JP3727761B2

JP3727761B2 - Mobile farm machine

Info

Publication number: JP3727761B2
Application number: JP26280697A
Authority: JP
Inventors: 高茂實日
Original assignee: Yanma Agricultural Equipment Co Ltd
Current assignee: Yanma Agricultural Equipment Co Ltd
Priority date: 1997-09-09
Filing date: 1997-09-09
Publication date: 2005-12-14
Anticipated expiration: 2016-09-20
Also published as: JPH1095362A

Description

【０００１】
【発明の属する技術分野】
本発明は例えば圃場の穀稈を連続的に刈取って脱穀するコンバインなどの移動農機に関する。
【０００２】
【発明が解決しようとする課題】
従来、左右走行クローラを装設したコンバインを圃場の未刈り穀稈列に沿わせて走行移動させ乍ら収穫作業を行うと共に、圃場枕地で前記コンバインを方向転換させて次工程の未刈り穀稈列に移動させていたが、エンジン出力を変速伝達するミッションケースの左右走行出力を左右サイドクラッチを介して左右走行クローラに伝達させ、左右サイドクラッチの継断操作により左右走行クローラの一方を一時的に停止させて旋回させることにより、左右サイドクラッチ操作と走行変速操作の両方を作業者が略同時期に行う必要があり、また圃場枕地で方向転換するときの旋回半径が大きくなる不具合がある。
【０００３】
そこで、エンジンの動力を各別に伝える左右油圧無段変速機を設けて左右走行クローラを駆動することにより、旋回時の減速並びに旋回半径の縮少などを容易に行えるが、直進性能が低下し易く、未刈り穀稈列に沿わせて走行移動させる操向操作が面倒になる不具合がある。
【０００４】
また、左右走行クローラにエンジン動力を変速伝達する単一の油圧無段変速機構と、旋回内側の走行クローラを減速しかつ旋回外側の走行クローラを増速させる油圧無段操向機構を設けることにより、直進性能を良好に維持して操向操作性を向上させ、かつ旋回半径も容易に縮少できるが、直進時と旋回時とで走行速度が略一定に保たれ、旋回半径が小さいスピンターン動作などを行うときに走行変速により減速操作を行う必要があり、圃場枕地で方向転換するときに旋回操作と走行変速操作の両方を行う必要がある。
【０００５】
さらに、前記操向機構を伝動させる旋回操作と連動させて走行速度を自動的に減速させ、かつ直進走行に戻す操作と連動させて元の走行速度に自動的に増速させることにより、旋回操作だけでスピンターン動作などを適正走行速度に減速させて行え、面倒な走行変速操作を省けるが、収穫作業中に未刈り穀稈列に沿わせる条合せ（進路修正）のための操向操作を行っても、走行速度が減速されたり増速されて収穫作業途中に走行速度が不均一に変化し、作業者の運転感覚とコンバインの走行動作との間にずれが生じて適正な操向操作を容易に行い得ない等の問題がある。
【０００６】
【課題を解決するための手段】
そこで、本発明は、変速操作部材の走行変速操作によりエンジンの駆動力を左右走行部に変速伝達する走行変速部材と、操向ハンドルの操向操作により左右走行部の駆動速度に差を生じさせる操向部材を設ける移動農機において、操向ハンドルの直進位置を基準とした略一定範囲内の操向操作で旋回方向側の走行部の減速量と旋回方向と反対側の走行部の増速量を略同等に変化させて走行速度を略一定に保つ動作と、前記の操向操作の範囲外で走行速度を操向ハンドルの操作と連動して自動的に増減速変化させる動作を行わせるように構成し、操向ハンドルの操作により減速リンク機構を介して走行速度を減速させて圃場枕地で方向転換させ、次作業工程に移動して直進走行に戻す操向ハンドルの操作によって減速リンク機構の復動により前工程作業の走行速度まで増速させて作業を再開させることができるようにしたことを特徴とする移動農機を提供するものである。
【０００９】
【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は主変速レバー及び操向ハンドルの操作系の斜視説明図、図２はコンバインの全体側面図、図３は同平面図であり、図中（１）は走行クローラ（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機である脱穀部、（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）は丸形操向ハンドル（１９）及び運転席（２０）など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。
【００１０】
図４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）からなる主変速機構である走行用の油圧式無段変速機構（２５）と、１対の第２油圧ポンプ（２６）及び第２油圧モータ（２７）からなる操向機構である旋回用の油圧式無段変速機構（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（２９）を伝達ベルト（３０）を介し連動連結させて、これら油圧ポンプ（２３）（２６）の駆動を行うように構成している。
【００１１】
そして前記第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）を介し走行クローラ（２）の駆動輪（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。
【００１２】
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ている。
【００１３】
また、走行用の油圧式無段変速機構（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（４５）を有する副変速軸（４７）と、前記センタギヤ（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）（４８）・中速用ギヤ（５１）（５２）・高速用ギヤ（５３）（５４）を設けて、中央位置のギヤ（５１）のスライド操作によってこれら低速・中速・高速の切換えを可能とさせる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ものである）。また前記ブレーキ軸（４９）には車速検出ギヤ（５５）を設けると共に、該ギヤ（５５）の回転数より車速を検出する車速センサ（５６）を設けている。なお、刈取部（８）に回転力を伝達する刈取ＰＴＯ軸（５７）のＰＴＯ入力ギヤ（５８）に、前記出力軸（３１）の伝達ギヤ（４２）を噛合連結させている。
【００１４】
そして、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）を介しキャリヤ軸（４０）に伝達させると共に、該キャリヤ軸（４０）に伝達された回転を左右各一対の減速ギヤ（６０）（６１）を介し左右の駆動輪（３４）の左右輪軸（３４ａ）にそれぞれ伝えるように構成している。
【００１５】
