 between the right cabin rear frame 30 erected on the machine base 3. An engine 21 is provided on the upper surface, and the engine 21 is covered with an engine room cover 31. Further, the upper parts of the left and right rear frames 29 and 30 are connected to each other by the cabin horizontal frame 32 above the cover 31, the hook lever 33 is provided on the cabin horizontal frame 32, and the rear portion of the step frame 27 of the cabin 18 is mounted on the horizontal frame 32. The hook lever 33 is detachably fixed and the horizontal connecting frame 34 is fixed between the right support 24 and the front frame 26, and the inclined connecting frame 35 is fixed between the horizontal connecting frame 34 and the horizontal frame 32. The frame rigidity is ensured by the connecting frames 34 and 35. In addition, an auger support 36 is connected to the left rear frame 29 to provide an auger rest 37 on the upper side, and the discharge auger 17 provided so as to be able to move up and down and turn is supported at the machine storage position of the auger rest 37.
[0009]
Further, as shown in FIGS. 8 to 12, the transmission case 22 for driving the traveling crawler 2 is provided with a pair of hydraulic traveling pumps 38 and a hydraulic traveling motor 39 to provide a hydraulic continuously variable transmission mechanism for traveling main transmission. A traveling speed change member 40 to be formed, and a turning member 43 which forms a hydraulic continuously variable transmission mechanism for turning by providing a pair of hydraulic turning pumps 41 and a hydraulic turning motor 42, are provided on the output shaft 44 of the engine 21. The pumps 38 and 41 are configured to be connected via an input shaft 45 of the mission case 22.
[0010]
Further, each drive wheel 49 of the left and right traveling crawler 2 is interlockedly connected to the motor shaft 46 of the traveling motor 39 via a sub-transmission mechanism 47 and a differential mechanism 48. Each planetary gear mechanism 50 includes a single sun gear 51, three planetary gears 52 that mesh with the outer periphery of the sun gear 51, and a ring gear 53 that meshes with these planetary gears 52. .
[0011]
The planetary gear 52 is rotatably supported by a free-wheeling shaft 54 of the sun gear 51 and a carrier 56 of an axle 55 on the same axis, so that the left and right carriers 56 are opposed to each other with the left and right sun gears 51 therebetween. Has internal teeth meshing with each planetary gear 52 and is rotatably supported on an axle 55. The axle 55 is extended to support a drive wheel 49.
[0012]
The traveling speed change member 40 controls forward / reverse rotation and rotational speed of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. The traveling speed of the traveling motor 39 is controlled by the motor shaft 46 and the auxiliary transmission mechanism 47. The low-speed and high-speed gears 57 and 58, the brake shaft 59, and the branch shaft 60 are transmitted to the left and right ring gears 53 to rotate the left and right carriers 56. A parking brake 61 is provided on the brake shaft 59, and a cutting drive pulley 62 that transmits a rotational force to the cutting unit 7 is provided on the motor shaft 46 to drive the cutting unit 7 at a vehicle speed synchronization speed.
[0013]
As described above, the driving force of the traveling motor 39 transmitted to the ring gear 53 via the branch shaft 60 is transmitted to the left and right carriers 56 via the left and right planetary gear mechanisms 50, and the rotation transmitted to the left and right carriers 56. Is transmitted to the left and right drive wheels 49, respectively, so that the left and right traveling crawlers 2 are driven in the same direction and at the same speed.
[0014]
Further, the turning member 43 formed by the hydraulic continuously variable transmission mechanism for turning controls the forward / reverse rotation and the rotational speed of the turning motor 42 by changing the swash plate angle of the turning pump 41. A motor shaft 64 provided with 63, a clutch shaft 66 provided with a steering output clutch 65, and left and right input gears 67 and 68 that are always meshed with the left and right sun gears 51. The clutch shaft 66 is connected via the steering output clutch 65, and the left and right input gears 67 and 68 are connected to the clutch shaft 66 via the forward rotation gear 69 and the reverse rotation gear 70. Then, the rotational force of the motor 42 is transmitted to the right sun gear 51 via the forward rotation gear 69, and the rotation of the motor 42 is transmitted to the left sun gear 51 via the reverse rotation gear 70. The left sun gear 51 is reversely rotated (forward rotation) and the right sun gear 51 is rotated forward (reverse rotation) at the same left and right rotational speeds, and the left and right traveling crawlers 2 are driven in the reverse direction at the same speed.
[0015]
Thus, when the traveling motor 39 is driven in a state where the turning motor 42 is stopped and the left and right sun gears 51 are stationary, the rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 at the same rotational speed, and the left and right planetary gears. The left and right traveling crawlers 2 are driven at the same rotational speed in the same direction in the left and right directions through the carrier 56 of the mechanism 50, and the vehicle body travels straight forward and backward. On the other hand, when the turning motor 42 is driven to rotate forward and reverse with the traveling motor 39 stopped and the left and right ring gears 53 stationary, the left planetary gear mechanism 50 rotates forward or reverse, and the right planetary gear mechanism 50. Rotates in the reverse or forward direction, drives the left and right traveling crawler 2 in the reverse direction, and turns the aircraft to the left or right. Further, by driving the turning motor 42 while driving the traveling motor 39, the aircraft turns left and right to correct the course, and the turning radius of the aircraft is determined by the output rotation speed of the turning motor 42. .
