JP2004100853A - Working vehicle - Google Patents

Working vehicle Download PDF

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Publication number
JP2004100853A
JP2004100853A JP2002265013A JP2002265013A JP2004100853A JP 2004100853 A JP2004100853 A JP 2004100853A JP 2002265013 A JP2002265013 A JP 2002265013A JP 2002265013 A JP2002265013 A JP 2002265013A JP 2004100853 A JP2004100853 A JP 2004100853A
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Japan
Prior art keywords
speed
hydraulic
output
traveling
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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JP2002265013A
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Japanese (ja)
Inventor
Shigemi Hidaka
日高　茂實
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Yanmar Co Ltd
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Yanmar Agricultural Equipment Co Ltd
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Publication date
Application filed by Yanmar Agricultural Equipment Co Ltd filed Critical Yanmar Agricultural Equipment Co Ltd
Priority to JP2002265013A priority Critical patent/JP2004100853A/en
Priority to CNB02829582XA priority patent/CN100415075C/en
Priority to PCT/JP2002/012249 priority patent/WO2004023862A1/en
Priority to KR1020057004015A priority patent/KR100955857B1/en
Priority to AU2002355026A priority patent/AU2002355026A1/en
Publication of JP2004100853A publication Critical patent/JP2004100853A/en
Pending legal-status Critical Current

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    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D41/00—Combines, i.e. harvesters or mowers combined with threshing devices
    • A01D41/12—Details of combines
    • A01D41/127—Control or measuring arrangements specially adapted for combines
    • A01D41/1274—Control or measuring arrangements specially adapted for combines for drives
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers

Abstract

<P>PROBLEM TO BE SOLVED: To improve maneuvering operability and handling performance by starting driving of a traveling part 2 (and a working part 7) by stable output of a hydraulic shift mechanism 40 by varying output of only a hydraulic pump 38. <P>SOLUTION: This working vehicle drives the traveling part 2 and the working part 7 by shift output of the hydraulic pump 38 of the hydraulic shift mechanism 40 at a speed just before the highest speed or less, and directly connects the input side and the output side of the hydraulic shift mechanism 40 in the vicinity of the highest speed by a constant speed mechanism 76, and is characterized in that a hydraulic motor 39 of the hydraulic shift mechanism 40 is formed as an output variable structure, and an output variation in the hydraulic motor 39 is fixed on the low speed side before performing directly connecting operation of the constant speed mechanism 76. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
本発明は例えば左右一対の走行クローラを装設して移動するコンバインまたはトラクタまたは建設車輌などの作業車に関する。
【０００２】
【発明が解決しようとする課題】