さらに、旋回用の油圧式無段変速機構（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、第２油圧モータ（２７）の出力軸（６２）の出力ギヤからギヤ伝達機構（６３）を介し旋回入力軸（６４）の入力ギヤ（６５ａ）（６５ｂ）に回転出力を伝達し、右側のリングギヤ（３８）の外歯（３８ｂ）を対しては直接的に、また左側のリングギヤ（３８）の外歯（３８ｂ）に対しては逆転軸（６６）の逆転ギヤ（６７）を介し伝えて、第２油圧モータ（２７）の正転時に左右のリングギヤ（３８）を左右同一回転数で左ギヤ（３８）を正転、右ギヤ（３８）を逆転とさせるように構成している。
【００１６】
而して旋回用の第２油圧モータ（２７）の駆動を停止させ左右リングギヤ（３８）を静止固定させた状態で、走行用の第１油圧モータ（２４）の駆動を行うと、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）及び減速ギヤ（６０）（６１）を介し左右の輪軸（３４ａ）に左右同回転方向の同一回転数で伝達されて、機体の前後直進走行が行われる。一方、走行用の第１油圧モータ（２４）の駆動を停止させ左右のサンギヤ（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て、左右走行クローラ（２）の駆動方向を前後逆方向とさせて機体を左或いは右にその場でスピンターンさせるものである。
【００１７】
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）を駆動して機体を左右に旋回させる場合には旋回半径の大きい旋回を可能にできるもので、その旋回半径は左右走行クローラ（２）の速度に応じ決定される。
【００１８】
図５乃至図１３に示す如く、前記走行用の油圧式無段変速機構（２５）に連結する主変速レバー（６８）と、旋回用の油圧式無段変速機構（２８）に連結する操向ハンドル（１９）とを、変速及び旋回連動機構（６９）に連動連結させると共に、該連動機構（６９）を走行変速及び操向リンク系であるリンク機構（７０）（７１）介し走行及び操向用の無段変速機構（２５）（２８）のコントロールレバー（７２）（７３）に連動連結させている。
【００１９】
前記連動機構（６９）は、主変速レバー（６８）の基端折曲部（６８ａ）を筒軸（７４）に左右揺動自在に支持する回動板（７５）と、機体側の本機フレーム（７６）に固設して前記回動板（７５）を左右方向の第１枢軸（７７）を介し前後回動自在に支持する固定取付板（７８）と、前記枢軸（７７）とは直交する前後方向の第２枢軸（７９）を介して回動板（７５）に連結させて該軸（７９）回りに回動自在に設ける変速操作部材（８０）と、前記第２枢軸（７９）の軸回りに回動自在に連結させる操向操作部材（８１）とを備え、変速及び操向操作部材（８０）（８１）の第２枢軸（７９）とは偏心位置の各操作出力部（８０ａ）（８１ａ）を変速及び操向リンク機構（７０）（７１）に連動連結させている。
【００２０】
前記変速及び操向リンク機構（７０）（７１）は、連動機構（６９）後方位置で本機フレーム（７６）側に揺動軸（８２）外側の揺動筒軸（８３）を介し支持する変速アーム（８４）と、前記揺動軸（８２）に基端を固設する旋回出力逆転手段である操向アーム（８５）と、前記出力部（８０ａ）（８１ａ）の各操作出力軸（８６）（８７）と各アーム（８４）（８５）間を連結する自在継手軸（８８）（８９）と、前記揺動軸（８２）の右端に固設する操向出力アーム（９１）と、前記運転キャビン（１８）の回動支点軸（９２）の支点軸受（９３）に取付ける中間軸（９４）に回転自在に設ける変速及び操向用第１揺動アーム（９５）（９６）と、前記アーム（８４）（９１）と第１揺動アーム（９５）（９６）の各先端間をそれぞれ連結する変速及び操向用自在継手形第１ロッド（９７）（９８）と、前記中間軸（９４）に設けて第１揺動アーム（９５）（９６）に一体連結する変速及び操向用第２揺動アーム（９９）（１００）と、前記ミッションケース（２２）上部の軸受板（１０１）に取付ける支軸（１０２）に回動自在に支持させる変速及び操向用筒軸（１０３）（１０４）と、該筒軸（１０３）（１０４）に基端を固設する第１揺動アーム（１０５）（１０６）と前記第２揺動アーム（９９）（１００）の各先端間を連結する変速及び操向用自在継手形第２ロッド（１０７）（１０８）と、前記筒軸（１０３）（１０４）に基端を固設する第２揺動アーム（１０９）（１１０）と前記コントロールレバー（７２）（７３）の各先端間を連結させる変速及び操向用自在継手形第３ロッド（１１１）（１１２）とを備え、前記第１枢軸（７７）を中心とした変速操作部材（８０）の回動によって走行用のコントロールレバー（７２）を、また走行中の第２枢軸（７９）を中心とした操向操作部材（８１）の回動によって操向用のコントロールレバー（７３）を操作して変速及び操向制御を行うように構成している。
【００２１】
一方前記操向ハンドル（１９）下端のハンドル操作軸（１１３）にギヤ（１１４）を設けて、この後方の回転軸（１１５）に取付けるセクタギヤ（１１６）に前記ギヤ（１１４）を噛合せると共に、前記主変速レバー（６８）位置下方に配設する操向軸（１１７）の第１揺動アーム（１１８）と、前記回転軸（１１５）に基端を固設する出力アーム（１１９）との各先端間を操向リンク機構である自在継手形操向第１ロッド（１２０）を介して連結させ、操向軸（１１７）の第１揺動アーム（１１８）と一体の第２揺動アーム（１２１）を、前記自在継手軸（８９）の前端に自在継手形操向第２ロッド（１２２）を介して連結させ、前記ハンドル（１９）の回動操作によって前記第２枢軸（７９）を中心として操向操作部材（８１）を回動するように構成している。
【００２２】
また、前記ハンドル操作軸（１１３）のギヤ（１１４）下方に中立位置決め板（１２３）を設けていて、該位置決め板（１２３）下面の突出軸（１２４）に操向検出リンク（１２５）の一端を連結させ、前記回転軸（１１５）の右側に配設する減速アーム軸（１２６）の第１揺動アーム（１２７）と前記検出リンク（１２５）の他端長孔（１２５ａ）とを軸（１２８）を介し連結させると共に、前記操向軸（１１７）の減速アーム（１２９）と減速アーム軸（１２６）の第２揺動アーム（１３０）との各先端間を減速リンク機構である自在継手形第１減速ロッド（１３１）で連結させ、前記変速操作部材（８０）の最右端の減速伝達軸（１３２）と第２揺動アーム（１３０）の他端間を自在継手形第２減速ロッド（１３３）で連結させて、走行状態で前記ハンドル（１９）の操向量を大とする程第２減速ロッド（１３３）を下方に引張って走行速度を減速させるように構成している。
【００２３】
而して、前記変速及び操向操作部材（８０）（８１）を軸回りに回動可能とさせる第２枢軸（７９）と、操向アーム（８５）と継手軸（８９）との自在継手部（８９ａ）とを前後方向の水平ライン（Ｌ１）上に位置させ、また前記操作出力軸（８６）（８７）と自在継手軸（８８）（８９）との自在継手部（８８ｂ）（８９ｂ）と、第１枢軸（７７）とを前記ライン（Ｌ１）に直交させる左右水平ライン（Ｌ２）上に位置させ、さらに前記変速アーム（８４）と継手軸（８８）との自在継手部（８８ａ）と前記継手部（８９ａ）とを前記ライン（Ｌ２）と平行な左右水平ライン（Ｌ３）上に位置させ、且つ継手部（８９ａ）に継手部（８８ａ）を可及的に接近（最大限近い位置）させて、主変速レバー（６８）及び操向ハンドル（１９）の中立保持時に、これら何れか一方が操作されても、各操作部材（８０）（８１）を第１及び第２枢軸（７７）（７９）の軸回りに回動させるのみとさせて、継手軸（８８）（８９）には操作力を作用させないものである。
【００２４】
