JP4279381B2 - Combine - Google Patents

Description

【０００１】
【発明の属する技術分野】
本発明は圃場の穀稈を連続的に刈取って脱穀するコンバインに関する。
【０００２】
【発明が解決しようとする課題】
従来、本機運転操作部前方に刈取部を配備させた小形構造のコンバインにあっては、運転席に座乗する作業者から分草板の先端側を目線で確認する場合、操向ハンドルや引起しケース上端で視界が遮られて、その確認が短時間の間には充分に行えないという問題があった。また、走行速度を変速させる主変速レバーなど変速操作部材と操向ハンドルとが近接配備された構造においては、例えば左手による変速操作部材、右手による操向ハンドルのそれぞれの操作で相互が近接するときには左手及び右手が干渉するなどして正確な操作が行い難いという問題があった。
【０００３】
【課題を解決するための手段】
そこで、本発明では、運転操作部前方に刈取部を配備させたコンバインにおいて、運転席と刈取部とを近接させると共に、同刈取部最前端の分草板先端部を上記運転席の作業者が目視する目線より後方に、上記刈取部の引起しケースを配置し、同引起しケースより上方で且つ後方に操向ハンドルのチルト支点を設けて、操向ハンドル軸をチルト支点より後方に傾動させるように構成し、運転席と分草板とを近接配置すると共に、同運転席の作業者の視線位置から操向ハンドルの丸形ハンドル操作部の円内に、刈取部の分草板先端部を臨ませるように設けると共に、側面視にて、引起しケースの上端部の直上方位置に丸形ハンドル操作部の前部が位置するようにしたことを特徴とするコンバインを提供するものである。
【０００４】
【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側面図、図２は同平面図であり、図中（１）は左右一対の走行クローラ（２）を装設するトラックフレーム、（３）は前記トラックフレーム（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（７）を内蔵している脱穀部、（８）は刈刃（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（８）を昇降させる油圧シリンダ、（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（１６）を介して搬入する穀物タンク、（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）は旋回用操作部材である丸形操向ハンドル（１９）及び運転席（２０）などを備える運転台、（２１）は運転席（２０）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。
【０００５】
さらに、図３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対の第１油圧ポンプ（２３）及び第１油圧モータ（２４）を備えて走行主変速用の油圧式無段変速機構を形成する変速部材（２５）と、１対の第２油圧ポンプ（２６）及び第２油圧モータ（２７）を備えて旋回用の油圧式無段変速機構を形成する操向部材（２８）とを備え、前記エンジン（２１）の出力軸（２１ａ）に第１及び第２油圧ポンプ（２３）（２６）の入力軸（２９ａ）（２９ｂ）を伝達ベルト（３０ａ）（３０ｂ）によって連結させ、前記各油圧ポンプ（２３）（２６）を駆動するように構成している。
【０００６】
また、前記第１油圧モータ（２４）の出力軸（３１）に、副変速機構（３２）及び差動機構（３３）を介して左右走行クローラ（２）の各駆動輪（３４）を連動連結させるもので、前記差動機構（３３）は左右対称の１対の遊星ギヤ機構（３５）（３５）を有し、各遊星ギヤ機構（３５）は１つのサンギヤ（３６）と、該サンギヤ（３６）の外周で噛合う３つのプラネタリギヤ（３７）と、これらプラネタリギヤ（３７）に噛合うリングギヤ（３８）などで形成している。
【０００７】
前記プラネタリギヤ（３７）はサンギヤ軸（３９）と同軸線上とのキャリヤ軸（４０）のキャリヤ（４１）にそれぞれ回転自在に軸支させ、左右のサンギヤ（３６）（３６）を挾んで左右のキャリヤ（４１）を対向配置させると共に、前記リングギヤ（３８）は各プラネタリギヤ（３７）に噛み合う内歯（３８ａ）を有してサンギヤ軸（３９）とは同一軸芯上に配置させ、キャリヤ軸（４０）に回転自在に軸支させ、キャリヤ軸（４０）を延設して車軸を形成して駆動輪（３４）を軸支させている。
【０００８】
また、走行用の油圧式無段変速部材（２５）は、第１油圧ポンプ（２３）の回転斜板の角度変更調節により第１油圧モータ（２４）の正逆回転と回転数の制御を行うもので、第１油圧モータ（２４）の回転出力を出力軸（３１）の伝達ギヤ（４２）より各ギヤ（４３）（４４）（４５）及び副変速機構（３２）を介して、サンギヤ軸（３９）に固定したセンタギヤ（４６）に伝達してサンギヤ（３６）を回転するように構成している。前記副変速機構（３２）は、前記ギヤ（４４）を有する副変速軸（４７）と、前記ギヤ（４５）を介してセンタギヤ（４６）に噛合うギヤ（４８）を有する駐車ブレーキ軸（４９）とを備え、副変速軸（４７）とブレーキ軸（４９）間に各１対の低速用ギヤ（５０）（５１）・中速用ギヤ（５２）（５３）・高速用ギヤ（５４）（４８）を設けて、低中速スライダ（５５）及び高速スライダ（５６）のスライド操作によって副変速の低速・中速・高速の切換を行うように構成している。なお低速・中速間及び中速・高速間には中立を有する。また前記ブレーキ軸（４９）に駐車ブレーキ（５７）を設けると共に、刈取部（８）に回転力を伝達する刈取ＰＴＯ軸（５８）にギヤ（５９）（６０）及び一方向クラッチ（６１）を介して副変速軸（４７）を連結させ、刈取部（８）を車速同調速度で駆動している。
【０００９】
上記のように、前記センタギヤ（４６）を介しサンギヤ軸（３９）に伝達された第１油圧モータ（２４）からの駆動力を、左右の遊星ギヤ機構（３５）を介して左右キャリヤ軸（４０）に伝達させると共に、左右キャリヤ軸（４０）に伝達された回転を左右の駆動輪（３４）にそれぞれ伝え、左右走行クローラ（２）を駆動するように構成している。
【００１０】
さらに、旋回用の油圧式無段変速機構で形成する操向部材（２８）は、第２油圧ポンプ（２６）の回転斜板の角度変更調節により第２油圧モータ（２７）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（６２）を有するブレーキ軸（６３）と、操向出力クラッチ（６４）を有するクラッチ軸（６５）と、前記の左右リングギヤ（３８）の外歯（３８ｂ）に常時噛合させる左右入力ギヤ（６６）（６７）を設け、第２油圧モータ（２７）の出力軸（６８）に前記ブレーキ軸（６３）及び操向出力クラッチ（６４）を介してクラッチ軸（６５）を連結させ、クラッチ軸（６５）に正転ギヤ（６９）を介して右入力ギヤ（６７）を連結させ、またクラッチ軸（６５）に正転ギヤ（６９）及び逆転ギヤ（７０）を介して左入力ギヤ（６６）を連結させている。そして、副変速スライダ（５５）（５６）の中立によって前記ブレーキ（６２）を入にしかつクラッチ（６４）を切にする一方、前記中立以外の副変速出力時にブレーキ（６２）を切にしかつクラッチ（６４）を入にし、右側のリングギヤ（３８）の外歯（３８ｂ）に正転ギヤ（６９）を介してモータ（２７）回転力を伝え、また左側のリングギヤ（３８）の外歯（３８ｂ）に正転ギヤ（６９）及び逆転ギヤ（７０）を介してモータ（２７）回転を伝え、第２油圧モータ（２７）を正転（逆転）時、左右同一回転数で、左リングギヤ（３８）を逆転（正転）させ、かつ右リングギヤ（３８）を正転（逆転）とさせるように構成している。
【００１１】
而して、旋回用の第２油圧モータ（２７）を停止させて左右リングギヤ（３８）を静止固定させた状態で、走行用の第１油圧モータ（２４）を駆動すると、第１油圧モータ（２４）からの回転出力はセンタギヤ（４６）から左右のサンギヤ（３６）に同一回転数で伝達され、左右遊星ギヤ機構（３５）のプラネタリギヤ（３７）・キャリヤ（４１）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、走行用の第１油圧モータ（２４）を停止させて左右のサンギヤ（３６）を静止固定させた状態で、旋回用の第２油圧モータ（２７）を正逆回転駆動すると、左側の遊星ギヤ機構（３５）が正或いは逆回転、また右側の遊星ギヤ機構（３５）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、走行用の第１油圧モータ（２４）を駆動させながら、旋回用の第２油圧モータ（２７）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、機体の旋回半径は第２油圧モータ（２７）の出力回転数によって決定される。
【００１２】
さらに、図２、図４乃至図１３に示す如く、前記運転台（１８）の前部上面にステアリングコラム（７１）を立設固定させ、ステアリングコラム（７１）上面上方側に操向ハンドル（１９）を縦軸回りに回転自在に取付けると共に、運転台（１８）左側にサイドコラム（７２）を設け、サイドコラム（７２）下方にミッション（２２）を配設させ、走行用変速操作部材である主変速レバー（７３）、副変速レバー（７４）、刈取クラッチレバー（７５）、脱穀クラッチレバー（７６）を前記サイドコラム（７２）に取付ける。また、前記ステアリングコラム（７１）は、アルミニウム合金鋳物を成形加工して形成し、左右に分割自在な２つ割れ構造で複数のボルト（７７）で締結して箱形に形成している。
【００１３】
また、前記ステアリングコラム（７１）上部にチルト台（７８）を一体形成し、チルト台（７８）に支点ボルト（７９）を介してチルトブラケット（８０）を回転自在に軸支させ、チルトレバー（８１）によってチルトブラケット（８０）を角度調節自在に固定させる。前記チルトブラケット（８０）に軸ケース（８２）下部を一体固定させ、コラム（７１）上面に固定させる上面カバー（８３）上方に軸ケース（８２）を延設させ、軸ケース（８２）内部に上ハンドル軸（８４）を回転自在に軸支させ、上ハンドル軸（８４）上端に操向ハンドル（１９）を固定させ、チルトレバー（８１）操作によりチルト支点である支点ボルト（７９）回りにハンドル（１９）を前後方向に移動調節して一定位置に支持させ、ハンドル（１９）取付け位置を前後方向に調節して作業者が操作し易い位置に固定させる。
【００１４】
また、前記上ハンドル軸（８４）の下端部に自在継手（８５）を介して下ハンドル軸（８６）上端側を連結させ、下ハンドル軸（８６）をステアリングコラム（７１）上部に回転自在に軸支させると共に、ステアリングコラム（７１）上部に操向入力軸（８７）上端部を回転自在に軸支させ、下ハンドル軸（８６）のギヤ（８８）と操向入力軸（８７）のセクタギヤ（８９）を噛合させて各軸（８６）（８７）を連結させ、ステアリングコラム（７１）内部の略中央で上下方向に操向入力軸（８７）を延設させる。