従来、例えば特開昭６２−１６３８２６号公報に示す如く、左右走行クローラを装設したコンバインなどにおいて、最高速度で油圧変速機構の油圧ポンプの変速出力により、走行部（走行クローラ）を駆動すると共に、最高速度で油圧変速機構の入力側と出力側を定速機構により直結させるから、不安定で損失馬力が大きい油圧変速機構の最高速度の出力により運転される不具合があると共に、油圧変速機構の出力から定速機構の出力に切換えても速度が上がることがなく、運転性能の向上などを容易に図り得ない等の問題がある。また、定速機構により直結される前と後の回転差（速度差）によってショックが発生し易い等の不具合があると共に、定速機構の定速出力によって走行部を駆動するとき、例えば油圧伝動特性が不均一な油圧変速機構では、油圧ポンプとモータの各吐出量を一致させるのが困難であり、損失馬力の回収を効果的に行えなかったり、負荷を増大させる等の不具合がある。
【０００３】
【課題を解決するための手段】
然るに、本発明は、請求項１の如く、最高速手前以下の速度で、油圧変速機構の油圧ポンプの変速出力により、走行部を駆動すると共に、最高速付近で油圧変速機構の入力側と出力側を定速機構により直結させる作業車において、油圧変速機構の油圧モータを出力可変構造とし、定速機構の直結動作を行わせる前は低速側で油圧モータの出力可変を固定させるもので、油圧モータの出力を可変にすることによって油圧変速機構の変速範囲を拡大させることが行えるが、油圧変速機構の出力が不安定になり易い不具合がある。そこで、油圧変速機構の出力によって走行部（及び作業部）の駆動を開始するとき、油圧モータの出力を低速側にロックさせるから、油圧ポンプだけの出力を可変して油圧変速機構の安定した出力により走行部（及び作業部）の駆動を開始し得、運転操作性及び取扱い性を向上させ得る。
【０００４】
また、請求項２の如く、定速機構の出力操作により油圧モータの出力可変をフリーにするもので、油圧ポンプの入力側と油圧モータの出力側を直結させたとき、油圧モータの出力調整をフリーにすることにより、油圧ポンプ側の吐出量に応じて主回路油圧が最低になるように油圧モータが出力調整され、油圧ポンプとモータの各吐出量を容易に一致させ得、主油圧回路油圧をチャージ圧にスムーズに低下させ得、油圧変速機構の損失馬力を有効に回収し得る。
【０００５】
【発明の実施の形態】
以下、本発明の実施例を図面に基づいて詳述する。図１はコンバインの全体の斜視図、図２は同右側面図、図３は平面説明図であり、図中１は左右一対の走行クローラ２を装設する左右一対のトラックフレーム、３は前記の左右トラックフレーム１に架設する機台、４はフィードチェン５を左側に張架し扱胴６及び処理胴を内蔵している脱穀機である脱穀部、７は引起機構８及び刈刃９及び穀稈搬送機構１０などを備える刈取部、１１は刈取フレーム１２を介して刈取部７を昇降させる油圧昇降シリンダ、１３は排藁チェン１４終端を臨ませる排藁処理部、１５は脱穀部４からの穀粒を揚穀筒を介して搬入する穀物タンク、１６・１７は前記タンク１５の穀粒を機外に搬出する排出オーガ、１８は運転操作ハンドル１９及び運転席２０を備える運転キャビン、２１は運転キャビン１８下方に設けるエンジンであり、連続的に穀稈を刈取って脱穀するように構成している。
【０００６】
さらに、図４乃至図８に示す如く、機台３前側で左右の走行クローラ２の間にミッションケース２２を配設させ、ミッションケース２２とエンジン２１を略直列に前後に設け、ミッションケース２２を介して走行クローラ２にエンジン２１の駆動力を伝えると共に、脱穀部４前側の機台３上面に左右の支持台２３・２４を立設させ、支持台２３・２４に刈取フレーム１２を介して刈取部７を昇降自在及び横移動可能に設ける。また、支持台２３・２４後側の機台３上面にカウンタケース２５を設け、脱穀部４及び刈取部７にカウンタケース２５を介してエンジン２１の駆動力を伝える。
【０００７】
さらに、ミッションケース２２側方の機台３にキャビン前フレーム２６を立設させ、キャビン１８のステップフレーム２７前部を前フレーム２６上部に回動支点軸２８を介して設け、支点軸２８回りにキャビン１８を前方に回動自在に支持させると共に、右の支持台２４に左のキャビン後フレーム２９を立設させ、機台３に立設させる右のキャビン後フレーム３０との間の機台３上面にエンジン２１を設け、エンジン２１をエンジンルームカバー３１で覆う。また、前記カバー３１の上方で左右の後フレーム２９・３０上部をキャビン横フレーム３２によって連結させ、キャビン横フレーム３２にフックレバー３３を設け、キャビン１８のステップフレーム２７後部を横フレーム３２に上載させてフックレバー３３により係脱自在に固定させると共に、右の支持台２４と前フレーム２６の間に水平連結フレーム３４を固定させ、水平連結フレーム３４中間と横フレーム３２中間に傾斜連結フレーム３５を固定させ、連結フレーム３４・３５によってフレーム剛性を確保する。また、左の後フレーム２９にオーガ支柱３６を連結させて上側にオーガレスト３７を設け、昇降及び旋回自在に設ける排出オーガ１７をオーガレスト３７の本機収納位置に支持させる。
【０００８】
さらに、図９乃至図１４に示す如く、前記走行クローラ２を駆動するミッションケース２２は、１対の油圧走行ポンプ３８及び油圧走行モータ３９を設けて走行主変速用の油圧式無段変速機構を形成する走行変速部材４０と、１対の油圧旋回ポンプ４１及び油圧旋回モータ４２を設けて旋回用の油圧式無段変速機構を形成する旋回部材４３とを備え、前記エンジン２１の出力軸４４にミッションケース２２の入力軸４５を介して連結させて前記各ポンプ３８・４１を駆動するように構成している。
【０００９】
また、前記走行モータ３９のモータ軸４６に、副変速機構４７及び差動機構４８を介して左右走行クローラ２の各駆動輪４９を連動連結させるもので、前記差動機構４８は左右対称の１対の遊星ギヤ機構５０を有し、各遊星ギヤ機構５０は１つのサンギヤ５１と、該サンギヤ５１の外周で噛合う３つのプラネタリギヤ５２と、これらプラネタリギヤ５２に噛合うリングギヤ５３などで形成している。
【００１０】
前記プラネタリギヤ５２は、サンギヤ５１の遊転軸５４と同軸線上の車軸５５のキャリヤ５６にそれぞれ回転自在に軸支させ、左右のサンギヤ５１を挾んで左右のキャリヤ５６を対向配置させると共に、前記リングギヤ５３は各プラネタリギヤ５２に噛み合う内歯を有して車軸５５に回転自在に軸支させ、車軸５５を延設して駆動輪４９を軸支させている。
【００１１】
また、走行変速部材４０は、走行ポンプ３８の斜板角度の変更により走行モータ３９の正逆回転と回転数の制御を行うもので、走行モータ３９の回転を、モータ軸４６と副変速機構４７の低速及び高速ギヤ５７・５８とブレーキ軸５９と分岐軸６０を介して、左右のリングギヤ５３に伝達して左右のキャリヤ５６を回転させるように構成している。また前記ブレーキ軸５９に駐車ブレーキ６１を設けると共に、刈取部７に回転力を伝達する刈取駆動プーリ６２を前記モータ軸４６に設け、刈取部７を車速同調速度で駆動させる。
【００１２】
上記のように、前記分岐軸６０を介しリングギヤ５３に伝達された走行モータ３９の駆動力を、左右の遊星ギヤ機構５０を介して左右キャリヤ５６に伝達させると共に、左右キャリヤ５６に伝達された回転を左右の駆動輪４９にそれぞれ伝え、左右走行クローラ２を同一方向に同一速度で駆動するように構成している。
【００１３】
さらに、旋回用の油圧式無段変速機構で形成する旋回部材４３は、旋回ポンプ４１の斜板角度の変更により旋回モータ４２の正逆回転と回転数の制御を行うもので、操向出力ブレーキ６３を設けるモータ軸６４と、操向出力クラッチ６５を設けるクラッチ軸６６と、前記の左右サンギヤ５１に常時噛合させる左右入力ギヤ６７・６８を設け、旋回モータ４２の出力用の前記モータ軸６４及び操向出力クラッチ６５を介してクラッチ軸６６を連結させ、クラッチ軸６６に正転ギヤ６９及び逆転ギヤ７０を介して左右の入力ギヤ６７・６８を連結させる。そして、右側のサンギヤ５１に正転ギヤ６９を介してモータ４２回転力を伝え、また左側のサンギヤ５１に逆転ギヤ７０を介してモータ４２回転を伝え、旋回モータ４２を正転（逆転）時、左右同一回転数で、左サンギヤ５１を逆転（正転）させ、かつ右サンギヤ５１を正転（逆転）させ、左右走行クローラ２を逆方向に同一速度で駆動するように構成している。