[0016]
Further, a fan shaft 71 is connected to the input shaft 45, and a cooling fan 72 of a radiator for cooling the engine 21 is driven by the fan shaft 71, and the pump shafts 73 and 74 of the traveling and swirling pumps 38 and 41 are connected to the pump shafts 73 and 74. The fan shaft 71 is connected via the gear group 75, the input shaft 45 is connected to each pump 38 and 41, and the pump shaft 73 of the traveling pump 38 and the motor shaft 46 of the traveling motor 39 are connected to the vehicle speed constant speed clutch. When the constant speed shaft 77 to be connected via 76 is provided and the vehicle speed constant speed clutch 76 is turned on, the pump shaft 73 and the motor shaft 46 are gear connected via the constant speed shaft 77 and the traveling speed change member 40 is interposed. Instead, the rotation of the input shaft 45 is transmitted to the sub-transmission mechanism 47, the left and right traveling crawlers 2 are driven by the constant speed rotation of the engine 21, and the harvesting is performed at a substantially constant vehicle speed. To perform the like. A charge pump 78 is provided on the swing pump shaft 74 and driven.
[0017]
Further, as shown in FIG. 12, a main transmission cylinder 80 that adjusts the output by changing the angle of the swash plate 79 of the traveling pump 38, a transmission valve 82 that is connected to the main transmission lever 81 and the steering handle 19, and a traveling pump. 38, a valve 83 for decelerating the output by a certain amount is provided, and the charge pump 78 is hydraulically connected to the main transmission cylinder 80 via the valves 82 and 83. The main transmission lever 81 switches the transmission valve 82, and the main transmission cylinder 80 is operated to change the angle of the swash plate 79 of the traveling pump 38, to change the rotational speed of the motor shaft 46 of the traveling motor 39 steplessly or to perform a traveling shift operation that reverses the rotation. The swash plate 7 is made proportional to the operation amount of the main transmission lever 81 by performing a feedback operation in which the transmission valve 82 is neutrally returned by the angle adjustment operation. The angle is varied, by varying the rotation speed of the traveling motor 39 to change the vehicle speed.
[0018]
Further, a sub-transmission cylinder 85 for adjusting the output by changing the angle of the swash plate 84 of the traveling motor 39 is provided, and the sub-transmission cylinder 85 is hydraulically connected to the charge pump 78 via the electromagnetic sub-transmission valve 86. When the engine is neutral, the auxiliary transmission cylinder 85 is short-circuited to the transmission case 22 which is an oil tank, the angle of the swash plate 84 of the traveling motor 39 is changed by the main circuit oil pressure, and the angle of the swash plate 84 is changed by switching the auxiliary transmission valve 86. The output of the traveling motor 39 is changed to a high speed or a low speed by forcibly changing.
[0019]
Further, a slewing cylinder 88 for adjusting the output by changing the angle of the swash plate 87 of the slewing pump 41 is provided, and is connected via the slewing valve 89 and the electromagnetic automatic steering valve 90 which are switched by being connected to the steering handle 19 and the main transmission lever 81. The charge pump 78 is hydraulically connected to the turning cylinder 88, the turning valve 89 is switched by the steering handle 19, the turning cylinder 88 is operated to change the angle of the swash plate 87 of the turning pump 41, and the motor shaft 64 of the turning motor 42 is changed. A left / right turning operation that changes the rotation speed steplessly or reversely is performed, and a feedback operation in which the turning valve 89 is neutrally returned by an angle adjustment operation of the swash plate 87 is performed. The angle of the swash plate 87 is changed proportionally, and the rotation speed of the turning motor 42 is changed to change the left / right turning angle.
[0020]
Further, when the main transmission lever 81 is operated to a position other than the neutral position and the steering handle 19 is operated other than the straight traveling, the hydraulic output of the traveling pump 38 is proportional to the operation direction and the operation amount of the main transmission lever 81. Increase / decrease, forward / reverse or increase / decrease the hydraulic motor 39 to change the forward / reverse speed (vehicle speed), and change the output of the swing pump 41 in proportion to the amount of operation of the main shift lever 81. Automatically reduces the turning radius and automatically increases the turning radius by low-speed side shifting, and the turning radius of the left and right traveling crawlers 2 is maintained substantially constant by constant operation of the steering handle 19 regardless of the traveling speed. To change the work travel speed and to correct the course so that the machine body is aligned with the uncut grain row. On the other hand, when the turning pump 41 output and the traveling pump 38 output are changed by the control of the valves 82 and 89 in proportion to the operation amount of the steering handle 19, the traveling speed is reduced when the turning radius (steering angle) is made small (large). The speed difference between the left and right traveling crawlers 2 is increased and the left and right traveling crawlers 2 are swung left and right while the vehicle speed is reduced in proportion to the vehicle speed. The direction is changed by spin-turning at, and the harvesting operation is carried out to continuously harvest and thresh grains. When the main transmission lever 81 is neutral, the swing valve 89 is maintained neutral regardless of the operation of the steering handle 19, the hydraulic output of the swing pump 41 is maintained at substantially zero, and the swing motor 42 is stopped.