【００１５】
さらに、前記ステアリングコラム（７１）の左側面で上下幅略中間に軸受部（９０）を一体形成し、変速入力軸（９１）の一端部を軸受部（９０）にボルト（９２）を介して回転自在に片持ち支持させ、変速入力軸（９１）を左右方向に略水平に軸支させると共に、操向入力軸（８７）下端に自在継手（９３）を介して入力支点軸（９４）上端側を連結させ、入力支点軸（９４）下端側を前記変速入力軸（９１）に回転自在に軸支させる。また、前記入力支点軸（９４）上端側に操向入力部材（９５）を固定させ、変速入力軸（９１）上面と操向入力部材（９５）下面の間に変速入力部材（９６）を挾持させ、入力支点軸（９４）回りに変速入力部材（９６）を回転自在に取付けると共に、変速入力部材（９６）に着脱自在に固定させる連係ボルト（９７）によって前記各入力部材（９５）（９６）を連結させ、また変速入力軸（９１）に設ける挾みバネ（９８）の両端を変速入力部材（９６）に係止させ、変速入力部材（９６）を前記バネ（９８）によって直進中立位置に支持させる。また、前記操向入力軸（８７）の正逆転によって前記各入力部材（９５）（９６）をバネ（９８）に抗して略垂直な入力軸（８７）芯線回りに正逆転させると共に、前記変速入力軸（９１）の正逆転によって略水平な左右方向の入力軸（９１）芯線回りに入力支点軸（９４）及び前記各入力部材（９５）（９６）を前後方向に傾動させるもので、垂直方向の操向入力軸（８７）芯線と左右水平方向の変速入力軸（９１）芯線とが直角交叉する交点に自在継手（９３）を取付け、操向ハンドル（１９）の操向入力軸（８７）正逆転操作により操向入力軸（８７）芯線回りに前記各入力部材（９５）（９６）を正逆転させる。
【００１６】
さらに、前記ステアリングコラム（７１）の下部前側に主変速軸（９９）を回転自在に軸支させ、左右方向に略水平に横架させる主変速軸（９９）の左側端をステアリングコラム（７１）の左側外方に突設させると共に、サイドコラム（７２）下方の機台（３）に回転自在に設ける中介軸（１００）に、リンク（１０１）（１０２）並びに長さ調節ターンバックル（１０３）付きロッド（１０４）を介して主変速軸（９９）を連結させる。また、レバー支点軸（１０５）を介して機台（３）に回転自在に支点板（１０６）を取付け、支点板（１０６）に筒軸（１０７）を介して主変速レバー（７３）基部を左右方向に揺動自在に取付けると共に、支点板（１０６）にリンク（１０８）（１０９）を介して中介軸（１００）を連結させ、主変速レバー（７３）をレバー支点軸（１０５）回りに前後方向に揺動させる変速操作によって主変速軸（９９）を正逆転させる。また、ロッド形主変速部材（１１０）及び上下リンク（１１１）（１１２）を介して変速入力軸（９１）に主変速軸（９９）を連結させ、主変速レバー（７３）の主変速軸（９９）正逆転操作により前記各入力部材（９５）（９６）を変速入力軸（９１）芯線回りに前後に傾動させる。
【００１７】
さらに、筒軸形の操向出力軸（１１３）を前記主変速軸（９９）に回転自在に取付け、リンク形操向出力部材（１１４）を操向出力軸（１１３）に固定させると共に、ロッド形操向結合部材（１１５）の上端部を前記操向入力部材（９５）に自在継手形操向入力連結部（１１６）を介して連結させ、球関継手形操向出力連結部（１１７）を介して操向結合部材（１１５）の下端部を操向出力部材（１１４）に連結させ、走行進路を変更させる操向機構（１１８）を構成している。
【００１８】
さらに、前記操向出力軸（１１３）の上方で該軸（１１３）と略平行に変速出力軸（１１９）をステアリングコラム（７１）内部に回転自在に軸支させ、リンク形変速出力部材（１２０）を変速出力軸（１１９）に固定させると共に、ロッド形変速結合部材（１２１）の上端部を前記変速入力部材（９６）に自在継手形変速入力連結部（１２２）を介して連結させ、球関継手形変速出力連結部（１２３）を介して変速結合部材（１２１）の下端部を変速出力部材（１２０）に連結させ、走行速度の変更並びに前後進の切換を行う変速機構（１２４）を構成している。
【００１９】
さらに、互に回転自在な二重軸構造の内側の変速操作軸（１２５）並びに外側の操向操作軸（１２６）をステアリングコラム（７１）の下部後側で左右幅中央の軸受部（１２７）に回転自在に取付けるもので、長さ調節自在な球関継手軸（１２８）及び変速リンク（１２９）（１３０）を介して前記変速出力軸（１１９）に変速操作軸（１２５）上端部を連結させると共に、長さ調節自在な球関継手軸（１３１）及び操向リンク（１３２）（１３３）を介して前記操向出力軸（１１３）に操向操作軸（１２６）上端部を連結させる。
【００２０】
また、前記各操作軸（１２５）（１２６）は同一軸芯上に略垂直にステアリングコラム（７１）底部に立設させ、各操作軸（１２５）（１２６）上端部をステアリングコラム（７１）内部に延設させて各出力軸（１１３）（１１９）に連結させると共に、ステアリングコラム（７１）底面下方に各操作軸（１２５）（１２６）下端部を突設させ、前記運転台（２０）の作業者搭乗ステップ（１３４）下面側に各操作軸（１２５）（１２６）下端側を延設させるもので、前記変速部材（２５）の出力制御軸（１３５）に車速制御アーム（１３６）を固定させ、ターンバックル（１３７）付き長さ調節自在ロッド（１３８）及びリンク（１３９）を介して前記変速操作軸（１２５）下端部に車速制御アーム（１３６）を連結させ、出力制御軸（１３５）の正逆転操作により第１油圧ポンプ（２３）斜板角調節を行って第１油圧モータ（２４）の回転数制御及び正逆転切換を行い、走行速度（車速）の無段階変更並びに前後進の切換を行う。また、前記操向部材（２８）の出力制御軸（１４０）に操向制御アーム（１４１）を固定させ、ターンバックル（１４２）付き長さ調節自在ロッド（１４３）及びリンク（１４４）を介して操向操作軸（１２６）下端部に操向制御アーム（１４１）を連結させ、出力制御軸（１４０）の正逆転操作により第２油圧ポンプ（２６）斜板角調節を行って第２油圧モータ（２７）の回転数制御及び正逆転切換を行い、操向角度（旋回半径）の無段階変更並びに左右旋回方向の切替を行う。
【００２１】
さらに、前記ステアリングコラム（７１）の右側外面にアクセルレバー（１４５）を前後方向回転自在に設け、エンジン（２１）にアクセルレバー（１４５）を連結させるアクセルワイヤ（１４６）をステアリングコラム（７１）前面内側に沿わせて下方から延出させ、アクセルレバー（１４５）によってエンジン（２１）回転数を手動調節すると共に、前記ステアリングコラム（７１）後面にメンテナンス窓（１４７）を開設させ、着脱自在な蓋（１４８）によってメンテナンス窓（１４７）を閉鎖している。
【００２２】
上記から明らかなように、エンジン（２１）の駆動力を左右走行クローラ（２）に伝える差動機構（３３）と、左右走行クローラ（２）の駆動速度を無段階に変更させる変速部材（２５）と、左右走行クローラ（２）の駆動速度の差を無段階に変化させる操向部材（２８）を設けると共に、操向操作具である操向ハンドル（１９）によって回転させる操向入力軸（８７）と、変速操作具である主変速レバー（７３）によって回転させる変速入力軸（９１）と、変速入力軸（９１）を変速部材（２５）に連結させる変速機構（１２４）と、操向入力軸（８７）を操向部材（２８）に連結させる操向機構（１１８）を設け、変速機構（１２４）動作量に比例させて操向機構（１１８）操向量を変化させるもので、高速側走行変速によって操向量を自動的に拡大させ、かつ低速側走行変速によって操向量を自動的に縮少させ、操向ハンドル（１９）の一定量の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、農作業走行速度の変更並びに作物列などに機体を沿わせる進路修正などを行わせる。また、操向入力軸（８７）に操向入力部材（９５）と変速入力部材（９６）を設け、変速入力軸（９１）芯線回りに変速入力部材（９６）と操向入力部材（９５）を回転自在に取付け、変速出力軸（１１９）に設ける変速出力部材（１２０）に変速結合部材（１２１）を介して変速入力部材（９６）を連結させ、操向出力軸（１１３）に設ける操向出力部材（１１４）に操向結合部材（１１５）を介して操向入力部材（９５）を連結させ、変速機構（１２４）並びに操向機構（１１８）を形成し、操向操作によって操向入力軸（８７）を回転させて操向入力部材（９５）及び変速入力部材（９６）を作動させ、例えば旋回させ乍ら走行速度を減速させる動作を行わせると共に、変速操作によって変速入力軸（９１）を回転させて変速入力部材（９６）及び操向入力部材（９５）を作動させ、走行変速による旋回半径の拡大縮少並びに走行変速中立による旋回出力の中止などの操作を行わせる。
【００２３】
また、操向入力部材（９５）と操向結合部材（１１５）を連結させる操向入力連結部（１１６）を変速入力軸（９１）芯線上に配設させ、変速入力部材（９６）と変速結合部材（１２１）を連結させる変速入力連結部（１２２）を、変速入力軸（９１）芯線と交叉する直線（Ａ）上に配設させ、操向入力軸（８７）及び変速入力軸（９１）を中心とする操向入力部材（９５）及び変速入力部材（９６）の相対的な運動を容易に設定でき、設計及び組立及び構造の簡略化並びに動作の信頼性向上などを図れると共に、変速入力軸（９１）芯線と操向入力軸（８７）芯線が交叉する軸芯交点（Ｂ）を中心とする円周（Ｃ）上に、変速入力連結部（１２２）並びに操向入力連結部（１１６）を配設させ、操向入力部材（９５）及び変速入力部材（９６）などの構造の簡略化及びコンパクト化などを図るもので、変速出力部材（１２０）と変速結合部材（１２１）を連結させる変速出力連結部（１２３）と、操向出力部材（１１４）と操向結合部材（１１５）を連結させる操向出力連結部（１１７）を、操向入力軸（８７）芯線上に配設させ、前進時と後進時の変速切換による逆ハンドル現像を容易に防止し、変速出力部材（１２０）及び操向出力部材（１１４）の設計及び組立及び構造の簡略化並びに動作の信頼性向上などを図ると共に、変速入力軸（９１）と操向入力軸（８７）の軸芯交点（Ｂ）に対する変速出力連結部（１２３）の距離と、操向出力連結部（１１７）の距離を異ならせ、変速出力連結部（１２３）と操向出力連結部（１１７）を同一直線（Ｄ）上で離間させることによって各連結部（１１７）（１２３）の干渉防止並びに移動範囲の設定などを容易に行え、変速結合部材（１２１）及び操向結合部材（１１５）を狭少場所に設置できるように構成している。
【００２４】