そして図９にも示す如く、主変速レバー（６８）の前後進操作で、第１枢軸（７７）を中心として操作部材（８０）を前後に角度（α１）（α２）傾けるとき前記継手軸（８８）を引張って或いは押して変速アーム（８４）を動作させて走行速度の前後進の切換えを行うと共に、図１１に示す如くこの状態中（主変速レバー（６８）が中立以外のとき）に操向ハンドル（１９）の回動操作で第２枢軸（７９）を中心として操作部材（８１）を上下に角度（β１）（β２）傾けるとき継手軸（８９）を引張って或いは押して操向アーム（８５）を動作させて機体の左及び右旋回を行うものである。即ち主変速の中立時に旋回操作を行っても継手軸（８９）はライン（Ｌ１）を中心とした円錐面上で移動する状態となって継手部（８９ａ）（８９ｂ）間の距離は変化せず、したがって操向アーム（８５）は動作しない。そして主変速の中立以外で旋回操作が行われるとき操向アーム（８５）は動作するもので、前後進に切換わるとき操向アーム（８５）は前後逆方向に動作して、第２油圧モータ（２７）の回転を前進時と後進時では逆方向とさせるように構成したものである。
【００２５】
つまり、走行用の第１油圧モータ（２４）の正回転時を前進時とすると、逆回転時の後進時には旋回用の第２油圧モータ（２７）による遊星ギヤ機構（３５）の作用は前進時と後進時では逆となるもので、前進時と後進時のハンドル（１９）操作による機体の旋回方向を一致させるため、第１油圧モータ（２４）の逆回転（後進）時には第２油圧ポンプ（２６）の斜板角度を逆方向に切換えて（第１及び第２油圧ポンプ（２３）（２６）の入力軸の回転方向は一定）、第２油圧モータ（２７）の回転を前進時と後進時では逆方向とさせるものである。
【００２６】
つまりこの場合、前進操作時の操作部材（８０）が中立より前方の角度（α１）側に傾いて、ハンドル（１９）の右回動操作によって第２ロッド（１２２）を引張り操作部材（８１）を下方向の角度（β２）側に傾けるとき、操作部材（８１）の出力部（８１ａ）を操向アーム（８５）側に近づけて、揺動軸（８２）を中心として操向アーム（８５）を操作部材（８１）より遠ざける方向（図５中反時計方向）に回転させ、前記第１及び第２ロッド（９８）（１０８）などを介しコントロールレバー（７３）を下方向に回転させて、旋回用の第２油圧モータ（２７）を正回転させる。即ち、機体を前進で右旋回（走行クローラ（２）の速度を左側が大、右側が小）させる。
【００２７】
また、上述の前進操作時で、ハンドル（１９）の左回動操作によって第２ロッド（１２２）を押し上げ、操作部材（８１）を上方向の角度（β１）側に傾けるとき、操作部材（８１）の出力部（８１ａ）を操作アーム（８５）側より遠ざけて、揺動軸（８２）を中心として操向アーム（８５）を操作部材（８１）側に近づける方向（図５中時計方向）に回転させ、前記コントロールレバー（７３）を上方向に回転させて、前記第２油圧モータ（２７）を逆回転させる。即ち、機体を前進で左旋回（走行クローラ（２）の速度を右側が大、左側が小）させる。
【００２８】
さらに、後進操作時の操作部材（８０）が中立より後方の角度（α２）側に傾いて、ハンドル（１９）の右回動操作によって第２ロッド（１２２）を引張り操作部材（８１）を下方向の角度（β２）側に傾けるとき、操作部材（８１）の出力部（８１ａ）を操向アーム（８５）側より遠ざけて、揺動軸（８２）を中心として操向アーム（８５）を操作部材（８１）側に近づける方向（図５中時計方向）に回転させ、前記コントロールレバー（７３）を上方向に回転させて、前記第２油圧モータ（２７）を逆回転させる。即ち、機体を後進で右旋回（走行クローラ（２）の速度を左側が大、右側が小）させる。
【００２９】
またさらに、上述とは逆に後進操作時で、ハンドル（１９）の左回動操作によって、操作部材（８１）を上方向の角度（β１）側に傾けるとき、操作部材（８１）の出力部（８１ａ）を操作部材（８１）側に近づけて、揺動軸（８２）を中心として操向アーム（８５）を操作部材（８１）より遠ざける方向（図５中反時計方向）に回転させ、前記コントロールレバー（７３）を下方向に回転させて、前記第２油圧モータ（２７）を正回転させる。即ち、機体を後進で左旋回（走行クローラ（２）の速度を右側が大、左側が小）とさせる。
【００３０】
このように前進及び後進時における旋回操作にあっては、操向アーム（８５）の動きを逆方向とさせて、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るものである。
【００３１】
さらに、図１５は機体の左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、これら左右走行クローラ（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ものであって、機体の右旋回時においても左右クローラ（２）が逆の関係となるだけで同様のものであり、図１５から明らかなように、変速操作部材である主変速レバー（６８）の走行変速操作によりエンジン（２１）の駆動力を左右走行部である左右走行クローラ（２）（２）に変速伝達する走行変速部材である第１油圧ポンプ（２３）及び第１油圧モータ（２４）と、操向ハンドル（１９）の操向操作により左右走行クローラ（２）（２）の駆動速度に差を生じさせる操向部材である第２油圧ポンプ（２６）及び第２油圧モータ（２７）を設ける移動農機において、操向ハンドル（１９）の直進位置を基準とした略一定の操向操作の範囲内で走行速度を略一定に維持する動作と、前記の操向操作の範囲外で走行速度を操向ハンドル（１９）の操作と連動して自動的に増減速変化させる動作を行わせ、操向ハンドル（１９）操作だけで第１減速ロッド（１３１）を介して減速させて圃場枕地で方向転換させ、次作業工程に移動して直進走行に戻す操作によって第１減速ロッド（１３１）の復動により前工程の作業走行速度まで増速させて作業を再開させ、操向操作に伴う走行変速操作を省けると共に、収穫作業中に未刈り穀稈（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収穫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ように構成している。
【００３２】
また、操向ハンドル（１９）の操向操作量に応じて走行速度を減速し乍ら左右走行クローラ（２）（２）の駆動速度差を連続的に拡大してスピンターン動作に移行させ、収穫作業中の直進走行及び進路修正動作と、圃場枕地で次作業工程位置に向けて方向転換させるスピンターン動作とを、連続した一連の操向操作だけでスムーズに行わせると共に、操向ハンドル（１９）の直進位置を基準とした略一定範囲内の操向操作で旋回方向側の走行クローラ（２）の減速量と旋回方向と反対側の走行クローラ（２）の増速量を略同等に変化させて走行速度を略一定に保ち、第１油圧ポンプ（２３）及び第１油圧モータ（２４）並びに第２油圧ポンプ（２６）及び第２油圧モータ（２７）を略同一仕様の無段変速機構を用いて構成し、第１油圧ポンプ（２３）及び第１油圧モータ（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）及び第２油圧モータ（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れるように構成している。
【００３３】
また図１２にも示す如く、前記操向ハンドル（１９）に設ける検出リンク（１２５）は中立位置より右或いは左旋回操作の何れにおいても第１揺動アーム（１２７）を同一方向に角度（θ）の範囲で回動させて第２減速ロッド（１３３）を常に引張る状態とさせて、前進操作時の操作部材（８０）が角度（α１）側に傾いてるときには、継手部（８８ａ）（８８ｂ）間の距離を縮め、また後進操作時の操作部材（８０）が角度（α２）側に傾いているときには、継手部（８８ａ）（８８ｂ）間の距離を大きくして、変速アーム（８４）をそれぞれ中立方向の低速側に変位させて、その旋回量に応じた減速を行うものである。