[0021]
Further, as shown in FIGS. 11 to 18, the output shaft 44 of the engine 21 is protruded to the front side and the rear side, the input shaft 45 is connected to the front side of the output shaft 44, and work is performed on the rear side of the output shaft 44. An output pulley 91 is provided, and a counter case 25 is provided on the upper surface of the machine base 3 in front of the threshing section 4 on the left side of the engine 21. The input pulley 92, the vehicle speed tuning pulley 93, the threshing pulley 94, the cutting pulley 95, and the sorting pulley 96 are countered. The case 25 is pivotally supported, and the input pulley 92 on the rear side of the case 25 is connected to the work output pulley 91 via a belt threshing clutch 97 to transmit the driving force of the engine 21 to the counter case 25. In addition, the vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected to the cutting drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support base 24 and is erected on the front upper surface of the machine base 3. A cutting input case 101 is pivotally supported on the support bases 23 and 24, a cutting frame 12 is connected to the case 101, and the cutting unit 7 is rotated around the case 101 to move up and down. The cutting input pulley 103 is pivotally supported via the cutting input shaft 102, the cutting pulley 95 on the left side of the counter case 25 is connected to the cutting input pulley 103 with the belt 104, and the driving force is transmitted to each part of the cutting unit 7.
[0022]
Further, a threshing pulley 94 on the front side of the counter case 25 is connected to the driving input pulley 105 of the handling cylinder 6 with a belt 106, and a driving force is transmitted from the sorting pulley 96 to the sorting and swinging selection mechanism on the lower side of the handling cylinder 6, thereby threshing. While driving each part of the part 6, a feed chain input shaft 107 is provided on the left side surface of the counter case 25, and power is transmitted from the input shaft 107 to the drive sprocket 108 of the feed chain 5 that can move outward. Further, a discharge drive pulley 109 is provided on the front side of the grain tank 15, the pulley 109 is belt-connected to the work output pulley 91 via a discharge clutch 110, and the output of the engine 21 is transmitted to the discharge auger 17 to transfer the grain in the tank 15. Drain the grains.
[0023]
Further, the barrel input shaft 111 is pivotally supported on the counter case 25, the shaft 111 is extended in the front-rear direction, a threshing pulley 94 is provided on the front side of the shaft 111 outside the front surface of the counter case 25, and the rear surface of the counter case 25 An input pulley 92 is provided on the rear side of the outer shaft 111, and a constant rotational power of the engine 21 is input to the handling cylinder input shaft 111 to rotate at a constant speed. Further, a tuning input shaft 112 is pivotally supported on the right side of the counter case 25, a vehicle speed tuning pulley 93 is provided on the right side of the shaft 112 outside the right side of the counter case 25, and a belt is provided between the pulleys 62 and 93 via the idle pulley 99. 100 is tensioned, and the vehicle speed synchronization power is input from the mission case 22 to the counter case 25.
[0024]
Further, the counter case 25 includes a constant speed shaft 114 that is a counter shaft or a selection input shaft for connecting the bevel gear 113 on the right side to the handle cylinder input shaft 111 and a vehicle speed tuning shaft 115 provided substantially parallel to the front side of the shaft 114. A one-way clutch 120 is provided on the tuning input shaft 112 for transmitting the vehicle speed tuning rotational force of the tuning input shaft 112 and the gear 117 and the cutting clutch 118 for transmitting the power from the vehicle speed tuning pulley 93 by the one-way clutch 120. The vehicle speed tuning shaft 115 is configured to rotate.
[0025]
Further, a cutting constant speed clutch 122 and a high speed cut gear 123 forming a cutting constant speed mechanism 121 are provided between the shafts 114 and 115, and the gear clutches are switched by a shift shifter 124 that drives the cutting part 7 in synchronization with the vehicle speed or high speed cut. 118 and 122 are selectively engaged, and the cutting unit 7 is driven in synchronization with the vehicle speed to drive the cutting unit 7 at a speed linked to the traveling speed, while the cutting unit 7 is driven at high speed to drive the maximum speed for vehicle speed synchronization. The mowing unit 7 is driven at a constant rotational speed faster than that to harvest the fallen cereal.