また、変速入力連結部（１１６）と、操向入力連結部（１２２）を、変速入力軸（９１）と操向入力軸（８７）の軸芯交点（Ｂ）を中心とする円周（Ｃ）上で約９０度離間させ、変速入力軸（９１）の回転によって操向入力連結部（１１６）を一定位置に維持させかつ変速入力連結部（１２２）の変位量を最大にして走行変速を行わせると共に、前記各入力連結部（１１６）（１２２）を移動させる平面上に変速入力軸（９１）を配置させる構造で各連結部（１１６）（１２２）の移動量を容易に確保し、コンパクトで機能的に変速入力部材（９６）及び操向入力部材（９５）を配置させるもので、操向入力軸（８７）回りに約９０度の範囲内で変速入力連結部（１２２）及び操向入力連結部（１１６）を移動させ、前後進切換による逆ハンドル現像の防止並びに各入力連結部（１１６）（１２２）の移動量の確保と共に、操向入力軸（８７）を回転させる操向角度に応じて変速入力連結部（１２２）を減速方向に移動させる動作と、旋回内側の走行クローラ（２）を中心に方向転換させるスピンターン動作を容易に行わせ、コンパクトな構造で機能的に構成している。変速出力軸（１１９）及び操向出力軸（１１３）を変速入力軸（９１）と略平行に設け、前記各出力軸（１１３）（１１９）を複数に分割自在なケースを形成するコラム（７１）に高精度で軸支させると共に、変速入力軸（９１）並びに前記各出力軸（１１３）（１１９）を左右方向に延設させることによって機体前後方向の連結構造を容易に得られ、主変速レバー（７３）と変速入力軸（９１）の連結、並びに変速部材（２５）及び操向部材（２８）と前記出力軸（１１３）（１１９）との連結を容易に行え、操作構造の簡略化並びに取扱い性向上などを図れるように構成している。
【００２５】
さらに、図１４、図１５に示す如く、前記連係ボルト（９７）を遊嵌挿通させる位相調節孔（１４９）を操向入力部材（９５）に開設させると共に、操向入力軸（８７）芯線を中心とする同一放射線上に複数（３個）のネジ孔（１５０）を設け、前記放射線を中心に操向入力軸（８７）側を底辺とする台形に前記位相調節孔（１４９）を形成するもので、直進位置の操向ハンドル（１９）を左右回転操作したとき、前記ネジ孔（１５０）に固定させた連係ボルト（９７）が位相調節孔（１４９）縁に当接するまで、変速入力部材（９６）を挾みバネ（９８）によって一定位置に固定させた状態で、操向入力部材（９５）だけを回転させ、走行速度を略一定に保ち乍ら左右に旋回させて進路を修正する。そして、連係ボルト（９７）が位相調節孔（１４９）縁に当接したとき、操向ハンドル（１９）をさらに同一方向に回転操作することにより、連係ボルト（９７）の連結によって操向入力部材（９５）と変速入力部材（９６）の両方がバネ（９８）に抗して回転し、走行速度を減速させ乍ら進路修正を行うもので、操向ハンドル（１９）操作によって決定される旋回半径と走行速度の減速量が比例して変化すると共に、操向ハンドル（１９）を直進位置に戻すことにより、挾みバネ（９８）によって変速入力部材（９６）が中立位置に戻され、元の走行速度に自動的に復帰する。また、連係ボルト（９７）を各ネジ孔（１５０）に付け換えることにより、位相調節孔（１４９）縁に連係ボルト（９７）が当接するまでの操向入力部材（９５）の回転角度が変化し、操向ハンドル（１９）操作による走行速度の減速開始時期を調整できると共に、操向ハンドル（１９）を直進支持しているとき、挾みバネ（９８）によって変速入力部材（９６）が変速入力軸（９１）に固定され、機械振動などによって変速入力部材（９６）が遊動するのを防ぎ、変速入力部材（９６）のふらつきによって走行速度が減速変化するのを阻止している。
【００２６】
さらに、図１６乃至図２０に示す如く、前記ギヤ（８８）は、２７０度の外周範囲に複数の歯（１５１）を形成し、９０度の外周範囲を円弧（１５２）に形成し、操向ハンドル（１９）の全回転角度を２７０度とし、左操向回転または右操向回転の角度を１３５度に設定し、操向ハンドル（１９）回転操作を片手で作業者が容易に行えるように形成する。また、前記セクタギヤ（８９）は、１３０度の外周範囲に複数の歯（１５３）を形成し、２３０度の外周範囲を円弧カム（１５４）に形成し、前記ギヤ（８８）の歯（１５１）とセクタギヤ（８９）の歯（１５３）を噛合せ、各ギヤ（８８）（８９）の最大正逆転時、前記円弧（１５２）両端のストッパ（１５５）と前記円弧カム（１５４）両端のストッパ（１５６）を当接させ、操向ハンドル（１９）の回転を規制すると共に、操向入力軸（８７）芯線回りに操向入力部材（９５）及び変速入力部材（９６）を６５度の範囲で正転または逆転させ、各入力部材（９５）が回転移動する平面上に変速入力軸（９１）及び主変速部材（１１０）上端部を配置させる空間を確保し、変速入力軸（９１）芯線上に操向入力連結部（１１６）を設ける構造、並びに同一円周上で前記各入力連結部（１１６）（１２２）を９０度離間させる構造を容易に得られ、構造のコンパクト化、設計組立の簡略化などを図れるように構成している。
【００２７】
また、前記セクタギヤ（８９）の円弧カム（１５４）中央に直進ノッチ（１５７）を形成すると共に、前記ステアリングコラム（７１）上面壁にデテント軸（１５８）を回転自在に軸支させ、デテント軸（１５８）下端部にデテントアーム（１５９）を固定させ、デテントアーム（１５９）にローラ軸（１６０）を介してデテントローラ（１６１）を回転自在に軸支させ、前記円弧カム（１５４）にデテントローラ（１６１）を当接させ、直進ノッチ（１５７）に係脱自在にデテントローラ（１６１）を係合させ、操向ハンドル（１９）を直進位置に支持させる。また、前記デテント軸（１５８）上端側にデテントレバー（１６２）を固定させ、デテント軸（１５８）に巻装させる中立バネ（１６３）の一端をデテントレバー（１６２）に係止させ、ステアリングコラム（７１）の受板（１６４）に中立バネ（１６３）の他端を当接させ、円弧カム（１５４）及び直進ノッチ（１５７）にデテントローラ（１６１）を中立バネ（１６３）によって弾圧当接させている。また、操向ハンドル（１９）の直進位置をオンオフ切換によって電気的に検出するマイクロスイッチ型直進センサ（１６５）をデテントレバー（１６２）に取付けている。
【００２８】
而して、前記主変速レバー（７３）が中立のとき、操向ハンドル（１９）の正転（逆転）操作により、操向入力軸（８７）芯線回りに前記各入力部材（９５）（９６）及び各結合部材（１１５）（１２１）が円錐軌跡上で移動し、前記各出力部材（１１４）（１２０）及び各出力軸（１１３）（１１９）が停止した状態が維持される。
【００２９】
また、主変速レバー（７３）を前方（後方）に倒す前進（後進）操作により、前記各入力部材（９５）（９６）が変速入力軸（９１）芯線回りに前方（後方）に傾き、操向入力連結部（１１６）が一定位置に停止した状態を維持し乍ら、変速入力連結部（１２２）を上方（下方）に移動させ、変速出力部材（１２０）の上方（下方）揺動によって変速出力軸（１１９）を正転（逆転）させ、変速部材（２３）の第１油圧ポンプ（２３）の斜板角切換によって第１油圧モータ（２４）を正転（逆転）させ、第１油圧モータ（２４）の出力軸（３１）の正転（逆転）によって左右走行クローラ（２）を前進（後進）駆動する。また、主変速レバー（７３）の倒し角に比例して出力軸（３１）の回転数が変化し、走行クローラ（２）の前進（後進）速度が無段階に変速される。
【００３０】
さらに、主変速レバー（７３）を前方（後方）に倒して前進（後進）操作を行っている状態下で、操向ハンドル（１９）を左方向（右方向）に回転させることにより、変速入力軸（９１）芯線回りに操向入力部材（９５）が前方（後方）に傾いた姿勢で操向入力軸（８７）芯線回りに正転（逆転）し、操向入力連結部（１１６）が下方（上方）に移動し、操向出力部材（１１４）の下方（上方）揺動によって操向出力軸（１１３）を正転（逆転）させ、操向部材（２８）の第２油圧ポンプ（２６）の斜板角切換によって第２油圧モータ（２７）を正転（逆転）させ、第２油圧モータ（２７）の出力軸（６８）の正転（逆転）により、左走行クローラ（２）を減速（増速）させ、かつ右走行クローラ（２）を増速（減速）させ、左方向（右方向）に機体を旋回させて左方向（右方向）に進路を修正する。また、前記の進路修正動作と同時に、操向ハンドル（１９）の左方向（右方向）回転により、変速入力軸（９１）芯線回りに変速入力部材（９６）が前方（後方）に傾いた状態で操向入力軸（８７）芯線回りに正転（逆転）し、変速入力連結部（１２２）が下方（上方）に移動し、変速出力部材（１２０）の下方（上方）揺動によって変速出力軸（１１９）を逆転（正転）させ、変速部材（２５）を中立方向に戻す制御を行って出力軸（３１）の回転数を低下させ、走行速度（車速）を減速させる。このように、走行移動中の操向ハンドル（１９）の左右操向操作により、操向ハンドル（１９）の回転角度に比例して、進路を修正する旋回半径（角度）と、走行速度の減速量が変化し、操向ハンドル（１９）を大きく回転させることによって左右走行クローラ（２）の速度差を大きくして旋回半径を小さくすると同時に、走行速度の減速量が多くなって車速が遅くなると共に、前進時と後進時とでは、操向ハンドル（１９）の回転に対して旋回入力連結部（１１６）の動きを逆方向にし、前後進の何れにおいても操向ハンドル（１９）の回動操作方向と機体の旋回方向とを一致させ、回転操作する丸形の操向ハンドル（１９）の回転操作によって例えばトラクタまたは田植機など四輪自動車と同様の運転感覚で進路修正及び方向転換などを行う。
【００３１】
さらに、図１９、図２０は機体の左右旋回時における操向ハンドル（１９）の切れ角と左右走行クローラ（２）の速度の関係を示すもので、ハンドル（１９）の切れ角が大となる程左右走行クローラ（２）の速度差は大となると共に、左右走行クローラ（２）の平均速度となる機体中心速度も走行速度（高速・標準・低速）状態に応じて減速される。直進位置の操向ハンドル（１９）を左方向（右方向）に約１５度回転させると、前記位相調節孔（１４９）内を連係ボルト（９７）が移動し、挾みバネ（９８）によって変速入力部材（９６）が直進と同一位置に維持されると共に、操向部材（２８）の第２油圧ポンプ（２６）によって第２油圧モータ（２７）を正転（逆転）させる操向出力によって左方向（右方向）に旋回させ、未刈り穀稈（作物）列の湾曲に合せる進路修正を行う。このとき、旋回内側の走行クローラ（２）の減速量と、旋回外側の走行クローラ（２）の増速量が略等しくなり、機体中心速度が直進と略同一速度に保たれる。また、操向ハンドル（１９）を直進位置から１５度以上回転させると、挾みバネ（９８）に抗して変速入力部材（９６）が左旋回及び右旋回のいずれでも減速動作し、第１油圧ポンプ（２３）及びモータ（２４）の走行変速出力を減速させ、左右走行クローラ（２）（２）を同一方向に回転駆動させて前進（または後進）させ、左右走行クローラ（２）（２）の走行速度差により左方向（右方向）に旋回するブレーキターン動作を行わせ、未刈り穀稈（作物）列から外れたときに元の列に戻したり隣の列に移動させる進路修正を行う。さらに、操向ハンドル（１９）を約１３５度回転させると、機体中心速度が直進時の約４分の１に減速され、旋回内側の走行クローラ（２）が逆転駆動され、旋回内側の走行クローラ（２）を中心として機体が旋回するスピンターン動作が行われ、左右走行クローラ（２）の左右幅だけ旋回方向にずらせて機体を１８０度方向転換させるもので、ハンドル角度０度からハンドル角度１３５度の範囲で操向ハンドル（１９）を回転させて左または右方向の旋回操作を行い、直進位置を中心とした左右１５度のハンドル（１９）回転範囲で未刈り穀稈（作物）列に沿って移動する条合せ進路修正を、直進時の走行速度を維持し乍ら行うと共に、直進位置から左右１３５度のハンドル（１９）回転により、圃場枕地で機体を方向転換させて次作業工程に移動させるスピンターン動作を、直進時の約４分の１の走行速度に自動的に減速して行う。