【００３４】
さらに、変速及び操向の操作力を伝達する前記第１ロッド（９７）（９８）と揺動アーム（９５）（９６）の自在継手部（９７ａ）（９８ａ）の中心を、運転キャビン（１８）の回動支点軸（９２）位置に一致させて、変速及び操向の中立保持においてはこれらの操作系を取外すことなく運転キャビン（１８）の前方向への回動を可能とさせるように構成している。
【００３５】
ところで、図４及び図１４に示す如く、前記第１及び第２油圧ポンプ（２３）（２６）と第１及び第２油圧モータ（２４）（２７）とをそれぞれループ油圧回路（１３４）（１３５）を介し正逆自在に接続させ、前記第１及び第２油圧モータ（２４）（２７）の出力軸（３１）（６２）には、電磁弁（１３６）（１３７）の作動によって出力軸（３１）（６２）を静止保持する走行停止及び直進固定用の走行及び旋回用ブレーキ装置（１３８）（１３９）を設けると共に、前記駐車ブレーキ軸（４９）にはブレーキ軸（４９）を静止保持する駐車ブレーキ装置（１４０）を設けている。
【００３６】
【発明の効果】
本発明では、変速操作部材（６８）の走行変速操作によりエンジン（２１）の駆動力を左右走行部（２）（２）に変速伝達する走行変速部材（２３）（２４）と、操向ハンドル（１９）の操向操作により左右走行部（２）（２）の駆動速度に差を生じさせる操向部材（２６）（２７）を設ける移動農機において、操向ハンドル（１９）の直進位置を基準とした略一定範囲内の操向操作で旋回方向側の走行部（２）の減速量と旋回方向と反対側の走行部（２）の増速量を略同等に変化させて走行速度を略一定に保つ動作と、前記の操向操作の範囲外で走行速度を操向ハンドル（１９）の操作と連動して自動的に増減速変化させる動作を行わせるように構成し、操向ハンドル（１９）の操作により減速リンク機構（１３１）を介して走行速度を減速させて圃場枕地で方向転換させ、次作業工程に移動して直進走行に戻す操向ハンドル（１９）の操作によって減速リンク機構（１３１）の復動により前工程作業の走行速度まで増速させて作業を再開させることができるようにしている。
このようにして、操向ハンドル（１９）の直進位置を基準とした略一定範囲内の操向操作で旋回方向側の走行部の減速量と旋回方向と反対側の走行部の増速量を略同等に変化させて走行速度を略一定に保つ動作を行わせることができるため、操向ハンドル（１９）の操作により減速させて圃場枕地で方向転換させることができる。
そして、次作業工程に移動して直進走行に戻す操向ハンドル（１９）の操作によって前工程の作業走行速度まで増速させて作業を再開できるため、操向操作に伴う走行変速操作を省くことができると共に、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容易に防止でき、略同一走行速度を保ち乍ら農作業中の進路修正を行うことができて、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容易に行うことができる。
【図面の簡単な説明】
【図１】主変速レバー及び操向ハンドルの操作系の斜視説明図。
【図２】コンバインの全体側面図。
【図３】コンバインの全体平面図。
【図４】ミッション駆動系の説明図。
【図５】走行変速及び操向操作部の説明図。
【図６】操作部の正面説明図。
【図７】操作部の平面説明図。
【図８】操作部の側面説明図。
【図９】操作部材の側面説明図。
【図１０】操作部材の正面説明図。
【図１１】操作部材の平面説明図。
【図１２】操向ハンドル部の平面説明図。
【図１３】リンク機構部の平面説明図。
【図１４】油圧回路図。
【図１５】機体旋回時のハンドル切れ角とクローラ速度との関係を示す線図。
【符号の説明】
（２）走行クローラ（走行部）
（１９）操向ハンドル
（２１）エンジン
（２３）第１油圧ポンプ（走行変速部材）
（２４）第１油圧モータ（走行変速部材）
（２６）第２油圧ポンプ（操向部材）
（２７）第２油圧モータ（操向部材）
（６８）主変速レバー（変速操作部材）[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a mobile agricultural machine such as a combine harvester that continuously harvests and thresh grain cereals in a field.
[0002]
[Problems to be solved by the invention]
Conventionally, a combine equipped with a left and right traveling crawler is moved and moved along an uncut grain culm row in the field, and harvesting is performed while turning the combine at a field headland to change the combine in the next process. Although it was moved in a row, the left and right traveling output of the transmission case transmitting the engine output is transmitted to the left and right traveling crawlers via the left and right side clutches, and one of the left and right traveling crawlers is temporarily suspended by the intermittent operation of the left and right side clutches. When the vehicle is stopped and turned, it is necessary for the operator to perform both the left and right side clutch operations and the traveling speed change operation at substantially the same time, and the turning radius when turning in the field headland increases. is there.
[0003]
Therefore, by installing left and right hydraulic continuously variable transmissions that transmit the engine power separately and driving the left and right traveling crawlers, it is possible to easily reduce the turning radius and reduce the turning radius, but the straight running performance tends to deteriorate. There is a problem that the steering operation for traveling along the uncut grain row is troublesome.