【００１４】
而して、旋回モータ４２を停止させて左右サンギヤ５１を静止固定させた状態で、走行モータ３９を駆動すると、走行モータ３９の回転は左右のリングギヤ５３に同一回転数で伝達され、左右遊星ギヤ機構５０のキャリヤ５６を介して左右の走行クローラ２が左右同一回転方向で同一回転数によって駆動され、機体の前後方向直進走行が行われる。一方、走行モータ３９を停止させて左右のリングギヤ５３を静止固定させた状態で、旋回モータ４２を正逆回転駆動すると、左側の遊星ギヤ機構５０が正或いは逆回転、また右側の遊星ギヤ機構５０が逆或いは正回転し、左右走行クローラ２を逆方向に駆動し、機体を左或いは右に旋回させる。また、走行モータ３９を駆動させながら、旋回モータ４２を駆動することにより、機体が左右に旋回して進路が修正されるもので、機体の旋回半径は旋回モータ４２の出力回転数によって決定される。
【００１５】
また、前記入力軸４５にファン軸７１を連結させ、ファン軸７１によってエンジン２１水冷用のラジエータの冷却ファン７２を駆動させると共に、前記の走行及び旋回ポンプ３８・４１の各ポンプ軸７３・７４にギヤ群７５を介して前記ファン軸７１を連結させ、各ポンプ３８・４１に入力軸４５を連結させると共に、走行ポンプ３８のポンプ軸７３と、走行モータ３９のモータ軸４６を、定速クラッチ７６を介して連結させる定速軸７７を設け、定速クラッチ７６を入にしたとき、定速軸７７を介してポンプ軸７３とモータ軸４６をギヤ連結させ、走行変速部材４０を介することなく、入力軸４５の回転を副変速機構４７に伝え、エンジン２１の定速回転によって左右の走行クローラ２を駆動させ、略一定の車速で走行して収穫作業などを行わせる。なお、旋回ポンプ軸７４上にチャージポンプ７８を設けて駆動する。
【００１６】
さらに、図１５に示す如く、走行ポンプ３８の斜板７９角度を変更して出力調整する主変速シリンダ８０と、主変速レバー８１及び操向ハンドル１９に連結させて切換える変速バルブ８２と、走行ポンプ３８出力を一定量減速するバルブ８３を設け、前記チャージポンプ７８を各バルブ８２・８３を介して主変速シリンダ８０に油圧接続させるもので、主変速レバー８１によって変速バルブ８２を切換え、主変速シリンダ８０を作動させて走行ポンプ３８の斜板７９角度を変更させ、走行モータ３９のモータ軸４６の回転数を無段階に変化させたり、逆転させる走行変速動作を行わせ、また前記斜板７９の角度調節動作によって変速バルブ８２が中立復帰するフィードバック動作を行わせ、主変速レバー８１の操作量に比例させて前記斜板７９角度を変化させ、走行モータ３９の回転数を変化させて車速を変更させる。
【００１７】
また、走行モータ３９の斜板８４角度を変更して出力調整する副変速シリンダ８５を設け、前記チャージポンプ７８に電磁副変速バルブ８６を介して副変速シリンダ８５を油圧接続させ、副変速バルブ８６が中立のときに副変速シリンダ８５を油タンクであるミッションケース２２に短絡させ、走行モータ３９の斜板８４角度を主回路油圧によって変化させると共に、副変速バルブ８６の切換によって斜板８４角度を強制的に変化させ、走行モータ３９の出力を高速または低速に変更させる。
【００１８】
さらに、旋回ポンプ４１の斜板８７角度を変更して出力調整する旋回シリンダ８８を設け、操向ハンドル１９及び主変速レバー８１に連結させて切換える旋回バルブ８９並びに電磁自動操向バルブ９０を介してチャージポンプ７８を旋回シリンダ８８に油圧接続させ、操向ハンドル１９によって旋回バルブ８９を切換え、旋回シリンダ８８を作動させて旋回ポンプ４１の斜板８７角度を変更させ、旋回モータ４２のモータ軸６４の回転数を無段階に変化させたり、逆転させる左右旋回動作を行わせ、また前記斜板８７の角度調節動作によって旋回バルブ８９が中立復帰するフィードバック動作を行わせ、操向ハンドル１９の操作量に比例させて前記斜板８７角度を変化させ、旋回モータ４２の回転数を変化させて左右旋回角度を変更させる。
【００１９】
また、主変速レバー８１が中立以外の位置に操作され、操向ハンドル１９が直進以外に操作されることにより、主変速レバー８１の操作方向と操作量に比例させて走行ポンプ３８の油圧出力を増減させ、油圧モータ３９を正逆転または増減速させて前後進速度（車速）を変更させると共に、主変速レバー８１の操作量に比例させて旋回ポンプ４１出力を変化させるもので、高速側走行変速によって旋回半径を自動的に小さくし、かつ低速側走行変速によって旋回半径を自動的に大きくし、操向ハンドル１９の一定操作によって走行速度に関係なく左右走行クローラ２の旋回半径を略一定に維持させ、作業走行速度の変更並びに未刈り穀稈列などに機体を沿わせる進路修正などを行わせる。一方、操向ハンドル１９の操作量に比例させて各バルブ８２・８９の制御により旋回ポンプ４１出力と走行ポンプ３８出力を変化させ、旋回半径（操舵角）を小さく（大きく）したとき、走行速度（車速）を比例させて減速させ乍ら、左右の走行クローラ２の速度差を大きくし、左右に旋回させるもので、左右走行クローラ２の駆動速度を変更して条合せ進路修正並びに圃場枕地でのスピンターンによる方向転換を行い、連続的に穀稈を刈取って脱穀する収穫作業を行う。なお、主変速レバー８１が中立のとき、操向ハンドル１９の操作に関係なく、旋回バルブ８９が中立維持され、旋回ポンプ４１の油圧出力が略零に保たれ、旋回モータ４２を停止させる。
【００２０】
さらに、図１４乃至図２２に示す如く、前記エンジン２１の出力軸４４を前側及び後側に突設させ、出力軸４４の前側に前記入力軸４５を連結させ、出力軸４４の後側に作業出力プーリ９１を設けると共に、エンジン２１の左側で脱穀部４前側の機台３上面にカウンタケース２５を設け、入力プーリ９２、車速同調プーリ９３、脱穀プーリ９４、刈取プーリ９５、選別プーリ９６をカウンタケース２５に軸支させ、ケース２５後側の入力プーリ９２を作業出力プーリ９１にテンション脱穀クラッチ９７を介してベルト９８連結させ、エンジン２１の駆動力をカウンタケース２５に伝える。また、右支持台２４前側のアイドルプーリ９９を介してミッションケース２２の刈取駆動プーリ６２に前記カウンタケース２５右側の車速同調プーリ９３をベルト１００連結させると共に、機台３の前側上面に立設させる支持台２３・２４に刈取入力ケース１０１を回転自在に軸支させ、前記ケース１０１に刈取フレーム１２を連結させてケース１０１回りに刈取部７を回転させて昇降させるもので、前記ケース１０１左側に刈取入力軸１０２を介して刈取入力プーリ１０３を軸支させ、前記カウンタケース２５左側の刈取プーリ９５を刈取入力プーリ１０３にベルト１０４連結させ、刈取部７の各部に駆動力を伝える。
【００２１】