【００３２】
さらに、副変速を標準（秒速１．５メートル）速度に保ち、操向ハンドル（１９）を９０度回転させたとき、主変速レバー（６８）操作により主変速出力を高速及び３分の２及び３分の１に変更しても、機体の旋回半径が略一定に保たれた状態で、旋回速度（機体中心速度）だけを変化させる。また、直進位置を基準として連係ボルト（９７）と位相調節孔（１４９）の設定範囲で第１油圧ポンプ（２３）第１油圧モータ（２４）を直進状態に維持させ、農作業中に作物列または畦などに機体を沿わせる操向操作を行っても走行速度が不均一に変化するのを防止し、略同一走行速度を保ち乍ら農作業中の進路修正を行え、作業者の運転感覚と機体の走行動作とを略一致させて適正な操向操作を行える。また、主変速レバー（７３）の変速基準値を切換える副変速レバー（７４）副変速操作の低速及び標準及び高速切換に比例させて旋回半径を小径乃至大径に変化させ、第１油圧ポンプ（２３）及びモータ（２４）と走行クローラ（２）間の減速比並びに第２油圧ポンプ（２６）及びモータ（２７）と走行クローラ（２）間の減速比の設定、或いはスピンターン動作に必要な小半径旋回に必要な走行駆動力の確保などを図ると共に、同一副変速操作位置で主変速レバー（７３）を操作することによって旋回半径を略一定に保った状態で旋回時の走行速度を変化させ、作業者の熟練度などに応じた運転操作を行え、機動性の向上並びに運転操作性の向上などを図る。
【００３３】
ところで図２１乃至図２６に示す如く、前記操向部材（２８）より出力される旋回操作力に対し、大きな走行駆動力を必要とする変速部材（２５）を形状的に大形（大容量）に、操向部材（２８）を小形（小容量）に形成すると共に、前記ミッションケース（２２）上部の前側に操向部材（２８）を、また後側に変速部材（２５）を一体的に固設し、ミッションケース（２２）前方に操向部材（２８）が突出するのを最小に抑制して、ミッションケース（２２）上部にコンパクトにこれら変速部材（２５）（２８）を配設させるように構成している。
【００３４】
そして、前記変速及び操向部材（２５）（２８）を出力制御する車速及び操向制御アーム（１３６）（１４１）基端のボス部（１３６ａ）（１４１ａ）を各部材（２５）（２８）の油圧ポンプ（２３）（２６）上側の制御軸（１３５）（１３６）にボルト（１３６ｂ）（１４１ｂ）を介し取外し自在に固定させて、各ロッド（１３８）（１４３）との連結の容易化やメンテナンス性の向上化を図ると共に、変速部材（２５）及び操向部材（２８）を構成する第１及び第２油圧ポンプ（２３）（２６）の入力軸（２９ａ）（２９ｂ）を各部材（２５）（２８）の左外側に突出させて、ミッションケース（２２）の後方に配設するエンジン（２１）左側のエンジン出力軸（２１ａ）に、プーリ（１６６）（１６７）及びベルト（３０ａ）及びテンションプーリ（１６８）を介して前記第１油圧ポンプ（２３）の入力軸（２９ａ）を連動連結させ、第２油圧ポンプ（２６）の入力軸（２９ｂ）にプーリ（１６７）（１６９）及びベルト（３０ｂ）及びテンションプーリ（１７０）を介して第１油圧ポンプ（２３）の入力軸（２９ａ）を連動連結させて、旋回より走行を優先させた駆動を行うように構成している。
【００３５】
またエンジン（２１）と第１油圧ポンプ（２３）間を連結する走行用ベルト（３０ａ）より第１及び第２油圧ポンプ（２３）（２６）間を連結する旋回用ベルト（３０ｂ）をポンプ（２３）（２６）側に近接させて、走行用ベルト（３０ａ）の前方で旋回用ベルト（３０ｂ）の左側方に空きスペース（１７１）を形成させ、この空きスペース（１７１）分刈取部（８）を干渉させることなく変速及び操向部材（２５）（２８）側に近接させて、機体全体をコンパクトとさせるように構成している。
【００３６】
また、車速制御アーム（１３６）とロッド（１３８）とは軸（１７２）及び長孔（１７３）を介して中立域で若干の融通を有して連結させ、操向制御アーム（１４１）とロッド（１４３）とは軸（１７４）を介して連結させ、各制御アーム（１３６）（１４１）に中立保持用デテント板（１７５）を一体連結させると共に、各油圧ポンプ（２３）（２６）外壁に固定するデテント軸（１７６）にデテントアーム（１７７）を回動自在に枢支させ、該デテントアーム（１７７）に軸受するデテントローラ（１７８）をバネ（１７９）力で前記デテント板（１７５）の凹部中立ノッチ（１７５ａ）に弾圧当接させるとき、各制御アーム（１３６）（１４１）の中立位置を保持させるように構成している。
【００３７】
なお、（１８０）は前記ＰＴＯ軸（５８）にプーリ（１８１）（１８２）及びベルト（１８３）及びテンションプーリ式刈取クラッチ（１８４）を介し連動連結して刈取部（８）を駆動する刈取入力軸、（１８５）は前記エンジン出力軸（２１ａ）にプーリ（１６６）（１８６）及びベルト（１８７）及びテンションプーリ式脱穀クラッチ（１８８）を介し連動連結して脱穀部（４）を駆動する脱穀入力軸である。
【００３８】
図２２、図２７、図２８に示す如く、運転席（２０）に座乗する作業者から刈取部（８）最前端の分草板（１８９）先端部を目視する目線（Ｍ）より後方に、引起しケース（１９０）及びハンドル軸（８４）（８６）を配置させると共に、前記引起しケース（１９０）より上方で且つ後方に前記支点ボルト（７９）を配置させ、ハンドル軸（８４）（８６）を支点ボルト（７９）より後方に傾動させるように設けるもので、運転席（２０）と刈取部（８）とが比較的近接する小型コンパクト構造のコンバイン機体の運転席（２０）位置で作業者が運転操作中においては、刈取部（８）の先端側を確認する作業者の目線（Ｍ）が引起しケース（１９０）や操向ハンドル（１９）の軸（８４）（８６）部に遮られるのを防いで、運転席（２０）位置より常に刈取部（８）を良好に確認しながらの適正な刈取作業を可能とさせるように構成している。
【００３９】
また、運転席（２０）の作業者の視線位置から操向ハンドル（１９）の丸形ハンドル操作部（１９ａ）の円内を通して分草板（１８９）先端部を目視するように設けて、作業者の視線位置から丸形ハンドル操作部（１９ａ）の円内空間域に分草板（１８９）先端部を臨ませるように設けると共に、側面視にて、引起しケース（１９０）の上端部の直上方位置に丸形ハンドル操作部（１９ａ）の前部が位置するようにして、運転席（２０）に分草板（１８９）が近接するコンバイン構造においても、運転作業中は操向ハンドル（１９）に目線（Ｍ）を遮られることなく、分草板（１８９）先端の作業状況を容易に確認しながらの良好な作業を可能とさせるように構成している。
【００４０】
さらに、図２８に示す如く、前記主変速レバー（７３）は最方位置（最高速位置）に傾動させたときに、レバー操作部（７３ａ）をハンドル軸（８４）の軸芯に近接させ、ハンドル軸（８４）より後方で主変速レバー（７３）を前後方向に揺動操作するように設けて、操向ハンドル（１９）と主変速レバー（７３）とが比較的近接配備された構造のコンバインにおいて、左手で主変速レバー（７３）を右手で操向ハンドル（１９）を握っての作業中に右手と左手とが干渉する不都合を最大回避させて、これら操向ハンドル（１９）及び主変速レバー（７３）それぞれの容易且つ正確な操作を可能とさせるように構成している。
【００４１】
【発明の効果】
本発明では、運転操作部前方に刈取部（８）を配備させたコンバインにおいて、運転席（２０）と刈取部（８）とを近接させると共に、同刈取部（８）最前端の分草板（１８９）先端部を上記運転席（２０）の作業者が目視する目線（Ｍ）より後方に、上記刈取部（８）の引起しケース（１９０）を配置し、同引起しケース（１９０）より上方で且つ後方に操向ハンドル（１９）のチルト支点（７９）を設けて、操向ハンドル軸（８４）をチルト支点（７９）より後方に傾動させるように構成し、運転席（２０）と分草板（１８９）とを近接配置すると共に、同運転席（２０）の作業者の視線位置から操向ハンドル（１９）の丸形ハンドル操作部（１９ａ）の円内に、刈取部（８）の分草板（１８９）先端部を臨ませるように設けると共に、側面視にて、引起しケース（１９０）の上端部の直上方位置に丸形ハンドル操作部（１９ａ）の前部が位置するようにしている。
【００４２】
従って、運転席（２０）位置で作業者が運転操作中、刈取部（８）の先端側を確認する作業者の目線（Ｍ）が引起しケース（１９０）や操向ハンドル（１９）で遮られるのを防いで、運転席（２０）位置より常に刈取部（８）を良好に確認しながらの適正な刈取作業を可能とさせることができる。
しかも、運転席（２０）位置と刈取部（８）とが比較的近接した小型コンパクト構造のコンバインにおいても、運転席（２０）位置より操向ハンドル（１９）の丸形ハンドル操作部（１９ａ）円内の空間域を通して、運転席（２０）に近接配置した分草板（１８９）先端部の作業状況を、容易に確認して良好に作業を行うことができる。
【図面の簡単な説明】
【図１】コンバインの全体側面図。
【図２】コンバインの全体平面図。
【図３】ミッション駆動系の説明図。
【図４】走行変速及び操向操作部の説明斜視図。
【図５】同部の作動説明図。
【図６】ステアリングコラムの側面図。
【図７】同上部拡大側面図。
【図８】同下部拡大側面図。
【図９】ステアリングコラムの正面図。
【図１０】同上部拡大正面図。
【図１１】同下部拡大正面図。
【図１２】図４の平面説明図。
【図１３】同拡大図。
【図１４】ステアリングコラム横断面図。
【図１５】図１４の分解説明図。
【図１６】ステアリングコラム上部の部分平面図。
【図１７】同部分図。
【図１８】図１７の作動説明図。
【図１９】主変速と操向ハンドル操作を表わす線図。
【図２０】副変速と操向ハンドル操作を表わす線図。
【図２１】運転操作部の正面説明図。
【図２２】運転操作部の平面説明図。
【図２３】ミッションケース部の側面説明図。
【図２４】ミッションケース部の平面説明図。
【図２５】変速及び旋回部材部の側面説明図。
【図２６】変速及び旋回部材部の平面説明図。
【図２７】運転部の側面説明図。
【図２８】運転操作部の側面説明図。
【符号の説明】
（８） 刈取部
（１９） 操向ハンドル
（１９ａ） ハンドル操作部
（２０） 運転席
（７３） 主変速レバー（変速操作部材）
（７９） 支点ボルト（チルト支点）
（８４） ハンドル軸
（１８９） 分草板
（１９０） 引起しケース[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a combine that continuously harvests and thresh cereal grains in a field.