[0004]
In addition, by providing a single hydraulic continuously variable transmission mechanism that shifts engine power to the left and right traveling crawlers, and a hydraulic continuously variable steering mechanism that decelerates the traveling crawler inside the turn and accelerates the traveling crawler outside the turn. While maintaining straight running performance and improving steering operability, the turning radius can be easily reduced, but the running speed is kept almost constant during straight running and turning, and the spin turn has a small turning radius. When performing an operation or the like, it is necessary to perform a decelerating operation by a traveling shift, and it is necessary to perform both a turning operation and a traveling shift operation when changing the direction at a field headland.
[0005]
Further, the turning operation is automatically reduced by interlocking with the turning operation for transmitting the steering mechanism and automatically increased to the original traveling speed in conjunction with the operation for returning to the straight traveling. It is possible to reduce the spin-turning operation to an appropriate traveling speed and to save troublesome traveling speed change operation, but to perform steering operation for the condition (course correction) along the uncut grain row during harvesting work. Even if it goes, the running speed is decelerated or increased, and the running speed changes unevenly during the harvesting work, and there is a difference between the operator's driving feeling and the combine's running action, and proper steering operation There is a problem that it cannot be easily performed.
[0006]
[Means for Solving the Problems]
Therefore, the present invention makes a difference in driving speed between the traveling speed change member that transmits the driving force of the engine to the left and right traveling parts by the traveling speed change operation of the speed change operation member and the left and right traveling parts by the steering operation of the steering handle. In a mobile agricultural machine with a steering member, the amount of deceleration of the traveling unit on the side of the turning direction and the amount of acceleration of the traveling unit on the opposite side of the turning direction by a steering operation within a substantially fixed range based on the straight position of the steering handle. To keep the running speed substantially constant by changing the speed substantially the same , and to automatically increase / decrease the running speed in conjunction with the steering handle operation outside the range of the steering operation. The speed reduction link mechanism is configured by operating the steering handle to reduce the traveling speed through the speed reduction link mechanism by operating the steering handle, change the direction at the field headland, and return to the next work process to return to the straight traveling. Before There is provided a mobile agricultural machine is characterized in that to be able to resume work by accelerated to the running speed of the degree work.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a perspective explanatory view of an operation system of a main transmission lever and a steering handle, FIG. 2 is an overall side view of the combine, FIG. 3 is a plan view thereof, and (1) is a traveling crawler (2). (3) is a machine base installed on the track frame (1), (4) is provided with a feed cylinder (5) stretched on the left side, and a handling cylinder (6) and a processing cylinder (7) are built in. The threshing unit, which is a threshing machine, (8) is a cutting part provided with a cutting blade (9) and a culm transport mechanism (10), and (11) is moved up and down the cutting part (8) via a cutting frame (12). (13) is a waste disposal section that faces the end of the waste chain (14), (15) is a grain tank that carries the grain from the threshing section (4) via the milling cylinder (16) , (17) is a discharge auger that transports the grain of the tank (15) out of the machine, and (18) is a round steering. Bundle (19) and the driver's seat (20) operating cabin comprising etc., constitute (21) as is an engine provided with the operating cabin (18) downward, threshing continuously harvests culms.
[0010]
As shown in FIG. 4, the transmission case (22) for driving the travel crawler (2) is a main transmission mechanism comprising a pair of first hydraulic pump (23) and first hydraulic motor (24). A hydraulic continuously variable transmission mechanism (25) and a turning hydraulic continuously variable transmission mechanism (28) which is a steering mechanism including a pair of second hydraulic pump (26) and a second hydraulic motor (27). And the input shaft (29) of the first and second hydraulic pumps (23), (26) is linked to the output shaft (21a) of the engine (21) via the transmission belt (30), and these hydraulic pumps ( 23) The driving of (26) is performed.
[0011]
The drive shaft (34) of the traveling crawler (2) is 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 left and right symmetrical planetary gear mechanisms (35) and (35). Each planetary gear mechanism (35) has one sun gear (36) and an outer periphery of the sun gear (36). Are formed by three planetary gears (37) meshed with each other and a ring gear (38) meshed with these planetary gears (37).
[0012]
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 ) Is rotatably supported.
[0013]
The traveling hydraulic continuously variable transmission mechanism (25) performs forward / reverse rotation and rotation speed control of the first hydraulic motor (24) by adjusting and changing the angle of the rotary swash plate of the first hydraulic pump (23). Thus, the rotational output of the first hydraulic motor (24) is transmitted from the transmission gear (42) of the output shaft (31) through 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 auxiliary transmission mechanism (32) includes an auxiliary transmission shaft (47) having the gear (45) and a parking brake shaft (49) having a gear (48) meshing with the center gear (46). A pair of low speed gears (50) (48), medium speed gears (51) (52), and high speed gears (53) (54) are provided between the shaft (47) and the brake shaft (49). It is configured to enable switching between low speed, medium speed, and high speed by sliding the gear (51) at the center position (note that it has neutrality between low speed and medium speed and between medium speed and high speed). is there). The brake shaft (49) is provided with a vehicle speed detection gear (55) and a vehicle speed sensor (56) for detecting the vehicle speed from the rotational speed of the gear (55). The transmission gear (42) of the output shaft (31) is meshedly connected to the PTO input gear (58) of the cutting PTO shaft (57) that transmits the rotational force to the cutting unit (8).
[0014]
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 carrier shaft (40) via the left and right planetary gear mechanisms (35). The rotation transmitted to the carrier shaft (40) is transmitted to the left and right wheel shafts (34a) of the left and right drive wheels (34) via a pair of left and right reduction gears (60) and (61), respectively.
[0015]
Further, the turning hydraulic continuously variable transmission mechanism (28) controls the forward and reverse rotation of the second hydraulic motor (27) and the rotational speed by adjusting the angle change of the rotary swash plate of the second hydraulic pump (26). The rotation output is transmitted from the output gear of the output shaft (62) of the second hydraulic motor (27) to the input gears (65a) and (65b) of the swing input shaft (64) via the gear transmission mechanism (63). Is transmitted directly to the outer teeth (38b) of the ring gear (38) and to the outer teeth (38b) of the left ring gear (38) via the reverse gear (67) of the reverse shaft (66). Thus, when the second hydraulic motor (27) is rotated forward, the left and right ring gears (38) are configured to rotate the left gear (38) forward and the right gear (38) reversely at the same left and right rotational speed.