また、前記扱胴６の駆動入力プーリ１０５にカウンタケース２５前側の脱穀プーリ９４をベルト１０６連結させ、扱胴６下側の選別唐箕及び揺動選別機構に選別プーリ９６から駆動力を伝え、脱穀部６の各部を駆動すると共に、前記カウンタケース２５の左側面にフィードチェン入力軸１０７を設け、外側に移動可能な前記フィードチェン５の駆動スプロケット１０８に入力軸１０７から動力を伝える。また、前記穀物タンク１５の前側に排出駆動プーリ１０９を設け、該プーリ１０９を前記作業出力プーリ９１に排出クラッチ１１０を介してベルト連結させ、排出オーガ１７にエンジン２１出力を伝えてタンク１５の穀粒を排出させる。
【００２２】
さらに、前記カウンタケース２５に扱胴入力軸１１１を軸支させ、該軸１１１を前後方向に延設させ、カウンタケース２５前面外側の前記軸１１１前側に脱穀プーリ９４を設け、カウンタケース２５の後面外側の前記軸１１１後側に入力プーリ９２を設け、扱胴入力軸１１１にエンジン２１の一定回転動力を入力させて定速回転させる。また、前記カウンタケース２５の右側に同調入力軸１１２を軸支させ、カウンタケース２５の右側外側の前記軸１１２右側に車速同調プーリ９３を設け、アイドルプーリ９９を介してプーリ６２・９３間にベルト１００を緊張させ、ミッションケース２２からカウンタケース２５に車速同調動力を入力させる。
【００２３】
さらに、前記扱胴入力軸１１１に右側をベベルギヤ１１３連結させるカウンタ軸または選別入力軸である定速軸１１４と、該軸１１４の前側に略平行に設ける車速同調軸１１５とを、カウンタケース２５に軸支させると共に、刈取変速機構１１６を形成する低速ギヤ１１７及び高速ギヤ１１８を前記各軸１１４・１１５の間に設け、低速及び中立及び高速の各刈取変速を行う刈取変速スライダ１１９によって前記各ギヤ１１７・１１８を車速同調軸１１５に択一的に係合させ、刈取変速を行う。また、前記各ギヤ１１７・１１８に同調入力軸１１２の車速同調回転力を伝える一方向クラッチ１２０を同調入力軸１１２上に設け、車速同調プーリ９３からの動力を一方向クラッチ１２０によって伝える前記ギヤ１１７・１１８を介して車速同調軸１１５を回転させるように構成する。
【００２４】
さらに、刈取定速機構１２１を形成する流し込みギヤ１２２と高速カットギヤ１２３を前記各軸１１４・１１５の間に設け、刈取部７を流し込み駆動または高速カット駆動させる切換スライダ１２４によって前記各軸１１４・１１５に前記各ギヤ１２２・１２３を択一的に係合させ、刈取部７を流し込み駆動して走行状態に関係なく刈取部７の穀稈をフィードチェン５側に搬送させる一方、刈取部７を高速カット駆動して車速同調の最高速よりも早い一定回転速度で刈取部７を駆動して倒伏穀稈を刈取る。
【００２５】
また、前記カウンタケース２５の左側で下部後側に定速軸１１４の左側端を突出させ、該軸１１４左側端部に選別プーリ９６を軸支させる。さらに、カウンタケース２５の左側で下部前側に刈取伝動軸１２５を軸支させ、該軸１２５右側を車速同調軸１１５にトルクリミッタ１２６を介して連結させ、カウンタケース２５左側に突出させる前記軸１２５の左側端部に刈取プーリ９５を軸支させると共に、前記刈取入力軸１０２に刈取駆動軸１２７をギヤ１２８連結させ、刈取駆動軸１２７に刈取入力プーリ１０３を軸支させるもので、前記の左の支持台２３に支点軸１２９を介してギヤ１２８のケースを縦軸回りに回転自在に設け、刈取入力ケース１０１の左側をギヤ１２８のケースに固定させ、各ケース１０１に前記ギヤ１２８を内設させ、刈取入力軸１０２の左端側から刈取り動力を入力させ、前記ケース１０１右端側の刈取フレーム１２に内挿させる刈取伝動軸１３０を介して刈取部７の駆動を行わせる一方、支点軸１２９回りに機体左側に略水平に刈取部７を回転移動させ、機体内側の各ケース２２・２５付近のメンテナンス等を行う。
【００２６】
さらに、前記カウンタケース２５の左側上部に前記フィードチェン入力軸１０７を軸支させ、フィードチェンクラッチ１３１を設けるフィードチェン駆動軸１３２に前記入力軸１０７をチェン１３３連結させると共に、定速軸１１４の回転を車速同調軸１１５の回転数変化によって変速して伝えるフィードチェン変速機構１３４を設け、サンギヤ１３５とプラネタリギヤ１３６とリングギヤ１３７を備える遊星ギヤ機構１３８によって無段変速可能に前記機構１３４を形成するもので、定速軸１１４にサンギヤ１３５を係合軸支させ、定速軸１１４に遊転支持させるリングギヤ１３７を車速同調軸１１５にギヤ１３９連結させると共に、プラネタリギヤ１３６を遊転支持させる軸受体１４０を定速軸１１４に遊転支持させ、前記フィードチェンクラッチ１３１を介して前記フィードチェン駆動軸１３２に軸受体１４０をギヤ１４１連結させ、穀稈の搬送に必要な最低回転を確保し乍ら、低い一定回転から高回転にフィードチェン５速度を車速と同調させて変更可能に構成している。
【００２７】
また、刈取変速スライダ１１９を作動させる油圧刈取変速シリンダ１４２と、切換スライダ１２４を作動させる油圧刈取定速シリンダ１４３と、脱穀クラッチ９７を入にする油圧脱穀シリンダ１４４を、前記カウンタケース２５の上面蓋である油路ベース１４５に固定させると共に、前記定速クラッチ７６を入にする車速定速シリンダ１４６を作動させる車速定速バルブ１４７と、刈取変速シリンダ１４２を作動させる刈取変速バルブ１４８と、刈取定速シリンダ１４３を作動させる刈取定速バルブ１４９と、脱穀シリンダ１４４を作動させる脱穀バルブ１５０とを、前記チャージポンプ７８に並列に油圧接続させる。
【００２８】
さらに、図１５、図２３乃至図２８に示す如く、前記脱穀クラッチ９７をテンションアーム１５１に軸支させ、カウンタケース２５の支軸１５２にテンションアーム１５１を回転自在に軸支させ、折曲自在な２本のリンク１５３・１５４を介して脱穀シリンダ１４４のピストンロッド１５５をテンションアーム１５１に連結させ、ピストンロッド１５５の押し（進出）動作により、脱穀クラッチ９７を入動作させてベルト９８を緊張させる一方、ピストンロッド１５５の引き（退入）動作により、脱穀クラッチ９７を切動作させてベルト９８を弛める。また、脱穀クラッチ９７を切り側に弾圧させるバネ１５６をリンク１５４に連結させると共に、複動型の脱穀シリンダ１４４のピストンロッド１５５進出側の油路の戻り側に絞り弁１５７を設け、ピストンロッド１５５を遅い速度で進出させて脱穀クラッチ９７を入にする一方、ピストンロッド１５５を速い速度で退入させて脱穀クラッチ９７を切にする。
【００２９】
上記から明らかなように、エンジン２１からの動力を、走行部である走行クローラ２と作業部である脱穀部４及び刈取部７に分配する伝動ケースであるカウンタケース２５を備える作業車において、カウンタケース２５の一部を形成する油路ベース１４５に、作業クラッチである脱穀クラッチ９７または作業変速用の複数の油圧シリンダ１４２・１４３・１４４を設けるもので、カウンタケース２５の内部または外部の両方の切換用として油圧シリンダ１４２・１４３・１４４を利用することができ、油圧切換え構造のコンパクト化並びにメンテナンス性の向上などを行うと共に、作業変速用の油圧シリンダ１４２・１４３のピストン１６０・１６１をカウンタケース２５に内装させ、脱穀クラッチ９７用の油圧シリンダ１４４のピストンロッド１５５をカウンタケース２５に外装させるもので、カウンタケース２５の内外に設ける変速またはクラッチ等の切換え構造を、カウンタケース２５の一部である油路ベース１４５周りにコンパクトに配置することができ、切換え反力に対する油圧シリンダ１４２・１４３・１４４の支持剛性を油路ベース１４５の取付けにより容易に確保でき、組付け取外し性及びメンテナンス性の向上などを行うことができる。