[0002]
[Problems to be solved by the invention]
Conventionally, in a combine having a small structure in which a cutting part is provided in front of the operation part of the machine, when checking the tip side of the weed board from the operator sitting on the driver's seat, There was a problem that the visibility was blocked at the upper end of the case and the confirmation could not be performed sufficiently in a short time. Further, in a structure in which a shift operation member such as a main shift lever for shifting the traveling speed and a steering handle are arranged close to each other, for example, when the shift operation member with the left hand and the steering handle with the right hand are in close proximity to each other, There is a problem that it is difficult to perform an accurate operation because the left hand and the right hand interfere with each other.
[0003]
[Means for Solving the Problems]
Therefore, in the present invention, in the combine in which the mowing unit is arranged in front of the driving operation unit, the driver seat and the mowing unit are brought close to each other , and the operator of the driver seat sets the foremost weed plate tip of the mowing unit foremost. The raising case of the cutting part is arranged behind the line of sight, the tilt fulcrum of the steering handle is provided above and behind the raising case, and the steering handle shaft is tilted backward from the tilt fulcrum. The driver's seat and the weeding board are arranged close to each other, and the tip of the weeding board of the cutting part is located in the circle of the round handle operating part of the steering handle from the line of sight of the operator in the driver's seat. And a combine that is characterized in that the front portion of the round handle operating portion is positioned directly above the upper end of the case in a side view. .
[0004]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings. 1 is an overall side view of the combine, and FIG. 2 is a plan view thereof. In FIG. 1, (1) is a track frame on which a pair of left and right traveling crawlers (2) are installed, and (3) is the track frame (1). A machine base to be installed, (4) is a threshing section that stretches the feed chain (5) to the left and incorporates a handling cylinder (6) and a processing cylinder (7), (8) is a cutting blade (9) and grains A cutting part provided with a reed transport mechanism (10), (11) is a hydraulic cylinder that raises and lowers the reeding part (8) via a cutting frame (12), and (13) is a discharge part that faces the end of the waste chain (14). A cocoon processing unit, (15) is a cereal tank that carries the grain from the threshing unit (4) through the milling cylinder (16), and (17) carries the cereal of the tank (15) out of the machine. A discharge auger (18) is a round steering handle (19) and a driver's seat (20) which are operation members for turning. Cab equipped, is configured to threshing harvests (21) the driver's seat (20) an engine provided below, continuously culms.
[0005]
Further, as shown in FIG. 3, the transmission case (22) for driving the traveling crawler (2) includes a pair of first hydraulic pump (23) and first hydraulic motor (24) for traveling main transmission. A speed change member (25) forming a hydraulic continuously variable transmission mechanism, a pair of second hydraulic pump (26) and a second hydraulic motor (27) are provided to form a hydraulic continuously variable transmission mechanism for turning. Direction member (28), and input shafts (29a) (29b) of the first and second hydraulic pumps (23), (26) to the output shaft (21a) of the engine (21). 30b) and the hydraulic pumps (23) and (26) are driven.
[0006]
Further, the drive wheels (34) of the left and right traveling crawler (2) are interlockedly connected to the output shaft (31) of the first hydraulic motor (24) via the subtransmission mechanism (32) and the differential mechanism (33). The differential mechanism (33) has a pair of symmetrical planetary gear mechanisms (35) (35), and each planetary gear mechanism (35) includes one sun gear (36) and the sun gear ( 36) three planetary gears (37) meshing with the outer periphery of the ring 36, and a ring gear (38) meshing with these planetary gears (37).
[0007]
The planetary gear (37) is rotatably supported by the carrier (41) of the carrier shaft (40) coaxial with the sun gear shaft (39), and the left and right sun gears (36) (36) are sandwiched between the left and right carriers. The ring gear (38) has an inner tooth (38a) that meshes with each planetary gear (37) and is arranged on the same axis as the sun gear shaft (39), so that the carrier shaft (40 The carrier shaft (40) is extended to form an axle to support the drive wheel (34).
[0008]
The traveling hydraulic continuously variable transmission member (25) controls forward / reverse rotation and rotation speed of the first hydraulic motor (24) by adjusting and changing the angle of the rotary swash plate of the first hydraulic pump (23). Therefore, the rotation output of the first hydraulic motor (24) is transmitted from the transmission gear (42) of the output shaft (31) via the gears (43) (44) (45) and the auxiliary transmission mechanism (32) to the sun gear shaft. The sun gear (36) is rotated by being transmitted to the center gear (46) fixed to (39). The sub-transmission mechanism (32) includes a sub-transmission shaft (47) having the gear (44) and a parking brake shaft (49) having a gear (48) meshing with the center gear (46) via the gear (45). ), And a pair of low speed gears (50) (51), medium speed gears (52) (53), and high speed gears (54) between the auxiliary transmission shaft (47) and the brake shaft (49). (48) is provided, and the sub-shift is switched between low speed, medium speed, and high speed by the sliding operation of the low and medium speed slider (55) and the high speed slider (56). There is neutrality between low speed and medium speed and between medium speed and high speed. In addition, a parking brake (57) is provided on the brake shaft (49), and gears (59) (60) and a one-way clutch (61) are provided on a cutting PTO shaft (58) that transmits rotational force to the cutting portion (8). The sub-transmission shaft (47) is coupled to the cutting part (8) at the vehicle speed synchronization speed.
[0009]
As described above, the driving force from the first hydraulic motor (24) transmitted to the sun gear shaft (39) via the center gear (46) is transmitted to the left and right carrier shafts (40) via the left and right planetary gear mechanisms (35). ) And the rotation transmitted to the left and right carrier shafts (40) to the left and right drive wheels (34), respectively, to drive the left and right traveling crawler (2).
[0010]
Further, the steering member (28) formed by the turning hydraulic continuously variable transmission mechanism is configured to rotate the second hydraulic motor (27) forward and backward by adjusting the angle of the rotary swash plate of the second hydraulic pump (26). The rotation speed is controlled by a brake shaft (63) having a steering output brake (62), a clutch shaft (65) having a steering output clutch (64), and the left and right ring gears (38). Left and right input gears (66) and (67) that are always meshed with the teeth (38b) are provided, and the output shaft (68) of the second hydraulic motor (27) is connected to the output shaft (68) via the brake shaft (63) and the steering output clutch (64). The clutch shaft (65) is connected, the right input gear (67) is connected to the clutch shaft (65) via the forward rotation gear (69), and the forward rotation gear (69) and the reverse rotation are connected to the clutch shaft (65). The left input gear (66 through the gear (70) And by connecting the. Then, the brake (62) is turned on and the clutch (64) is turned off by the neutral of the auxiliary transmission sliders (55) and (56), while the brake (62) is turned off and the clutch is turned off at the time of the auxiliary transmission other than the neutral. (64) is turned on, the rotational force of the motor (27) is transmitted to the external teeth (38b) of the right ring gear (38) via the forward rotation gear (69), and the external teeth (38b) of the left ring gear (38) ) Is transmitted to the rotation of the motor (27) via the forward rotation gear (69) and the reverse rotation gear (70), and when the second hydraulic motor (27) rotates forward (reverse rotation), the left ring gear (38 ) In the reverse direction (forward rotation) and the right ring gear (38) in the forward direction (reverse rotation).
[0011]
Thus, when the traveling first hydraulic motor (24) is driven in a state where the second hydraulic motor (27) for turning is stopped and the left and right ring gears (38) are stationary and fixed, the first hydraulic motor ( The rotational output from 24) is transmitted from the center gear (46) to the left and right sun gears (36) at the same rotational speed, and the left and right traveling crawlers are transmitted via the planetary gear (37) and carrier (41) of the left and right planetary gear mechanism (35). (2) is driven at the same rotational speed in the same rotational direction on the left and right, and the machine body travels straight forward and backward. On the other hand, when the second hydraulic motor (27) for rotation is driven to rotate in the forward and reverse directions with the first hydraulic motor (24) for traveling stopped and the left and right sun gears (36) stationary and fixed, the planet on the left side The gear mechanism (35) rotates forward or backward, and the right planetary gear mechanism (35) rotates backward or forward, driving the left and right traveling crawler (2) in the reverse direction and turning the aircraft to the left or right. Further, by driving the second hydraulic motor (27) for turning while driving the first hydraulic motor (24) for traveling, the aircraft turns left and right to correct the course. The turning radius is determined by the output rotational speed of the second hydraulic motor (27).
[0012]
Further, as shown in FIGS. 2 and 4 to 13, a steering column (71) is vertically fixed on the upper surface of the front portion of the cab (18), and a steering handle (19) is disposed on the upper surface of the steering column (71). ) Is rotatably mounted around the vertical axis, a side column (72) is provided on the left side of the cab (18), a transmission (22) is provided below the side column (72), and this is a traveling speed change operation member. A main transmission lever (73), an auxiliary transmission lever (74), a mowing clutch lever (75), and a threshing clutch lever (76) are attached to the side column (72). The steering column (71) is formed by molding an aluminum alloy casting, and is formed into a box shape by fastening with a plurality of bolts (77) in a split structure that can be divided into left and right.
[0013]
Further, a tilt base (78) is integrally formed on the steering column (71), and a tilt bracket (80) is rotatably supported on the tilt base (78) via a fulcrum bolt (79). The tilt bracket (80) is fixed by 81) so that the angle can be adjusted. The lower part of the shaft case (82) is integrally fixed to the tilt bracket (80), the shaft case (82) is extended above the upper surface cover (83) to be fixed to the upper surface of the column (71), and the shaft case (82) is disposed inside. The upper handle shaft (84) is rotatably supported, the steering handle (19) is fixed to the upper end of the upper handle shaft (84), and the tilt lever (81) is operated around the fulcrum bolt (79) as a tilt fulcrum. The handle (19) is moved and adjusted in the front-rear direction to be supported at a fixed position, and the handle (19) mounting position is adjusted in the front-rear direction to be fixed at a position where the operator can easily operate.
[0014]
Further, the upper end side of the lower handle shaft (86) is connected to the lower end portion of the upper handle shaft (84) via a universal joint (85) so that the lower handle shaft (86) can be rotated to the upper portion of the steering column (71). The upper end of the steering input shaft (87) is rotatably supported on the upper part of the steering column (71), and the gear (88) of the lower handle shaft (86) and the sector gear of the steering input shaft (87) are supported. (89) is engaged to connect the shafts (86) and (87), and the steering input shaft (87) is extended in the vertical direction substantially at the center inside the steering column (71).