[0026]
Further, the left end of the constant speed shaft 114 is protruded to the lower rear side on the left side of the counter case 25, and the sorting pulley 96 is pivotally supported on the left end portion of the shaft 114. Further, the cutting transmission shaft 125 is pivotally supported on the lower front side on the left side of the counter case 25, the right side of the shaft 125 is connected to the vehicle speed tuning shaft 115 via the torque limiter 126, and the shaft 125 is projected to the left side of the counter case 25. A cutting pulley 95 is pivotally supported at the left end, a cutting drive shaft 127 is connected to the cutting input shaft 102 and a gear 128 is coupled, and the cutting input pulley 103 is pivotally supported by the cutting drive shaft 127 and transmitted to the torque limiter 126. The on / off of the vehicle speed tuning input and the on / off of the constant speed driving input are performed by the same shifter 124 to eliminate the problem that the vehicle speed tuning input and the constant speed driving input transmitted to the torque limiter 126 are simultaneously turned on. Each input of the constant speed drive is selected and transmitted by the shifter 124, and transmission control is not required, thereby improving handling. Further, a case of the gear 128 is provided on the left support base 23 via a fulcrum shaft 129 so as to be rotatable about the vertical axis, and the left side of the cutting input case 101 is fixed to the case of the gear 128, While the gear 128 is installed, the cutting power is input from the left end side of the cutting input shaft 102, and the cutting unit 7 is driven via the cutting transmission shaft 130 inserted into the cutting frame 12 on the right end side of the case 101. Then, the mowing unit 7 is rotated about the fulcrum shaft 129 substantially horizontally on the left side of the machine body, and maintenance of the vicinity of the cases 22 and 25 inside the machine body is performed.
[0027]
Further, the feed chain input shaft 107 is pivotally supported on the upper left part of the counter case 25, the input shaft 107 is connected to the chain 133 to a feed chain drive shaft 132 provided with a feed chain clutch 131, and the constant speed shaft 114 is rotated. Is provided with a feed chain transmission mechanism 134 that transmits the speed by changing the rotational speed of the vehicle speed tuning shaft 115, and the planetary gear mechanism 138 including the sun gear 135, the planetary gear 136, and the ring gear 137 forms the mechanism 134 so as to be continuously variable. In addition, the sun gear 135 is supported on the constant speed shaft 114 and the ring gear 137, which freely supports the constant speed shaft 114, is connected to the gear 139 to the vehicle speed tuning shaft 115, and the bearing 140, which supports the planetary gear 136, is fixed. The fast shaft 114 is supported in an idle manner, and the feed chain is The bearing body 140 is connected to the gear 141 via the clutch 131 to the feed chain drive shaft 132 to ensure the minimum rotation necessary for conveying the cereal, and the feed chain 5 speed is increased from the low constant rotation to the high rotation. It is configured so that it can be changed in synchronization.
[0028]
Further, a hydraulic cutting speed cylinder 143 for operating the switching shifter 124 and a hydraulic threshing cylinder 144 for receiving the threshing clutch 97 are fixed to an oil passage base 145 which is a top cover of the counter case 25, and the vehicle speed is fixed. The vehicle speed constant speed valve 147 for operating the vehicle speed constant speed cylinder 146 for engaging the speed clutch 76, the cutting constant speed valve 149 for operating the cutting constant speed cylinder 143, and the threshing valve 150 for operating the threshing cylinder 144 are described above. The charge pump 78 is hydraulically connected in parallel.
[0029]
Further, as shown in FIGS. 12, 23, and 24, the threshing clutch 97 is pivotally supported on the tension arm 151, and the tension arm 151 is pivotally supported on the support shaft 152 of the counter case 25 so that it can be bent. The piston rod 155 of the threshing cylinder 144 is connected to the tension arm 151 via the two links 153 and 154, and the threshing clutch 97 is engaged by the pushing (advancing) operation of the piston rod 155 to tension the belt 98. By the pulling (withdrawing) operation of the piston rod 155, the threshing clutch 97 is operated to loosen the belt 98. In addition, a spring 156 that presses the threshing clutch 97 to the cut side is connected to the link 154.
[0030]
Further, as shown in FIGS. 17 and 18, the fastening seat 185 formed on the counter case 25 is fixed to the machine base 3 with bolts 186, and the separation case 187 is detachably fixed to the machine case 3 with the bolts 188 attached thereto. A part of the counter case 25 is formed by the separation case 187, and the outer side surface of the counter case 25 is formed to be openable and closable by detaching the separation case 187. The counter case 25 and the separation case 187 Each shaft 107, 114, 115, 125, 132 is pivotally supported, and the opening area of the outer surface of the case 25 machine when the separation case 187 is removed is larger than the opening of the oil passage base 145 on the upper surface of the counter case 25, The shafts 107, 114, 115, 125 and 132 can be attached and detached and the gears can be exchanged.
[0031]
Further, as shown in FIG. 33, a threshing switch 190 that detects a threshing operation of the work lever 189, a reaping switch 191 that detects a reaping operation of the work lever 189, and a high-speed forward / reverse switching of the main transmission lever 81 are detected. A high-speed operation switch 193 and a reverse switch 194, and a sub-shift switch 197 that performs low-speed / high-speed sub-shift switching are connected to a work controller 198 constituted by a microcomputer.