[0016]
Thus, when the driving of the first hydraulic motor (24) for driving is performed in a state where the driving of the second hydraulic motor (27) for turning is stopped and the left and right ring gears (38) are fixed stationary, the first hydraulic pressure is obtained. The rotational output from the motor (24) is transmitted from the center gear (46) to the left and right sun gears (36) at the same rotational speed, and the planetary gear (37), carrier (41) and reduction gear (60) of the left and right planetary gear mechanism (35). ) (61) is transmitted to the left and right wheel shafts (34a) at the same rotational speed in the same direction of left and right, so that the aircraft moves straight forward and backward. On the other hand, when the driving of the first hydraulic motor (24) for traveling is stopped and the left and right sun gears (36) are stationary, the second hydraulic motor (27) for turning is driven to rotate forward and reverse. The planetary gear mechanism (35) is rotated forward or backward, and the right planetary gear mechanism (35) is rotated backward or forward so that the driving direction of the left and right traveling crawler (2) is reversed in the front-rear direction. Spin-turn on the spot.
[0017]
Further, when the aircraft is turned left and right by driving the second hydraulic motor (27) for turning while driving the first hydraulic motor (24) for traveling, it is possible to enable turning with a large turning radius. The turning radius is determined according to the speed of the left and right traveling crawler (2).
[0018]
As shown in FIGS. 5 to 13, the main transmission lever (68) connected to the traveling hydraulic continuously variable transmission mechanism (25) and the steering connected to the turning hydraulic continuously variable transmission mechanism (28). The steering wheel (19) is linked and connected to the gear shifting and turning interlocking mechanism (69), and the interlocking mechanism (69) is traveled and steered via the link mechanism (70) (71) which is a traveling gear shifting and steering link system. Are connected to the control levers (72) and (73) of the continuously variable transmission mechanism (25) and (28).
[0019]
The interlocking mechanism (69) includes a rotating plate (75) for supporting the base end bent portion (68a) of the main transmission lever (68) on the cylindrical shaft (74) so as to be swingable in the left-right direction, and the main body side machine. A fixed mounting plate (78) fixed to a frame (76) and supporting the rotating plate (75) through a first pivot (77) in the left-right direction so as to be capable of pivoting back and forth, and the pivot (77). A speed change operation member (80) that is connected to a rotating plate (75) through a second pivot (79) in the front-rear direction orthogonal to the shaft (79) and is rotatable about the shaft (79), and the second pivot (79) ) And a steering operation member (81) that is pivotally connected around the axis of the gear, and the second pivot (79) of the speed change and steering operation members (80) and (81) is each operation output portion at an eccentric position. (80a) (81a) are interlockingly connected to the speed change and steering link mechanism (70) (71).
[0020]
The shift and steering link mechanisms (70) (71) are supported on the frame (76) side of the machine mechanism (69) via the swinging cylinder shaft (83) outside the swinging shaft (82) at the rear position of the interlocking mechanism (69). A transmission arm (84), a steering arm (85) which is a turning output reversing means for fixing a base end to the swing shaft (82), and each output shaft (80a) (81a) 86) (87) and universal joint shafts (88) (89) connecting the arms (84) (85), and a steering output arm (91) fixed to the right end of the swing shaft (82). A first swing arm (95) (96) for shifting and steering provided rotatably on an intermediate shaft (94) attached to a fulcrum bearing (93) of a pivot fulcrum shaft (92) of the operating cabin (18). The tips of the arms (84) (91) and the first swing arms (95) (96) are connected to each other. And a universal joint type first rod (97) (98) for shifting and steering, and a first gear for shifting and steering provided on the intermediate shaft (94) and integrally connected to the first swing arm (95) (96). Two swinging arm (99) (100) and a shift and steering cylinder shaft (103) (103) (which is rotatably supported by a support shaft (102) attached to the bearing plate (101) on the transmission case (22). 104) and the distal ends of the first swing arm (105) (106) and the second swing arm (99) (100), the base ends of which are fixed to the cylindrical shafts (103) (104), are connected. Universal joint-type second rods (107) (108) for shifting and steering, second swinging arms (109) (110) having base ends fixed to the cylindrical shafts (103) (104), and the control Shifting and steering gears for connecting the tips of the levers (72) and (73) A joint-type third rod (111) (112), and a control lever (72) for traveling by turning the speed change operation member (80) about the first pivot (77), Shifting and steering control is performed by operating the steering control lever (73) by turning the steering operating member (81) about the second pivot (79).
[0021]
On the other hand, a gear (114) is provided on the handle operating shaft (113) at the lower end of the steering handle (19), and the gear (114) is engaged with a sector gear (116) attached to the rear rotating shaft (115). A first swing arm (118) of a steering shaft (117) disposed below the position of the main transmission lever (68), and an output arm (119) having a base end fixed to the rotating shaft (115). A second swinging arm integrated with the first swinging arm (118) of the steering shaft (117) is connected between the respective ends via a universal joint type steering first rod (120) which is a steering link mechanism. (121) is connected to the front end of the universal joint shaft (89) via a universal joint type steering second rod (122), and the second pivot (79) is connected by rotating the handle (19). The steering operation member (81) is rotated as the center. It is configured so as.
[0022]
Further, a neutral positioning plate (123) is provided below the gear (114) of the handle operating shaft (113), and one end of the steering detection link (125) is attached to the protruding shaft (124) on the lower surface of the positioning plate (123). And the first swing arm (127) of the reduction arm shaft (126) disposed on the right side of the rotation shaft (115) and the other end long hole (125a) of the detection link (125) are connected to the shaft ( 128), and a universal joint which is a speed reduction link mechanism between the tips of the speed reduction arm (129) of the steering shaft (117) and the second swing arm (130) of the speed reduction arm axis (126). The first speed reduction rod (131) is connected, and the rightmost speed reduction transmission shaft (132) of the speed change operation member (80) and the other end of the second swing arm (130) are connected with a universal joint type second speed reduction rod. Connect at (133) and run State is configured so as to decelerate the steering amount to pull the second reduction rod enough to a large (133) below the running speed of the handle (19).
[0023]
Thus, a universal joint of the second pivot (79) that allows the shifting and steering operation members (80) and (81) to rotate about the axis, the steering arm (85), and the joint shaft (89). And the universal joint portion (88b) (89b) between the operation output shaft (86) (87) and the universal joint shaft (88) (89). ) And the first pivot (77) are positioned on a horizontal horizontal line (L2) orthogonal to the line (L1), and a universal joint portion (88a) between the transmission arm (84) and the joint shaft (88). ) And the joint part (89a) are positioned on a horizontal horizontal line (L3) parallel to the line (L2), and the joint part (88a) is as close as possible to the joint part (89a) (maximum In the main shift lever (68) and the steering handle (19) Even if any one of these is operated during holding, each operating member (80) (81) is only rotated around the axis of the first and second pivots (77) (79). 88) (89) does not apply an operating force.