【００３０】
また、脱穀クラッチ９７を形成するベルトクラッチのテンションアーム１５１に脱穀クラッチ９７用油圧シリンダ１４４のピストンロッド１５５を連結させるもので、前記油圧シリンダ１４４の容量を大きくすることによってベルトクラッチに必要なテンション力を充分に得ることができ、コンパクト化及びメンテナンス性の向上などを行うと共に、脱穀クラッチ９７用油圧シリンダ１４４を複動形にしてベルトクラッチの入と切の両方を油圧操作するもので、前記油圧シリンダ１４４の容量を大きくすることによってベルトクラッチに必要なテンション力を充分に得ることができ、コンパクト化及びメンテナンス性の向上などを行う。また、油圧チャージポンプ７８を利用して脱穀クラッチ９７用油圧シリンダ１４４を駆動するもので、チャージポンプ７８の油圧力と、油圧シリンダ１４４のピストン１５５径と、テンションアーム１５１比によりテンション力を容易に決定することができ、テンション調整を不要にしてメンテナンス性の向上させると共に、ベルト９８の最大伸び量よりも脱穀クラッチ９７用油圧シリンダ１４４のピストンロッド１５５ロークを大きくするもので、前記ベルト９８が伸びても、テンション調整をすることなく、適正なテンション力を容易に確保することができる。
【００３１】
さらに、図１５、図２７乃至図３２に示す如く、前記カウンタケース２５の上面に油路ベース１４５を着脱自在にボルト１５８止め固定させ、カウンタケース２５の上面開口１５９を閉塞すると共に、油路ベース１４５上面側に前記の各バルブ１４８・１４９・１５０を固定させ、油路ベース１４５の下面側に前記の各シリンダ１４２・１４３・１４４を固定させ、カウンタケース２５の外側に脱穀シリンダ１４４を設け、刈取変速シリンダ１４２と刈取定速シリンダ１４３をカウンタケース２５に内設させる。また、各シリンダ１４２・１４３対向する側面から各ピストンロッド１６０・１６１を互に反対の方向に突設させると共に、各シリンダ１４２・１４３の後側蓋を形成するアーム台１６２・１６３に変速アーム１６４及び定速アーム１６５一端側の各支点軸１６６・１６７を回転自在に下方側から差込んで軸支させ、各アーム１６４・１６５の他端側に各ピストンロッド１６０・１６１を連結させる。
【００３２】
また、前記カウンタケース２５内部で車速同調軸１１５と略平行にフォーク軸１６８を軸芯回りに回転自在に設け、刈取変速スライダ１１９を切換える変速フォーク１６９、並びに切換スライダ１２４を切換える定速フォーク１７０を、フォーク軸１６８に軸芯方向に摺動自在に設けると共に、前記各アーム１６４・１６５の中間に設ける各ピン１７１・１７２を各フォーク１６９・１７０に係合させ、各アーム１６４・１６５を各フォーク１６９・１７０に連結させ、前記各バルブ１４８・１４９制御により各シリンダ１４２・１４３のピストンロッド１６０・１６１を進出または退入させ、前記各アーム１６４・１６５を支点軸１６６・１６７回りに揺動させ、変速フォーク１６９を中立から高速または標準（低速）出力側に移動させる一方、定速フォーク１７０を中立から高速カットまたは流し込み回転出力側に移動させるように構成している。
【００３３】
また、図１４、図２９、図３０に示す如く、前記ピストンロッド１６０・１６１にピストンヘッド１７３を介して背圧ロッド１７４を固定させ、背圧ロッド１７４の外周にリング形退入ピストン１７５を設け、ピストンロッド１６０・１６１よりも大径でピストンヘッド１７３よりも小径に背圧ロッド１７４を形成し、退入ピストン１７５の外径をピストンヘッド１７３よりも大径に形成し、前記バルブ１４８・１４９が中立のとき、チャージポンプ７８のＡポート１７６圧油によって退入ピストン１７５をシリンダ１４２・１４３の段差１７７に当接させ、チャージポンプ７８のＢポート１７８圧油によってピストンヘッド１７３を退入ピストン１７５に当接させるもので、ピストンロッド１６０・１６１を油圧力によって中立位置に復動させて支持させる。そして、前記バルブ１４８・１４９を切換えたとき、Ｂポート１７８を前記バルブ１４８・１４９のタンク通路に開放することにより、Ａポート１７６圧油によって背圧ロッド１７４とヘッド１７３とピストンロッド１６０・１６１が進出する一方、Ａポート１７６を前記バルブ１４８・１４９のタンク通路に開放することにより、Ｂポート１７８圧油によってヘッド１７３と背圧ロッド１７４と退入ピストン１７５とピストンロッド１６０，・１６１が退入するもので、ピストンロッド１６０・１６１を介してアーム１６４・１６５が中立位置に加圧状態で復動して固定され、バネ等を設けることなくスライダ１１９・１２４を中立位置に復帰させて支持できる。また、前記シリンダ１４２・１４３の段差１７７に潤滑ポート１７９を開設させ、該ポート１７９をＡポート１７６またはＢポート１７８に連通させる。
【００３４】
上記から明らかなように、複動形の油圧刈取変速及び刈取定速シリンダ１４２・１４３のピストンロッド１６０・１６１及び退入ピストン１７５を二重構造にして両側に圧力をかけることにより中立に支持されるもので、３位置切換バルブ１４８・１４９の中立操作によりピストンロッド１６０・１６１及び退入ピストン１７５を油圧によって中立位置に保持でき、シリンダ１４２・１４３本体の一方にピストンロッド１６０・１６１を突出させる複動形のシリンダ１４２・１４３によって３ポジション切換を適正に行わせることができ、コンパクトで確実な切換え機構を構成でき、刈取変速機構１１６または定速機構１２１の一方または両方の切換え構造の簡略化並びに操作性の向上などを図る。
【００３５】
さらに、図３２に示す如く、前記フォーク１６９・１７０をデテントボール１８０によって中立位置に支持させると共に、フォーク軸１６８の軸芯方向と直交する方向に頂角を位置させる四角孔形の変速カム１８１を変速フォーク１６９のボス部に設け、フォーク軸１６８と変速カム１８１にピン１８２を貫挿させると共に、フォーク軸１６８に対して斜交させる長孔形の定速カム１８３を定速フォーク１７０のボス部に設け、フォーク軸１６８と定速カム１８３にピン１８４を貫挿させる。そして、変速フォーク１６９を刈取標準（低速）または高速側に切換えることにより、フォーク軸１６８の軸芯方向の変速カム１８１の頂角部にピン１８２が当接し、フォーク軸１６８の軸芯回りの回転を阻止し、定速フォーク１７０を中立位置に支持させる。一方、定速フォーク１７０を高速カットまたは流込回転側に切換えることにより、定速カム１８０によってピン１８４を押してフォーク軸１６８を軸芯回りに回転させ、フォーク軸１６８の軸芯と直交する方向の変速カム１８１の頂角部にピン１８２を当接させ、変速フォーク１６９の軸芯方向の移動を阻止し、変速フォーク１６９を中立位置に支持させる。このように、１本のフォーク軸１６８上に変速フォーク１６９と定速フォーク１７０を設け、変速カム１８１と定速カム１８３によって各フォーク１６９・１７０の動作を相互に規制し、同時切換によるギヤ１１７・１１８・１２２・１２３噛みなどの発生を防止している。
【００３６】