[0032]
Further, a direct drive switch 199 for manually switching to an operation for driving the cutting unit 7 by a constant rotational output of the engine 21, an automatic switch 200 for turning on / off the manual input of the switch 199, and the speeds (vehicle speeds) of the left and right traveling crawlers 2 ) For detecting left and right vehicle speed sensors 201 and 202, for detecting the presence or absence of a conveying culm in the cutting unit 7, and for input of a tuning input shaft 112 for inputting a driving force for vehicle speed synchronization to the reaping unit 7. A cutting input sensor 204 that detects the rotational speed via the low speed gear 117, a feed chain solenoid 191 that operates the feed chain clutch cylinder so as to turn off the feed chain clutch 131, and a constant speed cylinder 143 cause the switching shifter 124 to operate at high speed. The high speed cut solenoid 209 for engaging the cut gear 123 and the cutting clutch 118 are turned on. A clutch solenoid 210 reaper that, is connected to the work controller 198, as shown in the flowchart of FIG. 22, the reaper 7 is operated at a high speed cutting speed or the vehicle speed synchronization speed.
[0033]
In addition, when the automatic switch 200 is turned on and the high-speed operation switch 193 is turned on, the high-speed operation solenoid 211 that turns on the constant-speed clutch 76 and the sub-transmission cylinder 197 are switched. The operation controller includes a low speed and high speed solenoids 212 and 213 for sub-transmission for operating the motor 85 to output the traveling motor 39 at low speed or high speed, and a threshing clutch solenoid 214 for turning on the threshing clutch 97 when the threshing switch 190 is turned on. Connect to 198.
[0034]
Furthermore, as shown in the flowchart of FIG. 22, when the threshing switch 190 is turned on by operating the operation lever 189, the feed chain solenoid 207 is turned off, the feed chain clutch 131 is turned on, the drive of the feed chain 5 is started, and The threshing clutch solenoid 214 is operated to turn on the threshing clutch 97, and the threshing unit 4 and the feed chain 5 are driven. When the cutting switch 191 is turned on by operating the operation lever 189, the cutting clutch 118 is turned on, and the main transmission driving force is transmitted to the cutting unit 7 via the vehicle speed tuning pulley 93.
[0035]
Further, when the reverse switch 194 is off and the axle 55 detected by the vehicle speed sensors 201 and 202 is driven, the cutting unit detected by the cutting input sensor 204 when the sub-shift output of the travel motor 39 is low. When the input rotation for synchronizing the vehicle speed of 7 is equal to or higher than the rotation setting by the high speed cut gear 123, the high speed cut solenoid 209 is operated, and the high speed cut operation for driving the cutting unit 7 at a constant speed at the maximum speed is performed via the high speed cut gear 123.
[0036]
In addition, when the sub-shift output of the traveling motor 39 is low, the input rotation of the cutting unit 7 is less than the setting, the automatic switch 200 is on, and the direct drive switch 199 is turned on, the high-speed operation solenoid 211 is operated, the vehicle speed constant speed clutch 76 is turned on, and the driving force of the engine 21 is directly transmitted from the constant speed clutch 76 to the subtransmission mechanism 47 without the traveling speed change member 40, so that the high speed driving operation is performed.
[0037]
Further, as shown in FIGS. 13, 14, 23 to 28, a torque limiter 126 is provided on the cutting transmission shaft 125, and a detachable separating case 187 forming a part of the side wall of the counter case 25 is provided. A torque limiter mounting hole 219 is opened, and a bearing lid 220 is fitted into the mounting hole 219 from the outside, and is detachably fixed with a bolt 221. The detachable bearing lid 220 forming a part of the counter case 25 is trimmed. The middle of the transmission shaft 125 is supported by a bearing bearing 222 so as to be rotatable and slidable.
[0038]
Further, a cutting pulley 95 is key-fitted and fixed to one end side of the cutting transmission shaft 125 that protrudes to the outside of the counter case 25, and a bearing stage is connected to the other end side of the cutting transmission shaft 125 that is inserted inside the counter case 25. A portion 224, a spline 225, and a screw 226 are formed, and a flat gear type limiter transmission gear 227 is rotatably supported by the bearing step portion 224 via the bearing bearing 228. In addition, the outer diameter of the pulley 95 is formed larger than the outer diameter of the bearing lid 220, and the bearing lid 220 and the bolt 221 are attached and detached while the pulley 95 is detached from the shaft 125, and the outer diameter of the gear 227 is attached. With the gear 227 attached to the shaft 125, the fitting portion of the shaft 125 and the bearing lid 220 is inserted into and removed from the mounting hole 219, and the flat gear 229 that meshes with the gear 227 is provided. An engagement shaft is supported on the vehicle speed tuning shaft 115, and a limiter transmission gear 227 is connected to the vehicle speed tuning shaft 115.