[0015]
Further, a bearing portion (90) is integrally formed on the left side surface of the steering column (71) in the middle of the vertical width, and one end portion of the transmission input shaft (91) is connected to the bearing portion (90) via a bolt (92). The shift input shaft (91) is pivotally supported in a cantilever manner so as to be rotatable, and the upper end of the input fulcrum shaft (94) is connected to the lower end of the steering input shaft (87) via a universal joint (93). The lower end side of the input fulcrum shaft (94) is rotatably supported on the transmission input shaft (91). Further, the steering input member (95) is fixed to the upper end side of the input fulcrum shaft (94), and the transmission input member (96) is held between the upper surface of the transmission input shaft (91) and the lower surface of the steering input member (95). The transmission input member (96) is rotatably attached around the input fulcrum shaft (94), and the input members (95) (96) are connected to the transmission input member (96) by linkage bolts (97). ), And both ends of a kneading spring (98) provided on the transmission input shaft (91) are locked to the transmission input member (96), and the transmission input member (96) is moved straight to the neutral position by the spring (98). To support. In addition, by rotating the steering input shaft (87) forward and backward, the input members (95) and (96) are rotated forward and backward around the core line of the substantially vertical input shaft (87) against the spring (98). The input fulcrum shaft (94) and the input members (95) and (96) are tilted in the front-rear direction about the substantially horizontal input shaft (91) core line by forward and reverse rotation of the speed change input shaft (91). A universal joint (93) is attached to the intersection point where the vertical steering input shaft (87) core wire and the horizontal shifting input shaft (91) core wire intersect at right angles, and the steering input shaft ( 87) The input members (95) and (96) are rotated in the forward and reverse directions about the steering input shaft (87) about the core line by forward and reverse operations.
[0016]
Further, the main transmission shaft (99) is rotatably supported on the lower front side of the steering column (71), and the left end of the main transmission shaft (99) horizontally mounted in the horizontal direction is connected to the steering column (71). And a link (101) (102) and a length-adjusting turnbuckle (103) on a central shaft (100) that is rotatably provided on the machine base (3) below the side column (72). The main transmission shaft (99) is connected through the attached rod (104). Further, a fulcrum plate (106) is rotatably attached to the machine base (3) via the lever fulcrum shaft (105), and the base of the main transmission lever (73) is attached to the fulcrum plate (106) via the cylindrical shaft (107). The center shaft (100) is connected to the fulcrum plate (106) via the links (108) and (109), and the main speed change lever (73) is rotated around the lever fulcrum shaft (105). The main transmission shaft (99) is rotated in the forward and reverse directions by a shifting operation that swings back and forth. The main transmission shaft (99) is connected to the transmission input shaft (91) via the rod-shaped main transmission member (110) and the upper and lower links (111) (112), and the main transmission shaft ( 99) The input members (95) and (96) are tilted back and forth about the center line of the transmission input shaft (91) by forward and reverse operations.
[0017]
Further, a cylindrical shaft-shaped steering output shaft (113) is rotatably attached to the main transmission shaft (99), the link-type steering output member (114) is fixed to the steering output shaft (113), and the rod An upper end portion of the shape steering coupling member (115) is connected to the steering input member (95) via a universal joint type steering input connecting portion (116), and a ball joint type steering output connecting portion (117) is connected. The steering coupling member (115) is connected to the steering output member (114) via the steering wheel to change the travel path, thereby constituting the steering mechanism (118).
[0018]
Further, a shift output shaft (119) is rotatably supported inside the steering column (71) above the steering output shaft (113) and substantially in parallel with the shaft (113), so that a link type shift output member (120 ) Is fixed to the speed change output shaft (119), and the upper end of the rod-type speed change coupling member (121) is connected to the speed change input member (96) via the universal joint type speed change input connecting portion (122). A transmission mechanism (124) for connecting the lower end portion of the transmission coupling member (121) to the transmission output member (120) via the joint-type transmission output connecting portion (123) and changing the traveling speed and switching between forward and backward travel. It is composed.
[0019]
Furthermore, the inner shift operation shaft (125) and the outer steering operation shaft (126) of the double shaft structure that can rotate with each other are connected to the bearing portion (127) at the center of the left and right width on the lower rear side of the steering column (71). The upper end of the speed change operation shaft (125) is connected to the speed change output shaft (119) via the ball joint shaft (128) and the speed change links (129) (130) which are adjustable in length. At the same time, the upper end portion of the steering operation shaft (126) is connected to the steering output shaft (113) via the ball joint shaft (131) and the steering links (132) (133) that are adjustable in length.
[0020]
The operation shafts (125) (126) are erected on the bottom of the steering column (71) substantially vertically on the same axis, and the upper ends of the operation shafts (125) (126) are located inside the steering column (71). To the output shafts (113) and (119), and the lower end portions of the operation shafts (125) and (126) are projected below the bottom surface of the steering column (71). The lower end side of each operation shaft (125) (126) is extended on the lower surface side of the worker boarding step (134), and the vehicle speed control arm (136) is fixed to the output control shaft (135) of the transmission member (25). The vehicle speed control arm (136) is connected to the lower end portion of the speed change operation shaft (125) via the length adjustable rod (138) with the turnbuckle (137) and the link (139), and the output control shaft (1 5) The first hydraulic pump (23) swash plate angle is adjusted by the forward / reverse operation of 5), the rotation speed control and forward / reverse switching of the first hydraulic motor (24) are performed, and the running speed (vehicle speed) is changed steplessly and before and after. Switch the decimal. Further, the steering control arm (141) is fixed to the output control shaft (140) of the steering member (28), and the length adjustable rod (143) with the turnbuckle (142) and the link (144) are used. A steering control arm (141) is connected to the lower end of the steering operation shaft (126), and the second hydraulic pump (26) swash plate angle is adjusted by forward / reverse operation of the output control shaft (140) to thereby adjust the second hydraulic motor. (27) The rotational speed control and forward / reverse switching are performed, and the steering angle (turning radius) is changed steplessly and the left / right turning direction is switched.
[0021]
Further, an accelerator lever (145) is provided on the right outer surface of the steering column (71) so as to be rotatable in the front-rear direction, and an accelerator wire (146) for connecting the accelerator lever (145) to the engine (21) is connected to the front surface of the steering column (71). Extending from below along the inside, manually adjusting the engine (21) rotation speed by the accelerator lever (145), and opening a maintenance window (147) on the rear surface of the steering column (71) The maintenance window (147) is closed by (148).
[0022]
As is apparent from the above, the differential mechanism (33) that transmits the driving force of the engine (21) to the left and right traveling crawler (2) and the speed change member (25) that changes the driving speed of the left and right traveling crawler (2) steplessly. ) And a steering member (28) for steplessly changing the difference in driving speed between the left and right traveling crawlers (2), and a steering input shaft (19) that is rotated by a steering handle (19) that is a steering operating tool. 87), a transmission input shaft (91) that is rotated by a main transmission lever (73) that is a transmission operation tool, a transmission mechanism (124) that connects the transmission input shaft (91) to the transmission member (25), and steering A steering mechanism (118) for connecting the input shaft (87) to the steering member (28) is provided, and the steering mechanism (118) is changed in proportion to the operation amount of the speed change mechanism (124). Side steering shift Dynamically expanding and automatically reducing the steering amount by the low speed side shifting, and by turning the steering handle (19) by a certain amount, the turning radius of the left and right traveling crawler (2) is substantially reduced regardless of the traveling speed. It is maintained at a constant level, and the speed of the farm work is changed, and the course is corrected to keep the aircraft along the crop line. Further, a steering input member (95) and a transmission input member (96) are provided on the steering input shaft (87), and the transmission input member (96) and the steering input member (95) around the core line of the transmission input shaft (91). Is connected to a transmission output member (120) provided on the transmission output shaft (119) via a transmission coupling member (121), and an operation provided on the steering output shaft (113). The steering input member (95) is connected to the steering output member (114) via the steering coupling member (115) to form the speed change mechanism (124) and the steering mechanism (118). The input shaft (87) is rotated to operate the steering input member (95) and the speed change input member (96), for example, to turn and perform an operation of decelerating the traveling speed. 91) is rotated to change the speed of the input member 96) and actuates the steering input member (95), to perform operations such as stop of the turning output by the running gear Neutral expansion contraction small sequence of turning radius by the running gear.
[0023]
Further, a steering input connecting portion (116) for connecting the steering input member (95) and the steering coupling member (115) is disposed on the core line of the transmission input shaft (91), and the transmission input member (96) and the transmission are changed. The shift input connecting portion (122) for connecting the coupling member (121) is disposed on the straight line (A) intersecting the core line of the shift input shaft (91), and the steering input shaft (87) and the shift input shaft (91). ), The relative movement of the steering input member (95) and the speed change input member (96) can be easily set, the design and assembly and the structure can be simplified, and the operation reliability can be improved. On the circumference (C) centered on the axis center intersection (B) where the input shaft (91) core wire and the steering input shaft (87) core wire intersect, the transmission input connecting portion (122) and the steering input connecting portion ( 116), a steering input member (95) and a transmission input member (9 ) And the like, and a shift output connecting portion (123) for connecting the shift output member (120) and the shift connecting member (121), and the steering output member (114). A steering output connecting portion (117) for connecting the direction coupling member (115) is disposed on the steering input shaft (87) core line, and it is possible to easily prevent reverse handle development due to shift switching between forward and reverse. The design, assembly, and structure of the shift output member (120) and the steering output member (114) are simplified, and the reliability of the operation is improved. The shift input shaft (91) and the steering input shaft (87) The distance between the shift output connecting portion (123) and the steering output connecting portion (117) with respect to the shaft center intersection (B) is made different, so that the shift output connecting portion (123) and the steering output connecting portion (117) are the same. To be separated on a straight line (D) Thus, it is possible to easily prevent interference between the connecting portions (117) and (123), set the movement range, etc., and install the speed change coupling member (121) and the steering coupling member (115) in a narrow place. ing.
[0024]
Further, the shift input connecting portion (116) and the steering input connecting portion (122) are arranged with a circumference (C) centered on the axis intersection (B) of the shift input shaft (91) and the steering input shaft (87). ) About 90 degrees apart, the steering input connecting portion (116) is maintained at a fixed position by the rotation of the speed change input shaft (91), and the displacement of the speed change input connecting portion (122) is maximized. And a structure in which the speed change input shaft (91) is arranged on a plane on which the input connecting portions (116) and (122) are moved, and the amount of movement of the connecting portions (116) and (122) is easily secured. The shift input member (96) and the steering input member (95) are arranged in a compact and functional manner. The shift input connecting portion (122) and the steering input member (122) and the steering input member (95) are within a range of about 90 degrees around the steering input shaft (87). Move the direction input connecting part (116), reverse reverse by switching forward and backward The shift input connecting portion (122) is moved in the decelerating direction according to the steering angle for rotating the steering input shaft (87). And a spin turn operation that changes the direction around the traveling crawler (2) inside the turn, and is functionally configured with a compact structure. A shift output shaft (119) and a steering output shaft (113) are provided substantially in parallel with the shift input shaft (91), and the output shaft (113) (119) is formed into a column (71) that can be divided into a plurality of cases. ) With a high degree of accuracy, and the shifting input shaft (91) and the output shafts (113) and (119) are extended in the left-right direction. The lever (73) can be easily connected to the speed change input shaft (91), and the speed change member (25) and the steering member (28) can be easily connected to the output shaft (113) (119) to simplify the operation structure. In addition, it is configured so as to improve the handleability.