[0024]
As shown in FIG. 9, when the main transmission lever (68) is moved forward and backward, when the operation member (80) is tilted back and forth by an angle (α1) (α2) about the first pivot (77), the joint shaft ( 88) is pulled or pushed to operate the speed change arm (84) to switch the traveling speed forward and backward, and as shown in FIG. 11, it is operated during this state (when the main speed change lever (68) is other than neutral). When the operating member (81) is tilted up and down by an angle (β1) (β2) about the second pivot (79) by rotating the direction handle (19), the steering shaft (89) is pulled or pushed to operate the steering arm ( 85) is operated to turn the aircraft left and right. That is, even if the turning operation is performed at the neutral position of the main speed, the joint shaft (89) moves on the conical surface centered on the line (L1), and the distance between the joint portions (89a) and (89b) does not change. Therefore, the steering arm (85) does not operate. Then, the steering arm (85) operates when the turning operation is performed at a position other than the neutral of the main speed change, and when switching to the forward / reverse operation, the steering arm (85) operates in the backward / forward direction, and the second hydraulic motor. The rotation of (27) is configured to be reversed in the forward and reverse directions.
[0025]
In other words, if the forward rotation of the first hydraulic motor (24) for traveling is defined as forward travel, the planetary gear mechanism (35) by the second hydraulic motor (27) for rotation during reverse travel during reverse rotation is the forward travel. When the first hydraulic motor (24) rotates backward (reverse), the second hydraulic pump (in order to match the turning direction of the machine body by the operation of the handle (19) during forward movement and reverse movement is reversed. 26) by switching the swash plate angle to the opposite direction (the rotation direction of the input shafts of the first and second hydraulic pumps (23) and (26) is constant), the rotation of the second hydraulic motor (27) is made forward and backward. Sometimes it is the opposite direction.
[0026]
That is, in this case, the operation member (80) during the forward operation is tilted to the angle (α1) ahead of the neutral position, and the second rod (122) is pulled by the right rotation operation of the handle (19), thereby operating the operation member (81). Is tilted to the downward angle (β2) side, the output portion (81a) of the operating member (81) is brought closer to the steering arm (85) side, and the steering arm (85) is centered on the swing shaft (82). ) In a direction away from the operation member (81) (counterclockwise in FIG. 5), and the control lever (73) is rotated downward through the first and second rods (98) (108). Then, the second hydraulic motor (27) for turning is rotated forward. That is, the aircraft is turned to the right (the speed of the traveling crawler (2) is large on the left side and small on the right side).
[0027]
Further, during the forward operation described above, when the second rod (122) is pushed up by the left turning operation of the handle (19) and the operation member (81) is tilted to the upward angle (β1) side, the operation member (81 ) Of the steering arm (85) closer to the operating member (81) side with the pivot shaft (82) as the center (clockwise in FIG. 5). And the control lever (73) is rotated upward to reversely rotate the second hydraulic motor (27). In other words, the aircraft is turned leftward (the speed of the traveling crawler (2) is large on the right side and small on the left side).
[0028]
Further, the operation member (80) during the backward operation is inclined toward the angle (α2) behind the neutral position, and the second rod (122) is pulled by the right rotation operation of the handle (19) to lower the operation member (81). When tilting to the direction angle (β2) side, the output portion (81a) of the operating member (81) is moved away from the steering arm (85) side, and the steering arm (85) is centered on the swing shaft (82). The second hydraulic motor (27) is rotated in the reverse direction by rotating in the direction approaching the operation member (81) (clockwise in FIG. 5) and rotating the control lever (73) upward. That is, the aircraft turns backward and turns right (the speed of the traveling crawler (2) is large on the left side and small on the right side).
[0029]
Furthermore, contrary to the above, when the operation member (81) is tilted to the upward angle (β1) side by the left rotation operation of the handle (19) during the reverse operation, the output portion of the operation member (81) (81a) is moved closer to the operation member (81) side, and the steering arm (85) is rotated away from the operation member (81) around the swing shaft (82) (counterclockwise in FIG. 5). The control lever (73) is rotated downward to rotate the second hydraulic motor (27) forward. In other words, the aircraft is turned backward to turn left (the speed of the traveling crawler (2) is large on the right side and small on the left side).
[0030]
Thus, in the turning operation at the time of forward and backward movement, the movement of the steering arm (85) is reversed, and the turning operation direction of the steering handle (19) and the direction of the machine body are both forward and backward. This is to match the turning direction.
[0031]
Further, FIG. 15 shows the relationship between the turning angle of the steering handle (19) and the speed of the left / right traveling crawler (2) when the aircraft is turning to the left, and the left / right traveling increases as the turning angle of the steering wheel (19) increases. The speed difference of the crawler (2) becomes large, and 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, Even when the aircraft turns right, the left and right crawlers (2) are the same in the reverse relationship. As is apparent from FIG. 15, the travel speed change operation of the main speed change lever (68), which is the speed change operation member. The first hydraulic pump (23) and the first hydraulic motor (24), which are traveling speed change members that transmit the driving force of the engine (21) to the left and right traveling crawlers (2) and (2), which are left and right traveling portions, Operation of direction handle (19) In a mobile agricultural machine provided with a second hydraulic pump (26) and a second hydraulic motor (27) which are steering members that cause a difference in the driving speed of the left and right traveling crawlers (2) and (2) by operation, a steering handle (19 ) In which the traveling speed is maintained substantially constant within the range of the substantially constant steering operation based on the straight traveling position, and the operating speed of the steering handle (19) is adjusted outside the range of the steering operation. In conjunction with this, an operation of automatically increasing / decelerating / decreasing is performed, and only the steering handle (19) is operated to decelerate via the first decelerating rod (131) to change the direction at the field headland and move to the next work process. Then, by returning to the straight traveling, the first decelerating rod (131) is moved backward to increase the work traveling speed of the previous process to resume the work, thereby omitting the traveling speed change operation accompanying the steering operation and during the harvesting operation. Uncut grain row (crop) Or, even if a steering operation is carried out along the hull, etc., the traveling speed is prevented from changing unevenly, while maintaining the same traveling speed, the course can be corrected during the harvesting work, and the operator's driving It is configured so that proper steering operation can be performed by making the sense and the traveling motion of the aircraft substantially coincide.