[0039]
Furthermore, a cylindrical outer case 230 integrally formed on the side surface of the limiter transmission gear 227, a donut plate-shaped receiving plate 231 and a push plate 232 opposed on the cutting transmission shaft 125, and a plurality of torques on the same circumference A donut plate-shaped torque plate 234 in which the rollers 233 are arranged at substantially equal intervals, and a donut plate-shaped inner plate 235 that holds the torque roller 233 of the torque plate 234 from opposite sides in the axial direction of the cutting transmission shaft 125; The torque limiter 126 includes an outer plate 236 and a detachable nut 223 and a washer 181 that are screwed onto the screw 226 and press-contacted to the pressing plate 232, and the outer case on the torque limiter 126 main body side is provided inside the counter case 25. 230 etc. are arrange | positioned and let it be an oil bath.
[0040]
Then, the cutting transmission shaft 125 is pivotally supported by the bearing lid 220, the limiter transmission gear 227 is pivotally supported by the bearing step portion 224 of the shaft 125, and the receiving plate 231 is inserted into the inner hole 240 of the outer case 230. A plurality of sets of inner plates 235, torque plates 234, and outer plates 236 are inserted into the outer case 230, and the inner holes of the inner plates 235 are engaged and supported by the splines 225 of the cutting transmission shaft 125 at intervals of approximately 120 degrees. The protruding key 242 on the outer periphery of the outer plate 236 is engaged with the key groove 241 of the outer case 230 provided on the outer case 230. Further, a seat plate 238 supporting the torque spring 239 is rotatably supported on the machine outer end portion of the cutting transmission shaft 125, a torque nut 237 is screwed onto the screw 182 of the shaft 125, and the torque limiter 126 is attached to the bearing lid. 220 and the cutting transmission shaft 125 are assembled in a unit structure. The torque nut 237 is tightened to adjust the torque spring 239 force, and the transmission torque of the torque roller 233 is set. Further, the cutting pulley 95 and the pulley boss 183 are formed separately, the pulley 95 and the boss 183 are detachably fixed with bolts 184, the pulley boss 183 is key-fitted to the cutting drive shaft 125, and the pulley boss 183 is externally mounted. A torque spring 239 is pressed against the side surface, and a torque nut 237 and a spring 239 are provided outside the counter case 25.
[0041]
Further, an L-shaped oil hole 243 is formed in the shaft core portion of the cutting transmission shaft 125, one end side of the oil hole 243 is opened inside the counter case 25 at the end face of the shaft 125, and the other end side of the oil hole 243 is cut off. An opening is formed in the peripheral surface of the spline 225 forming portion of the transmission shaft 125, and an oil passage notch 244 is formed in the inner hole of the inner plate 235 to be fitted to the spline 225, and the torque roller 233 of each of the multilayer torque plates 234 is formed. The oil in the case 25 is moved from the oil hole 243 toward the torque roller 233 by the centrifugal force generated by the rotation of the cutting transmission shaft 125 through the oil hole 243 and the notch 244, and the torque roller 233 is forced to oil by the centrifugal force. To force lubrication.
[0042]
Further, a rectangular support hole 245 similar in plan view to the cylindrical shape of the torque roller 233 is formed in the torque plate 234, the torque roller 233 is rotatably inserted into the support hole 245, and the support hole 245 A pair of tongue pieces 246 are provided to face the opening edge on the opposite long side, and the tongue piece 246 is brought into sliding contact with the outer periphery of the torque roller 233. Further, a tongue piece 246 is projected in the same direction as the bent edge 247 formed on the outer periphery of the torque plate 234, and the width in the axial direction of the torque plate 234 is formed to be smaller than the outer diameter of the torque roller 233. The outer peripheral side of the torque roller 233 protrudes from both side surfaces of the 234 to make sliding contact with the inner plate 235 and the outer plate 236, and the tip side of the pair of tongue pieces 246 forming the holder is folded in the circumferential direction of the torque roller 233. The outer periphery of the torque roller 233 is bent and is rotatably held by a pair of tongue pieces 246.
[0043]
Further, the axis 249 of the torque roller 233 is inclined at a constant inclination angle θ toward the lower rotation side of the torque plate 234 with respect to the radiation 248 passing through the rotation center 247 of the torque plate 234. In the configuration in which the torque roller 233 is disposed so as to be inclined by an angle θ with respect to the plane (radiation 248) including the rotation center of the torque plate 234, the outer case 230 is rotationally driven via the flat gear 229 of the vehicle speed tuning shaft 114. Then, each torque roller 233 rolls in contact with the inner plate 235 and the outer plate 236, and the torque plate 234 also rotates. At this time, each torque roller 233 tries to roll in the direction inclined by the angle θ with respect to the rotation track of the outer plate 236 in the direction of the rotation track of the outer plate 236 while being restricted by the torque plate 234. Therefore, a frictional resistance proportional to the pressure of the torque spring 239 is generated, and each torque roller 233 generates a sliding friction while rolling, so that no static friction is generated and a stable frictional resistance force due to dynamic friction is always obtained. can get. Further, when the cutting drive load on the cutting transmission shaft 125 side increases, or when the rotational speed of the outer case 230 suddenly changes to the high speed side by changing the input speed on the flat gear 229 side, each of the inner plate 235 and the outer plate 236 As the rotational torque difference increases and becomes greater than the frictional resistance of the torque roller 233, the inner plate 235 and the outer plate 236 slide relative to the torque roller 233, and the transmission power is cut off.