上記から明らかなように、刈取部７の駆動速度を変更する刈取変速機構１１６と、刈取部７を略定速で駆動する刈取定速機構１２１を備えるコンバインにおいて、刈取定速機構１２１が中立のときに刈取変速機構１１６の切換を可能にしたもので、前記の各機構１１６・１２１の異なる回転数の出力が同時に刈取部７に伝えられる不具合をなくすことができ、刈取定速機構１２１の定速出力を刈取変速機構１１６の出力に優先させて刈取部７に伝えることにより、刈取部７をスムーズに駆動でき、刈取部７の駆動トラブルの発生を低減させることができ、運転操作性を向上させると共に、刈取定速機構１２１の定回転操作具である定速フォーク１７０を中立以外に操作することにより、刈取変速機構１１６を中立にするもので、刈取定速機構１２１を中立以外の出力に切換えるとき、刈取変速機構１１６を中立に戻したり、中立であることを確認する等の手間を省くことができ、運転操作性を向上させる。
【００３７】
また、刈取変速機構１１６を切換える変速操作具である変速フォーク１６９と、定速機構１２１を切換える定速フォーク１７０を、同一の操作軸であるフォーク軸１６８に設けると共に、前記の各フォーク１６９・１７０の切換動作を相互に牽制する規制機構である変速カム１８１と定速カム１８３を設けるもので、同一のフォーク軸１６８を共用して前記の各フォーク１６９・１７０を設けるから、各フォーク１６９・１７０の組立及び調整を容易に行うことができ、かつ各フォーク１６９・１７０をカム１８１・１８３により容易に連結させることができ、変速操作構造の簡略化及びコンパクト化並びに変速操作性の向上などを図ると共に、変速及び定回転フォーク１６９・１７０を設けるカム軸１６８を回転自在に設け、フォーク軸１６８のピン１８２・１８４をフォーク１６９・１７０の貫通穴に挿入させてカム１８１・１８３を形成するもので、前記フォーク軸１６８を有効に利用してカム１８１・１８３を設けることができ、前記ピン１８２・１８４と貫通穴によってカム１８１・１８３を簡単な構造であり乍ら高機能に構成でき、変速操作構造の簡略化及びコンパクト化並びに変速操作性の向上などを図る。
【００３８】
さらに、図１７、図２０乃至図２２に示す如く、前記カウンタケース２５に形成する締結座１８５を機台３にボルト１８６止め固定させると共に、カウンタケース２５の機外側に分離ケース１８７を着脱自在にボルト１８８止め固定させ、カウンタケース２５の一部を分離ケース１８７によって形成し、分離ケース１８７の脱着によってカウンタケース２５の機外側面を開閉自在に形成するもので、カウンタケース２５と分離ケース１８７とに、前記各軸１０７・１１４・１１５・１２５・１３２を軸支させ、カウンタケース２５上面開口１５９に比べ、分離ケース１８７を外したときのケース２５機外側面の開口面積を大きくし、各軸１０７・１１４・１１５・１２５・１３２の脱着及びギヤ交換などを行えるように構成している。
【００３９】
上記から明らかなように、エンジン２１からの動力を、走行部である走行クローラ２と作業部である脱穀部４及び刈取部７に分配するカウンタケース２５を備える作業車において、カウンタケース２５の上面に開閉自在な開口部１５９を設けるもので、前記開口部１５９を開放させることにより、開口部１５９を介してカウンタケース２５内部のメンテナンスを行うことができ、取扱い性を向上させることができると共に、カウンタケース２５の一部を形成する分離ケース１８７を、カウンタケース２５の機外側部の蓋として取外し自在に設け、分離ケース１８７を取外したときのカウンタケース２５の機外側部の開口面積を上面の開口部１５９よりも大きく形成したもので、前記分離ケース１８７を取外すことにより、カウンタケース２５内部のギヤまたは軸などを交換したり損傷チェックを行うことができ、メンテナンス性を向上させることができる。
【００４０】
また、油圧シリンダ１４２・１４３・１４４及び油圧バルブ１４８・１４９・１５０を装備する油路ベース１４５によってカウンタケース２５上面の開口部１５９を開閉自在に閉塞するもので、油圧構成部品をユニット化してカウンタケース２５の蓋を兼用させるから、コンパクトに構成することができ、かつメンテナンス性を向上させることができると共に、刈取部７の支持部材２３・２４と分離ケース１８７を各別に構成すると共に、カウンタケース２５を本機に固定させ、カウンタケース２５に分離ケース１８７を固定させるもので、分離ケース１８７の取付けまたは取外し作業を容易に行うことができ、メンテナンス等の取扱い性を向上させることができる。
【００４１】
さらに、図３３に示す如く、作業レバー１８９の脱穀操作を検出する脱穀スイッチ１９０と、作業レバー１８９の刈取操作を検出する刈取スイッチ１９１と、刈取変速スライダ１１９の低速・高速の切換を行う刈取変速スイッチ１９２と、主変速レバー８１の高速前進及び後進の切換を検出する高速運転スイッチ１９３及び後進スイッチ１９４と、作業者の流し込みペダル１９５の足踏み操作を検出する手動流し込みスイッチ１９６と、低速・高速の副変速切換を行う副変速スイッチ１９７とを、マイクロコンピュータで構成する作業コントローラ１９８に接続させる。
【００４２】
また、エンジン２１の一定回転出力によって刈取部７を駆動する動作に手動で切換える直接駆動スイッチ１９９と、該スイッチ１９９の手動入力を入切する自動スイッチ２００と、左右の走行クローラ２の速度（車速）を検出する左及び右車速センサ２０１・２０２と、刈取部７の搬送穀稈の有無を検出する穀稈センサ２０３と、刈取部７に車速同調の駆動力を入力する同調入力軸１１２の入力回転数を低速ギヤ１１７を介して検出する刈取入力センサ２０４と、刈取変速シリンダ１４２を低速または高速に切換える刈取低速及び刈取高速ソレノイド２０５・２０６と、フィードチェンクラッチ１３１を切にするようにフィードチェンクラッチシリンダを作動させるフィードチェンソレノイド１９１と、一定回転シリンダ１４３により切換スライダ１２４を流し込みギヤ１２２に係合動作させる流し込みソレノイド２０８と、定速シリンダ１４３により切換スライダ１２４を高速カットギヤ１２３係合動作させる高速カットソレノイド２０９とを、作業コントローラ１９８に接続させ、図３４のフローチャートのように、刈取部７を、流し込み速度、または高速カット速度、または車速同調速度で作動させる。
【００４３】
また、前記の自動スイッチ２００がオンの状態下で高速運転スイッチ１９３がオンになったときに定速クラッチ７６を入にする高速運転ソレノイド２１１と、前記の副変速スイッチ１９７の切換によって副変速シリンダ８５を作動させて走行モータ３９を低速または高速出力にする副変速用低速及び高速ソレノイド２１２・２１３と、前記脱穀スイッチ１９０のオンによって脱穀クラッチ９７を入にする脱穀クラッチソレノイド２１４とを、作業コントローラ１９８に接続させる。
【００４４】
さらに、図３４のフローチャートに示す如く、作業レバー１８９の操作により脱穀スイッチ１９０がオンになると、フィードチェンソレノイド２０７をオフにしてフィードチェンクラッチ１３１を入にし、フィードチェン５の駆動を開始し、かつ脱穀クラッチソレノイド２１４を作動させて脱穀クラッチ９７を入にし、脱穀部４とフィードチェン５を駆動する。
【００４５】
また、作業レバー１８９の操作により刈取スイッチ１９１がオンになると、車速同調プーリ９３を介して主変速駆動力が刈取部７に伝達される。このとき、流し込みペダル１９５の足踏み操作が行われて流し込みスイッチ１９６がオンになると、刈取入力センサ２０４が検出する刈取部７の車速同調の入力回転数が流し込みギヤ１２２による回転設定以下のとき、刈取変速スライダ１１９を中立位置に移動させて刈取変速機構１１６の刈取変速出力を中立にして車速同調入力軸１２２の伝動をオフにし、かつ流し込みソレノイド２０８を作動させて流し込みギヤ１２２を介して刈取部７を高速カットギヤ１２３よりも低速で定速駆動する。