[0032]
In addition, while reducing the traveling speed according to the steering operation amount of the steering handle (19), the drive speed difference between the left and right traveling crawlers (2) and (2) is continuously increased to shift to the spin turn operation, The straight-running and course correction operations during the harvesting operation and the spin-turn operation for changing the direction to the next work process position on the field headland can be smoothly performed only by a series of continuous steering operations, and the steering handle The amount of deceleration of the traveling crawler (2) on the side of the turning direction and the amount of acceleration of the traveling crawler (2) on the opposite side of the turning direction are substantially equal by the steering operation within a substantially constant range based on the straight traveling position of (19). The first hydraulic pump (23), the first hydraulic motor (24), the second hydraulic pump (26), and the second hydraulic motor (27) are continuously variable with substantially the same specifications. A first hydraulic pump configured using a speed change mechanism 23) and a reduction ratio between the first hydraulic motor (24) and the traveling crawler (2) and a reduction ratio between the second hydraulic pump (26) and the second hydraulic motor (27) and the traveling crawler (2), or The driving force required for the small radius turn necessary for the spin turn operation is secured.
[0033]
Also, as shown in FIG. 12, the detection link (125) provided on the steering handle (19) has the first swing arm (127) angled in the same direction (θ) in either the right or left turn operation from the neutral position. ), The second deceleration rod (133) is always pulled, and when the operation member (80) during forward operation is inclined to the angle (α1) side, the joint portions (88a) (88b) ), And when the operation member (80) during reverse operation is inclined to the angle (α2) side, the distance between the joint portions (88a) (88b) is increased to increase the speed change arm (84). Are respectively displaced toward the low speed side in the neutral direction, and the vehicle is decelerated according to the turning amount.
[0034]
Further, the center of the universal joints (97a) and (98a) of the first rods (97) and (98) and the swing arms (95) and (96) for transmitting the operating force for shifting and steering are arranged in the driving cabin (18 ) To coincide with the position of the pivot fulcrum shaft (92) so that the driving cabin (18) can be rotated in the forward direction without removing these operating systems in the neutral holding of shifting and steering. It is composed.
[0035]
4 and 14, the first and second hydraulic pumps (23) and (26) and the first and second hydraulic motors (24) and (27) are respectively connected to loop hydraulic circuits (134) and (135). ), The output shafts (31) and (62) of the first and second hydraulic motors (24) and (27) are connected to the output shaft (136) and (137) by the operation of the solenoid valves (136) and (137). 31) A travel and turning brake device (138) (139) for stationary travel and a straight-forward fixing is provided, and the brake shaft (49) is held stationary on the parking brake shaft (49). A parking brake device (140) is provided.
[0036]
【The invention's effect】
In the present invention, the traveling speed change members (23) and (24) that transmit the driving force of the engine (21) to the left and right traveling portions (2) and (2) by the traveling speed change operation of the speed change operation member (68), and the steering handle In the mobile agricultural machine provided with the steering members (26) and (27) that cause a difference in the driving speeds of the left and right traveling sections (2) and (2) by the steering operation of (19), the straight traveling position of the steering handle (19) is set. By changing the deceleration amount of the traveling part (2) on the turning direction side and the increasing amount of the traveling part (2) on the opposite side to the turning direction by a steering operation within a substantially constant range as a reference, the traveling speed is changed. The steering handle is configured to perform an operation of maintaining substantially constant and an operation of automatically increasing / decreasing the traveling speed in conjunction with the operation of the steering handle (19) outside the range of the steering operation. The travel speed is reduced via the deceleration link mechanism (131) by the operation of (19). By turning the steering handle (19) to move to the next work process and return to straight travel, the speed reduction link mechanism (131) is moved backward to increase the travel speed of the previous process. So that work can be resumed.
In this manner, the amount of deceleration of the traveling unit on the turning direction side and the amount of acceleration of the traveling unit on the opposite side of the turning direction can be obtained by a steering operation within a substantially constant range with reference to the straight position of the steering handle (19). Since it is possible to perform an operation of keeping the traveling speed substantially constant by changing the speed substantially the same, the direction can be changed at the field headland by decelerating by the operation of the steering handle (19).
Then, the operation can be resumed by increasing the operation travel speed to the previous process by operating the steering handle (19) to move to the next operation process and return to the straight traveling, thereby eliminating the traveling speed change operation associated with the steering operation. It is possible to easily prevent the traveling speed from changing unevenly even if the steering operation is performed along the crop line or the fence during the farming work, while maintaining the substantially same traveling speed. The course can be corrected, and an appropriate steering operation can be easily performed by substantially matching the operator's driving feeling with the traveling motion of the aircraft.
[Brief description of the drawings]
FIG. 1 is a perspective explanatory view of an operation system of a main transmission lever and a steering handle.
FIG. 2 is an overall side view of the combine.
FIG. 3 is an overall plan view of the combine.
FIG. 4 is an explanatory diagram of a mission drive system.
FIG. 5 is an explanatory diagram of a traveling speed change and steering operation unit.
FIG. 6 is an explanatory front view of an operation unit.
FIG. 7 is an explanatory plan view of an operation unit.
FIG. 8 is an explanatory side view of an operation unit.
FIG. 9 is an explanatory side view of an operation member.
FIG. 10 is a front explanatory view of an operation member.
FIG. 11 is an explanatory plan view of an operation member.
FIG. 12 is an explanatory plan view of a steering handle portion.
FIG. 13 is an explanatory plan view of a link mechanism unit.
FIG. 14 is a hydraulic circuit diagram.
FIG. 15 is a diagram illustrating a relationship between a handle turning angle and a crawler speed when the aircraft is turning.
[Explanation of symbols]
(2) Traveling crawler (traveling part)
(19) Steering handle (21) Engine (23) First hydraulic pump (traveling transmission member)
(24) First hydraulic motor (traveling transmission member)
(26) Second hydraulic pump (steering member)
(27) Second hydraulic motor (steering member)
(68) Main speed change lever (speed change operation member)

Claims

A travel transmission member that transmits the driving force of the engine to the left and right traveling parts by a traveling speed change operation of the speed change operation member, and a steering member that causes a difference in the driving speed of the left and right traveling parts by the steering operation of the steering handle In agricultural machinery,
Travel speed by changing the deceleration amount of the traveling part on the turning direction side and the acceleration amount of the traveling part on the opposite side to the turning direction by steering operation within a substantially fixed range with the straight position of the steering handle as a reference. the operation and to maintain substantially constant, and configured to perform an operation of changing automatically increase or decrease speed and the running speed outside the range of the steering operation in conjunction with the operation of the steering wheel,
By operating the steering handle, the traveling speed is decelerated via the deceleration link mechanism, the direction is changed at the field headland, and the steering link is moved back to the next work process to return to the straight traveling. A mobile agricultural machine characterized by being able to restart the work by increasing the traveling speed of the previous process work.