[0044]
As described above, either one of the hydraulic transmission mechanism 40 and the constant speed mechanism 121 transmits the driving force to the cutting unit 7 that is the working unit, and the torque limiter 126 is attached to the cutting transmission shaft 125 that rotates the cutting unit 7 at a constant speed. The shock generated by the difference in driving torque when the hydraulic transmission mechanism 40 and the constant speed mechanism 121 are switched is absorbed by the torque limiter 126, and the shock when switching the mechanisms 40 and 121 is reduced. The hydraulic oil level in the counter case 25 in which the torque limiter 126 is installed is made higher than the installation position of the shaft 125 of the torque limiter 126, and the torque limiter 126 is sufficiently lubricated and durable. Improve the performance and obtain a stable torque.
[0045]
As is apparent from the above, the outer case 230, the torque plate 234 for arranging the torque rollers 233, and the inner plate 235 and the outer plate 236 for holding the torque rollers 233 of the torque plate 234 are provided. 234 and the outer plate 236 are inserted into the outer case 230, the inner plate 235 is engaged with the transmission shaft 125, the outer plate 236 is engaged with the outer case 230, and sliding friction is generated while rolling the torque roller 233. On the other hand, the rotational torque difference between the inner plate 235 and the outer plate 236 increases and becomes larger than the frictional resistance force of the torque roller 233, so that the inner plate 235 and the outer plate 236 slide relative to the torque roller 233. In the torque limiter in which the transmission power is cut off, the oil is transferred in the direction of the torque roller 233 by the centrifugal force generated by the rotation of the transmission shaft 125. An oil hole 243 is provided to forcibly lubricate the torque roller 233 with centrifugal force. The lubricating oil is sufficiently supplied to the torque roller 233, and the transmission torque of the torque roller 233 is maintained and the transmission power is properly cut off. Make it.
[0046]
Further, an L-shaped oil hole 243 is formed in the shaft core portion of the transmission shaft 125, and one end side of the oil hole 243 is opened at the end face of the shaft 125 inside the counter case 25 which is a gear case, and the other end side of the oil hole 243 is formed. Is opened on the peripheral surface of the transmission shaft 125, and the counter case 25 oil as a gear case is moved from the oil hole 243 toward the torque roller 233 by the centrifugal force generated by the rotation of the transmission shaft 125, and the oil hole 243 is formed in an L shape. The lubricating oil is moved by centrifugal force using the rotation of the transmission shaft 125, and it is not necessary to put all the torque rollers 233 into the oil, and the opening of the oil hole 243 of the transmission shaft 125 is located in the oil. The installation location of the torque roller 233 and the like is secured, and an oil passage notch 244 is provided in the inner hole of the inner plate 235 to be fitted to the spline 225 of the transmission shaft 125. And the oil is moved in the direction of the torque roller 233 through the oil hole 243 and the notch 244 so that a plurality of sets of the torque plate 234, the inner plate 235, and the outer plate 236 are superposed on the transmission shaft 125. The oil is moved from the oil hole 243 through the notch 244 between the inner plate 235 and the outer plate 236 of each set to simplify the shape of the oil hole 243 and improve the lubrication function.
[0047]
Further, the main body side of the torque limiter 126 is provided inside the counter case 25 which is a transmission case and oil bathed, and a torque set member of the torque limiter 126 is provided outside the pulley boss 183 of the cutting pulley 95 which is a transmission pulley outside the counter case 25. A torque nut 237 and a torque spring 239 are provided, the durability is improved by oil bathing the main body side of the torque limiter 126, and the torque nut 237 and the torque spring 239 are provided outside the pulley boss 183. The torque limiter 126 is set from the outside of the machine, facilitating the improvement of handling such as maintenance, and the cutting pulley 95 and the pulley boss 183 are formed separately, and the cutting pulley 95 and the pulley boss 183 are fixed with bolts 184, Preevous Remove the pulley 95 cutting in a state of mounting the 83, remove the pulleys 95 cutting while maintaining the set torque of the torque limiter 126 fixed perform a belt replacement, achieving such improvement in handling property.