一方、流し込みスイッチ１９６がオンになったとき、刈取部７の車速同調の入力回転数が流し込みギヤ１２２による回転設定以上の場合、刈取変速機構１１６の刈取変速出力を中立にして同調入力軸１１２の伝動をオフにし、かつ高速カットソレノイド２０９の動作によって高速カットギヤ１２３を介して刈取部７を流し込みギヤ１２２よりも高速の最高回転で定速駆動する。
【００４６】
また、後進スイッチ１９４がオフのときで、車速センサ２０１・２０２によって検出する車軸５５が停止しているとき、刈取変速機構１１６を中立にして刈取部７の車速同調駆動を中止する。一方、車軸５５が駆動されていると、走行モータ３９の副変速出力が低速のときで、刈取入力センサ２０４が検出する刈取部７の車速同調の入力回転が高速カットギヤ１２３による回転設定以上のとき、高速カットソレノイド２０９を作動させ、刈取変速機構１１６を中立にし、高速カットギヤ１２３を介して刈取部７を最高速で定速駆動する高速カット動作を行わせる。
【００４７】
また、走行モータ３９の副変速出力が低速のときで、刈取部７の入力回転が設定以上のときで、自動スイッチ２００がオンのとき、直接駆動スイッチ１９９がオン操作されると、高速運転ソレノイド２１１を作動させて定速クラッチ７６を入にし、走行変速部材４０を介することなく、エンジン２１の駆動力を定速クラッチ７６から副変速機構４７に直接伝達させ、高速運転動作させる。
【００４８】
また、直接駆動スイッチ１９９がオフのとき、刈取変速スイッチ１９７の操作により、刈取変速機構１１６の刈取変速出力を低速または高速に切換え、各ギヤ１１７・１１８の一方を介して車速同調入力により刈取部７を低速または高速駆動し、起立している穀稈を低速で、または倒伏している穀稈を高速で刈取る。
【００４９】
さらに、図３５のフローチャートに示す如く、前記エンジン２１を作動させるキースイッチをオンにして作業コントローラ１９８に電源を印加させると、低速ソレノイド２１２がオンになって副変速バルブ８６作動させ、走行モータ３９の斜板８４を低速に切換える。そして、主変速レバー８１操作によって走行ポンプ３８の斜板７９角度を変更して走行させると共に、副変速スイッチ１９７を高速にすることにより、副変速バルブ８６が高速に切換わると共に、副変速スイッチ１９７を低速操作して副変速バルブ８６が低速に切換えられているとき、主変速レバー８１を走行ポンプ３８が最高速になるように操作することにより、走行ポンプ３８の容積効率が９０乃至９５パーセントになる最高速度付近で、主変速レバー８１によって高速運転スイッチ１９３がオンになり、主変速レバー８１の最高速度操作が検出されると、低速及び高速ソレノイド２１２・２１３を自動的にオフにして副変速バルブ８６を中立に維持させ、副変速シリンダ８５を油タンク側に短絡させて該シリンダ８５のピストンを自由に出入させ、走行ポンプ３８の吐出油圧がチャージポンプ７８油圧になるように、走行モータ３９の斜板８４をポンプ３８油圧によって中立側に戻すと共に、高速運転ソレノイド２１１を自動的にオンにして車速定速バルブ１４７を切換え、車速定速シリンダ１４６を作動させて定速クラッチ７６を入にし、走行変速部材４０を介することなく、エンジン２１の駆動力を定速クラッチ７６から副変速機構４７に直接伝達させ、左右の走行クローラ２を駆動させる。なお、前記シリンダ８５のピストンをフリーにしてバルブ１４７を切換えた後、前記シリンダ８５を低速側に固定してもよく、フリーにしてもよい。また、定速クラッチ７６を入にした後、約０．２秒経過してから、副変速バルブ８６を中立にし、走行モータ３９の斜板８４を遅延させてフリーにする。
【００５０】
また、図３６は走行ポンプ３８の斜板７９角度と油圧無段出力速度の関係を示すもので、走行ポンプ３８の斜板７９を最大に傾けた容積効率が１００パーセントのときの最高速度計算値に対し、斜板７９角度が最大のときの損失馬力（５乃至１０パーセント）が差し引かれて、実際に出力される速度実測値が低い速度になるが、定速クラッチ７６を介してポンプ軸７３とモータ軸４６をギヤ連結させるギヤ伝達比を、走行ポンプ３８の容積効率が１００パーセントの最高速度計算値の速度とモータ軸４６出力側の速度が略等しくなるように設定することにより、定速クラッチ７６を介して走行クローラ２が最高速度計算値の速度で駆動される。また、ポンプ軸７３とモータ軸４６を定速クラッチ７６を介して直結したとき、副変速バルブ８６が中立になって走行モータ３９の斜板８４角度が油圧によって自由に変化し、モータ軸４６の回転負荷を最も小さく保ち、走行変速部材４０の油圧損失馬力を有効に回収する。
【００５１】
上記から明らかなように、駆動速度を変更する油圧変速機構である走行変速部材４０と、略定速で駆動する定速機構である定速クラッチ７６を備える作業車において、走行変速部材４０の油圧走行モータ３９を出力可変構造とし、定速クラッチ７６の直結動作を行わせる前は低速側で油圧走行モータ３９の出力可変を固定させるもので、油圧走行モータ３９の出力を可変にすることによって走行変速部材４０の変速範囲を拡大させることが行えるが、走行変速部材４０の出力が不安定になり易い不具合がある。そこで、走行変速部材４０の出力によって走行クローラ２及び刈取部７の駆動を開始するとき、油圧走行モータ３９の出力を略一定にロックさせるから、油圧走行ポンプ３８だけの出力を可変して走行変速部材４０の安定した出力により走行クローラ２及び刈取部７の駆動を開始することができ、運転操作性及び取扱い性を向上させると共に、定速クラッチ７６の出力操作により油圧走行モータ３９の出力可変をフリーにするもので、油圧走行ポンプ３８の入力側と油圧走行モータ３９の出力側を直結させたとき、油圧走行モータ３９の出力調整をフリーにすることにより、油圧走行ポンプ３８側の吐出量に応じて主回路油圧が最低になるように油圧走行モータ３９が出力調整され、油圧走行ポンプ３８とモータ３９の各吐出量を容易に一致させることができ、主油圧回路油圧をチャージ圧にスムーズに低下させることができ、油圧変速機構の損失馬力を有効に回収することができる。
【００５２】
また、エンジン２１の動力を油圧無段変速出力に変換して走行部である走行クローラ２を駆動する油圧変速機構である走行変速部材４０と、該走行変速部材４０の入力側と出力側を直結させる定速機構である定速クラッチ７６を備える作業車において、走行変速部材４０の最高速度計算値になるように、前記定速クラッチ７６側の伝達比を設定する。そして、走行変速部材４０の容積効率が約１００パーセント（乃至数パーセント高め）の出力と略一致させるように定速クラッチ７６側のギヤ伝達比を設定することにより、例えば走行変速部材４０の容積効率が９０乃至９５パーセント以上のときに出力が不安定になって５乃至１０パーセントの出力損失が発生して油温が上昇する特性があっても、走行変速部材４０が最高速付近（例えば容積効率が９０〜９５パーセント）に増速されたとき、前記定速クラッチ７６の直結動作を行わせ、最高速度で運転するときの出力損失を低減させ、最高速付近から油圧変速の損失馬力分を速度アップして最高速度計算値の速度にスムーズに移行させ、安定した最高速度を安価な構造で提供でき、運転性能の向上などを図る。
【００５３】