[0025]
Further, as shown in FIGS. 14 and 15, a phase adjusting hole (149) for loosely inserting and inserting the linkage bolt (97) is opened in the steering input member (95), and the steering input shaft (87) core wire is connected. A plurality of (three) screw holes (150) are provided on the same radiation centered, and the phase adjustment hole (149) is formed in a trapezoidal shape with the steering input shaft (87) side as the base centering on the radiation. Thus, when the steering handle (19) in the straight traveling position is rotated left and right, the speed change input member until the linkage bolt (97) fixed to the screw hole (150) contacts the edge of the phase adjustment hole (149). In a state in which (96) is fixed at a certain position by the kneading spring (98), only the steering input member (95) is rotated, and the traveling speed is maintained to be substantially constant, and the left and right are turned to correct the course. . When the linkage bolt (97) contacts the edge of the phase adjusting hole (149), the steering handle (19) is further rotated in the same direction, whereby the steering input member is connected by the linkage bolt (97). (95) and the speed change input member (96) both rotate against the spring (98) to reduce the traveling speed and correct the course, and turn determined by operating the steering handle (19). While the radius and the speed reduction amount change proportionally, the steering handle (19) is returned to the straight-ahead position, whereby the shift input member (96) is returned to the neutral position by the kneading spring (98). It automatically returns to the running speed. Further, by changing the connecting bolt (97) to each screw hole (150), the rotation angle of the steering input member (95) until the connecting bolt (97) contacts the edge of the phase adjusting hole (149) changes. When the steering handle (19) is operated, the deceleration start timing of the traveling speed can be adjusted, and when the steering handle (19) is supported linearly, the speed change input member (96) is shifted by the kneading spring (98). It is fixed to the input shaft (91) and prevents the shift input member (96) from floating due to mechanical vibration or the like, and prevents the running speed from decelerating due to the wobbling of the shift input member (96).
[0026]
Further, as shown in FIG. 16 to FIG. 20, the gear (88) forms a plurality of teeth (151) in an outer peripheral range of 270 degrees, and forms an outer peripheral range of 90 degrees in an arc (152). The total rotation angle of the handle (19) is set to 270 degrees, the angle of left steering rotation or right steering rotation is set to 135 degrees, and the steering handle (19) can be rotated easily with one hand. Form. Further, the sector gear (89) forms a plurality of teeth (153) in an outer peripheral range of 130 degrees, forms an outer peripheral range of 230 degrees in an arc cam (154), and teeth (151) of the gear (88) Are engaged with the teeth (153) of the sector gear (89), and when the maximum forward / reverse rotation of each gear (88) (89), the stoppers (155) on both ends of the arc (152) and the stoppers on both ends of the arc cam (154) ( 156) and restricting the rotation of the steering handle (19), and the steering input member (95) and the transmission input member (96) are set in a range of 65 degrees around the steering input shaft (87) core. A space for arranging the speed change input shaft (91) and the upper end of the main speed change member (110) on the plane on which each input member (95) rotates is secured by rotating forward or reverse, and on the speed change input shaft (91) core line Is provided with a steering input connecting portion (116) And a structure in which the input connecting portions (116) and (122) are separated by 90 degrees on the same circumference can be easily obtained, and the structure can be made compact and the design and assembly can be simplified. .
[0027]
A straight notch (157) is formed at the center of the circular arc cam (154) of the sector gear (89), and a detent shaft (158) is rotatably supported on the upper surface wall of the steering column (71). 158) The detent arm (159) is fixed to the lower end, the detent arm (159) is rotatably supported by the detent arm (159) via the roller shaft (160), and the arc cam (154) is detent-rolled. (161) is brought into contact, and the detent roller (161) is detachably engaged with the rectilinear notch (157) to support the steering handle (19) in the rectilinear position. The detent lever (162) is fixed to the upper end side of the detent shaft (158), and one end of a neutral spring (163) wound around the detent shaft (158) is locked to the detent lever (162) to 71) is brought into contact with the receiving plate (164) of the neutral spring (163), and the detent roller (161) is brought into elastic contact with the arc cam (154) and the straight notch (157) by the neutral spring (163). ing. Further, a microswitch type rectilinear sensor (165) that electrically detects the rectilinear position of the steering handle (19) by switching on and off is attached to the detent lever (162).
[0028]
Thus, when the main speed change lever (73) is neutral, the input members (95) (96) around the steering input shaft (87) core line by the forward (reverse) operation of the steering handle (19). ) And the coupling members (115) and (121) move on a conical locus, and the output members (114) and (120) and the output shafts (113) and (119) are stopped.
[0029]
Further, by the forward (reverse) operation of tilting the main transmission lever (73) forward (rearward), the input members (95) (96) are tilted forward (rearward) around the core line of the speed change input shaft (91) and operated. While maintaining the state where the direction input connecting portion (116) is stopped at a certain position, the shift input connecting portion (122) is moved upward (downward), and the shift output member (120) is swung upward (downward). The transmission output shaft (119) is rotated forward (reverse), and the first hydraulic motor (24) is rotated forward (reverse) by switching the swash plate angle of the first hydraulic pump (23) of the transmission member (23). The left and right traveling crawler (2) is driven forward (reverse) by forward rotation (reverse rotation) of the output shaft (31) of the hydraulic motor (24). Further, the rotation speed of the output shaft (31) changes in proportion to the tilt angle of the main transmission lever (73), and the forward (reverse) speed of the traveling crawler (2) is steplessly changed.
[0030]
Further, under the condition that the main shift lever (73) is moved forward (rearward) and the forward (reverse) operation is performed, the steering handle (19) is rotated leftward (rightward) to thereby input the shift. The steering input member (95) rotates forward (reversely) about the steering input shaft (87) around the core line in a posture in which the steering input member (95) is tilted forward (rearward) around the axis (91), and the steering input connecting portion (116) is The steering output shaft (113) is normally rotated (reversed) by the downward (upward) swing of the steering output member (114), and the second hydraulic pump ( 26) forward rotation (reverse rotation) of the second hydraulic motor (27) by switching the swash plate angle, and left rotation crawler (2) by forward rotation (reverse rotation) of the output shaft (68) of the second hydraulic motor (27). Is decelerated (accelerated) and the right traveling crawler (2) is accelerated (decelerated) to the left (right To thereby pivot the body to correct the path to the left (right). Simultaneously with the course correcting operation, the shift input member (96) is tilted forward (rear) around the core line of the shift input shaft (91) by the leftward (rightward) rotation of the steering handle (19). The steering input shaft (87) rotates forward (reversely) around the core wire, the shift input connecting portion (122) moves downward (upward), and the shift output (120) swings downward (upward) to produce shift output. The shaft (119) is reversely rotated (normally rotated), and the speed change member (25) is controlled to return to the neutral direction to reduce the rotational speed of the output shaft (31), thereby reducing the traveling speed (vehicle speed). As described above, by the left / right steering operation of the steering handle (19) during traveling, the turning radius (angle) for correcting the course is proportional to the rotation angle of the steering handle (19), and the traveling speed is reduced. By changing the amount and rotating the steering handle (19) largely, the speed difference between the left and right traveling crawlers (2) is increased to reduce the turning radius, and at the same time, the amount of deceleration of the traveling speed increases and the vehicle speed decreases. At the time of forward movement and backward movement, the movement of the turning input connecting portion (116) is reversed with respect to the rotation of the steering handle (19), and the steering handle (19) is rotated in both forward and backward movements. By adjusting the operation direction and the turning direction of the aircraft and rotating the round steering handle (19) to rotate, for example, a course correction and a direction change with a driving feeling similar to that of a four-wheeled vehicle such as a tractor or a rice transplanter. Cormorant.
[0031]
19 and 20 show the relationship between the turning angle of the steering handle (19) and the speed of the left and right traveling crawler (2) when the aircraft is turning left and right. The turning angle of the handle (19) is large. As the speed difference between the left and right traveling crawlers (2) increases, the body center speed, which is the average speed of the left and right traveling crawlers (2), is also reduced according to the traveling speed (high speed, standard, low speed) state. When the steering handle (19) in the straight traveling position is rotated about 15 degrees leftward (rightward), the linkage bolt (97) moves in the phase adjusting hole (149), and the speed is changed by the kneading spring (98). The input member (96) is maintained at the same position as the straight travel, and left by the steering output that causes the second hydraulic motor (27) to rotate forward (reverse) by the second hydraulic pump (26) of the steering member (28). Turn in the direction (right direction) and correct the course to match the curve of the uncut grain row. At this time, the deceleration amount of the traveling crawler (2) inside the turning and the acceleration amount of the traveling crawler (2) outside the turning become substantially equal, and the body center speed is kept at substantially the same speed as the straight traveling. Further, when the steering handle (19) is rotated by 15 degrees or more from the straight traveling position, the speed change input member (96) decelerates in both the left turn and the right turn against the kneading spring (98). 1 The traveling shift output of the hydraulic pump (23) and the motor (24) is decelerated, the left and right traveling crawlers (2) and (2) are rotated in the same direction to move forward (or reverse), and the left and right traveling crawlers (2) ( 2) The course is corrected so that the brake turn operation that turns to the left (right direction) is performed due to the difference in the traveling speed, and when it is removed from the uncut grain row, it is returned to the original row or moved to the next row. I do. Further, when the steering handle (19) is rotated about 135 degrees, the center speed of the aircraft is reduced to about one fourth of the straight traveling speed, the traveling crawler (2) inside the turning is driven in reverse, and the traveling crawler inside the turning is driven. A spin turn operation is performed in which the aircraft turns around (2), and the aircraft is turned 180 degrees by shifting the lateral width of the left and right traveling crawler (2) in the turning direction. Rotate the steering handle (19) in the range of degrees to turn left or right, and turn to the uncut grain culm (crop) row in the rotation range of the handle (19) left and right of 15 degrees around the straight position In addition to maintaining the traveling speed while moving straight, the alignment course that moves along the road is changed and the body is turned on the field headland by turning the handle (19) left and right from the straight position to the next work. The spin turn operation to move and automatically decelerated to about a quarter of the speed of straight running performed.
[0032]
Further, when the sub-shift is maintained at a standard speed (1.5 meters per second) and the steering handle (19) is rotated by 90 degrees, the main shift output is set to a high speed and two thirds by operating the main shift lever (68). Even if it is changed to 1/3, only the turning speed (aircraft center speed) is changed in a state where the turning radius of the airframe is kept substantially constant. Further, the first hydraulic pump (23) and the first hydraulic motor (24) are maintained in a straight traveling state within a set range of the linkage bolt (97) and the phase adjusting hole (149) with reference to the straight traveling position, and the crop row or Even if a steering operation is carried out along the dredger, etc., the running speed is prevented from changing unevenly, and the course can be corrected during farm work while maintaining the same running speed. It is possible to perform an appropriate steering operation by substantially matching the traveling operation of the vehicle. Further, the sub-shift lever (74) for switching the shift reference value of the main shift lever (73) changes the turning radius from a small diameter to a large diameter in proportion to the low speed, standard and high speed switching of the sub-shift operation, and the first hydraulic pump ( 23) and the reduction ratio between the motor (24) and the traveling crawler (2) and the reduction ratio between the second hydraulic pump (26) and the motor (27) and the traveling crawler (2), or necessary for the spin turn operation. While ensuring the driving force required for small radius turning, and operating the main speed change lever (73) at the same sub-shift operation position, the running speed during turning is changed with the turning radius kept substantially constant. Thus, the driving operation can be performed according to the skill level of the worker, and the mobility and the driving operability are improved.