[0048]
Further, the transmission gear 227 is rotatably supported on the transmission shaft 125 via the bearing bearing 228, and the outer case 230 is integrally formed on one side of the transmission gear 227, so that the number of components of the torque limiter 126 can be reduced. A compact body is formed and the main body side of the torque limiter 126 is configured as a unit with respect to the transmission shaft 125 to improve assemblability and maintenance. Further, a torque limiter 126 is provided at one end side of the transmission shaft 125 that is supported in the middle of the transmission shaft 125 so as to be rotatable and slidable by a bearing lid 220 serving as a transmission case via a bearing 222. And a torque set member such as a torque nut 237 is provided on the other end side of the transmission shaft 125 that protrudes outside the bearing lid 220. For example, a separable bearing lid The torque limiter 126 is attached to and detached from the bearing cover 220 on the side to be separated by pivotally supporting the transmission shaft 125 on 220, while only the pulley 95 is provided with the torque limiter 126 and the pulley boss 183 provided on the counter case 25. It can be removed, improving assembly and maintenance.
[0049]
【The invention's effect】
In the present invention, in a cylindrical outer case, a plurality of donut-shaped inner plates, torque plates and outer plates are coaxially arranged on a transmission shaft inserted through the outer case, and torque is provided. A plurality of torque rollers are arranged on the same circumference of the plate, and the outer peripheral surfaces of the torque rollers are projected on both side surfaces of the torque plate so as to be in sliding contact with the inner plate and the outer plate. On the other hand, the outer plate is engaged with the outer case to generate sliding friction while rolling the torque roller, and an oil hole is formed in the transmission shaft, and one end of the oil hole is connected to the transmission shaft. Open in the peripheral surface and form oil notches in the inner holes of the inner plate, and arrange the oil in multiple layers through the oil holes and oil notches by centrifugal force generated by the rotation of the transmission shaft The torque plate is moved in the direction of the torque roller to generate centrifugal force. So that force lubricate the torque roller I.
Therefore, even if oil is moved in the direction of the torque roller through the oil hole and the notch for oil passage, a plurality of sets of torque plates, inner plates and outer plates are arranged in a coaxial manner on the transmission shaft, and each set is arranged. The oil can be moved between the inner plate and the outer plate from the oil hole through a notch for oil passage, so that the shape of the oil hole can be simplified and the lubrication function can be improved.
In addition, the lubricating oil can be sufficiently supplied to the plurality of torque rollers arranged on each torque plate, and the transmission torque of each torque roller can be maintained and the transmission power can be interrupted appropriately.
[Brief description of the drawings]
FIG. 1 is a perspective view of a combine.
FIG. 2 is a side view of the same.
FIG. 3 is an explanatory side view of the front aircraft.
FIG. 4 is an explanatory front view of the same.
FIG. 5 is an explanatory side view of a drive unit.
FIG. 6 is an explanatory front view of the same.
FIG. 7 is an explanatory diagram of the same plane.
FIG. 8 is a drive system diagram of the mission case.
FIG. 9 is a rear view of the same cross section.
FIG. 10 is an enlarged view of the previous figure.
FIG. 11 is an engine output system diagram.
FIG. 12 is a hydraulic circuit diagram.
FIG. 13 is a drive system diagram of a counter case.
FIG. 14 is a plan view of the same section.
FIG. 15 is an enlarged view of the same.
FIG. 16 is a front view of the same appearance.
FIG. 17 is a plan view of the same.
FIG. 18 is a side view of the same.
FIG. 19 is a plan view of a threshing clutch portion.
FIG. 20 is a rear view of the same.
FIG. 21 is a control circuit diagram.
FIG. 22 is a flowchart of the previous figure.
FIG. 23 is an explanatory diagram of mounting a torque limiter.
FIG. 24 is an enlarged explanatory view of the same.
FIG. 25 is an exploded explanatory view of the same.
FIG. 26 is an explanatory diagram of the development.
27 is an enlarged explanatory view of FIG. 25. FIG.
FIG. 28 is an exploded explanatory view of a cutting pulley.
[Explanation of symbols]
25 Counter case (gear case)
125 Transmission shaft
225 spline
230 Outer case
233 Torque roller
234 Torque plate
235 inner plate
236 skin
243 oil hole

Claims

In the cylindrical outer case, a plurality of donut plate-shaped inner plates, torque plates and outer plates are coaxially arranged on the transmission shaft inserted through the outer case,
In the torque plate, a plurality of torque rollers are arranged on the same circumference, and the outer peripheral surface of the torque roller is projected on both side surfaces of the torque plate so as to be in sliding contact with the inner plate and the outer plate.
While the inner plate is engaged with the transmission shaft, the outer plate is engaged with the outer case to generate sliding friction while rolling the torque roller,
An oil hole is formed in the transmission shaft, one end of the oil hole is opened in the peripheral surface of the transmission shaft, and an oil passage notch is formed in the inner hole of the inner plate, which is generated by rotation of the transmission shaft. A torque limiter characterized in that, by centrifugal force, oil is moved in the direction of the torque roller of each torque plate arranged in multiple layers through the oil hole and oil passage notch , and the torque roller is forcibly lubricated by centrifugal force.