[0033]
By the way, as shown in FIGS. 21 to 26, the speed change member (25) that requires a large driving force with respect to the turning operation force output from the steering member (28) is large in shape (large capacity). Further, the steering member (28) is formed in a small size (small capacity), and the steering member (28) is integrally formed on the front side of the transmission case (22), and the transmission member (25) is integrally formed on the rear side. The shift member (25) and (28) are compactly arranged on the upper part of the transmission case (22) by suppressing the protrusion of the steering member (28) in front of the transmission case (22) to a minimum. It is configured as follows.
[0034]
Then, the vehicle speed and steering control arms (136) and (141) for controlling the output of the speed change and steering members (25) and (28) are replaced with the bosses (136a) and (141a) at the base end of the members (25) and (28). The hydraulic pumps (23) and (26) of the hydraulic pumps are fixed to the upper control shafts (135) and (136) via bolts (136b) and (141b) so as to be easily connected to the rods (138) and (143). In addition to improving the maintainability, the input shafts (29a) and (29b) of the first and second hydraulic pumps (23) and (26) constituting the speed change member (25) and the steering member (28) (25) Projected to the left outer side of (28) and disposed on the rear side of the transmission case (22), the engine (21) on the left side engine output shaft (21a), the pulleys (166) (167) and the belt (30a) ) And Ten The input shaft (29a) of the first hydraulic pump (23) is interlocked and connected to the input shaft (29b) of the second hydraulic pump (26) via the pulley (168), and the pulleys (167) (169) and the belt ( 30b) and an input shaft (29a) of the first hydraulic pump (23) are interlocked and connected via a tension pulley (170), and driving is performed with priority on traveling over turning.
[0035]
Further, the traveling belt (30a) connecting the engine (21) and the first hydraulic pump (23) to the pump belt (30b) for connecting the first and second hydraulic pumps (23) (26) to the pump ( 23) An empty space (171) is formed on the left side of the turning belt (30b) in front of the traveling belt (30a), close to the side of the traveling belt (30a), and a trimming portion (8) for the empty space (171). ) Are made close to the speed change and steering members (25) and (28) without interfering with each other, so that the entire body is made compact.
[0036]
Further, the vehicle speed control arm (136) and the rod (138) are connected to each other through the shaft (172) and the long hole (173) with some flexibility in the neutral region, and the steering control arm (141) and the rod are connected. (143) is connected via a shaft (174), and the neutral holding detent plate (175) is integrally connected to each control arm (136) (141), and the hydraulic pump (23) (26) is connected to the outer wall. A detent arm (177) is pivotally supported on a detent shaft (176) to be fixed, and a detent roller (178) bearing on the detent arm (177) is moved by a spring (179) force of the detent plate (175). The structure is configured to hold the neutral position of each control arm (136) (141) when being brought into elastic contact with the concave neutral notch (175a).
[0037]
Reference numeral (180) denotes a cutting input for driving the cutting part (8) by interlockingly connecting to the PTO shaft (58) via pulleys (181) (182), a belt (183) and a tension pulley type cutting clutch (184). A shaft (185) is connected to the engine output shaft (21a) via a pulley (166) (186) and a belt (187) and a tension pulley type threshing clutch (188) to drive the threshing portion (4). It is an input shaft.
[0038]
As shown in FIGS. 22, 27, and 28, the operator sitting on the driver's seat (20) is behind the line of sight (M) for viewing the front end of the weed plate (189) at the foremost cutting portion (8). The raising case (190) and the handle shaft (84) (86) are arranged, and the fulcrum bolt (79) is arranged above and behind the raising case (190), so that the handle shaft (84) ( 86) is tilted backward from the fulcrum bolt (79), and the driver's seat (20) and the cutting part (8) are relatively close to each other in the position of the driver's seat (20) of the combine machine body having a small and compact structure. While the operator is driving, the operator's line of sight (M) confirming the tip side of the cutting part (8) is raised, and the shafts (84) and (86) of the case (190) and the steering handle (19). The driver's seat (20) It is configured to permit proper cutting work while confirming more always reaper (8) well.
[0039]
In addition, the tip of the weed plate (189) is provided to be visually observed from the position of the operator's line of sight of the driver's seat (20) through the circle of the round handle operating portion (19a) of the steering handle (19). Is provided so that the tip of the weed plate (189) faces the circular space of the round handle operating portion (19a) from the position of the person's line of sight, and the upper end of the case (190) is raised in side view. Even in a combine structure in which the front portion of the round handle operating portion (19a) is positioned directly above and the weed board (189) is close to the driver seat (20), the steering handle ( 19) It is configured to allow good work while easily confirming the work situation at the tip of the weed board (189) without obstructing the line of sight (M).
[0040]
Further, as shown in FIG. 28, when the main transmission lever (73) is tilted to the most position (the highest speed position), the lever operating portion (73a) is brought close to the shaft center of the handle shaft (84), The main transmission lever (73) is provided so as to swing in the front-rear direction behind the handle shaft (84), and the steering handle (19) and the main transmission lever (73) are arranged relatively close to each other. In the combine, the inconvenience of interference between the right hand and the left hand during the operation of holding the main transmission lever (73) with the left hand and the steering handle (19) with the right hand is maximally avoided. The speed change lever (73) is configured to be easily and accurately operated.
[0041]
【The invention's effect】
In the present invention, in the combine in which the cutting unit (8) is arranged in front of the driving operation unit, the driver seat (20) and the cutting unit (8) are brought close to each other, and the weeding plate at the foremost end of the cutting unit (8) (189) The pulling case (190) of the mowing part (8) is arranged behind the line of sight (M) where the operator of the driver's seat (20) visually observes the tip, and the pulling case (190) A tilt fulcrum (79) of the steering handle (19) is provided further upward and rearward, and the steering handle shaft (84) is tilted rearward from the tilt fulcrum (79), and the driver seat (20) And a weed board (189) are arranged close to each other , and a cutting part (19a) is placed in the circle of the round handle operating part (19a) of the steering handle (19) from the line of sight of the operator of the driver seat (20). 8) Weeding board (189) is provided to face the tip, At face view Marugata handle operation portion immediately above the upper end of the Pick-case (190) is the front of the (19a) is to be positioned.
[0042]
Accordingly, while the operator is driving at the driver's seat (20) position, the operator's line of sight (M) confirming the front end side of the cutting part (8) is raised and blocked by the case (190) or the steering handle (19). Therefore, it is possible to perform an appropriate cutting operation while confirming the cutting unit (8) well from the position of the driver seat (20).
Moreover, even in a small and compact structure combine where the driver's seat (20) position and the cutting part (8) are relatively close to each other, the round handle operating portion (19a) of the steering handle (19) from the driver seat (20) position. through space area within the circle, the working conditions of the operating frequency grass plate placed close to the seat (20) (189) tip can be performed satisfactorily work readily ascertained.
[Brief description of the drawings]
FIG. 1 is an overall side view of a combine.
FIG. 2 is an overall plan view of the combine.
FIG. 3 is an explanatory diagram of a mission drive system.
FIG. 4 is an explanatory perspective view of a traveling speed change and steering operation unit.
FIG. 5 is an operation explanatory view of the same part.
FIG. 6 is a side view of a steering column.
FIG. 7 is an enlarged side view of the upper part.
FIG. 8 is an enlarged side view of the lower part.
FIG. 9 is a front view of a steering column.
FIG. 10 is an enlarged front view of the upper part.
FIG. 11 is an enlarged front view of the lower part.
FIG. 12 is an explanatory plan view of FIG. 4;
FIG. 13 is an enlarged view of the same.
FIG. 14 is a cross-sectional view of a steering column.
FIG. 15 is an exploded explanatory view of FIG. 14;
FIG. 16 is a partial plan view of the upper part of the steering column.
FIG. 17 is a partial view thereof.
18 is an operation explanatory view of FIG. 17;
FIG. 19 is a diagram showing main shift and steering handle operation.
FIG. 20 is a diagram showing sub-shifting and steering handle operation.
FIG. 21 is an explanatory front view of a driving operation unit.
FIG. 22 is an explanatory plan view of a driving operation unit.
FIG. 23 is an explanatory side view of a mission case part.
FIG. 24 is an explanatory plan view of a mission case portion.
FIG. 25 is an explanatory side view of the speed change and swivel member.
FIG. 26 is an explanatory plan view of the speed change and turning member portion;
FIG. 27 is an explanatory side view of a driving unit.
FIG. 28 is an explanatory side view of a driving operation unit.
[Explanation of symbols]
(8) Cutting part (19) Steering handle (19a) Handle operating part (20) Driver's seat (73) Main speed change lever (speed change operation member)
(79) Support bolt (tilt support)
(84) Handle shaft (189) Weeding board (190) Lifting case

Claims (1)

運転操作部前方に刈取部（８）を配備させたコンバインにおいて、
運転席（２０）と刈取部（８）とを近接させると共に、同刈取部（８）最前端の分草板（１８９）先端部を上記運転席（２０）の作業者が目視する目線（Ｍ）より後方に、上記刈取部（８）の引起しケース（１９０）を配置し、同引起しケース（１９０）より上方で且つ後方に操向ハンドル（１９）のチルト支点（７９）を設けて、操向ハンドル軸（８４）をチルト支点（７９）より後方に傾動させるように構成し、
運転席（２０）と分草板（１８９）とを近接配置すると共に、同運転席（２０）の作業者の視線位置から操向ハンドル（１９）の丸形ハンドル操作部（１９ａ）の円内に、刈取部（８）の分草板（１８９）先端部を臨ませるように設けると共に、側面視にて、引起しケース（１９０）の上端部の直上方位置に丸形ハンドル操作部（１９ａ）の前部が位置するようにしたことを特徴とするコンバイン。In a combine in which a cutting part (8) is arranged in front of the driving operation part,
The driver's seat (20) and the cutting part (8) are brought close to each other, and the operator's eye of the driver's seat (20) visually observes the front end of the weeding board (189) of the cutting part (8) (M ), The raising case (190) of the cutting part (8) is arranged behind, and the tilt fulcrum (79) of the steering handle (19 ) is provided above and behind the raising case (190). The steering handle shaft (84) is configured to tilt backward from the tilt fulcrum (79) ,
The driver's seat (20) and the weed board (189) are arranged close to each other, and within the circle of the round handle operating portion (19a) of the steering handle (19) from the line of sight of the operator of the driver's seat (20) . Are provided so that the tip of the weed plate (189) of the cutting part (8) faces the round handle operating part (19a ) at a position directly above the upper end part of the raising case (190) in side view. The combine is characterized in that the front part of ) is located.

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