また、出力可変構造の油圧走行ポンプ３８と、出力可変構造の油圧走行モータ３９とを、走行変速部材４０に備え、前記油圧走行モータ３９の出力可変をフリーにした後、定速クラッチ７６の直結動作を行わせてもよく、走行変速部材４０の出力から定速クラッチ７６の出力に切換えるときの速度差によるショックを低減させ、また定速クラッチ７６を介して出力させている状態下で、油圧走行モータ３９の作動油圧をチャージポンプ７８油圧に降下させ、空運転状態の走行変速部材４０の駆動負荷を低減させ、定速クラッチ７６による最高速度での運転性能の向上などを図る。
【００５４】
また、図９、図１２に示す如く、走行ポンプ３８のポンプ軸７３上に定速クラッチ７６を設けたが、ポンプ軸７３に代えて定速軸７７上に定速クラッチ７６を設けることも行えると共に、ロックアップ定速軸であるポンプ軸７３の一側に車速定速バルブ１４７を配置させ、定速クラッチ７６に組込む定速シリンダ１４６と前記バルブ１４７の間の油圧配管を不要にしている。また、定速クラッチ７６のギヤ連結部に多段変速用ギヤを組込み、定速クラッチ７６のロックアップ速度を多段に切換えることも行える。
【００５５】
【発明の効果】
以上実施例から明らかなように本発明は、請求項１の如く、最高速手前以下の速度で、油圧変速機構４０の油圧ポンプ３８の変速出力により、走行部２及び作業部７を駆動すると共に、最高速付近で油圧変速機構４０の入力側と出力側を定速機構７６により直結させる作業車において、油圧変速機構４０の油圧モータ３９を出力可変構造とし、定速機構７６の直結動作を行わせる前は低速側で油圧モータ３９の出力可変を固定させるもので、油圧モータ３９の出力を可変にすることによって油圧変速機構４０の変速範囲を拡大させることが行えるが、油圧変速機構４０の出力が不安定になり易い不具合がある。そこで、油圧変速機構４０の出力によって走行部２（及び作業部７）の駆動を開始するとき、油圧モータ３９の出力を低速側にロックさせるから、油圧ポンプ３８だけの出力を可変して油圧変速機構４０の安定した出力により走行部２（及び作業部７）の駆動を開始することができ、運転操作性及び取扱い性を向上させることができる。
【００５６】
また、請求項２の如く、定速機構７６の出力操作により油圧モータ３９の出力可変をフリーにするもので、油圧ポンプ３８の入力側と油圧モータ３９の出力側を直結させたとき、油圧モータ３９の出力調整をフリーにすることにより、油圧ポンプ３８側の吐出量に応じて主回路油圧が最低になるように油圧モータ３９が出力調整され、油圧ポンプ３８とモータ３９の各吐出量を容易に一致させることができ、主油圧回路油圧をチャージ圧にスムーズに低下させることができ、油圧変速機構の損失馬力を有効に回収することができる。
【図面の簡単な説明】
【図１】コンバインの斜視図。
【図２】同側面図。
【図３】同平面説明図。
【図４】前部機体の側面説明図。
【図５】同正面説明図。
【図６】駆動部の側面説明図。
【図７】同正面説明図。
【図８】同平面説明図。
【図９】同ミッションケースの駆動系統図。
【図１０】同平面図。
【図１１】同断面背面図。
【図１２】前図の拡大図。
【図１３】同拡大図。
【図１４】エンジン出力系統図。
【図１５】油圧回路図。
【図１６】カウンタケースの駆動系統図。
【図１７】同断面平面図。
【図１８】同拡大図。
【図１９】同断面側面図。
【図２０】同外観正面図。
【図２１】同平面図。
【図２２】同側面図。
【図２３】脱穀クラッチ部の平面図。
【図２４】同背面図。
【図２５】同部分図。
【図２６】脱穀シリンダ部の断面図。
【図２７】油路ベースの底面図。
【図２８】同断面側面図。
【図２９】刈取変速シリンダ部の断面図。
【図３０】刈取定速シリンダ部の断面図。
【図３１】フォーク軸部の断面背面図。
【図３２】同説明図。
【図３３】制御回路図。
【図３４】前図の収穫作業制御フローチャート。
【図３５】同車速制御フローチャート。
【図３６】走行ポンプ出力線図。
【符号の説明】
２　　　走行クローラ（走行部）
３８　　油圧走行ポンプ
３９　　油圧走行モータ
４０　　走行変速部材（油圧変速機構）
７６　　車速定速クラッチ（定速機構）[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a working vehicle such as a combine or tractor or a construction vehicle that moves with a pair of left and right traveling crawlers mounted thereon.
[0002]
[Problems to be solved by the invention]
Conventionally, as shown in Japanese Patent Application Laid-Open No. 62-163826, for example, in a combine or the like provided with left and right traveling crawlers, a traveling section (traveling crawler) is driven at the highest speed by a shift output of a hydraulic pump of a hydraulic speed change mechanism. Since the input side and the output side of the hydraulic transmission mechanism are directly connected by the constant speed mechanism at the maximum speed, there is a problem that the hydraulic transmission mechanism is operated by the output of the maximum speed of the hydraulic transmission mechanism that is unstable and has a large loss horsepower, Even if the output is switched to the output of the constant speed mechanism, there is a problem that the speed does not increase, and the driving performance cannot be easily improved. In addition, there is a problem that a shock is likely to occur due to a rotation difference (speed difference) before and after being directly connected by the constant speed mechanism, and when the traveling unit is driven by the constant speed output of the constant speed mechanism, for example, hydraulic transmission In the case of a hydraulic transmission mechanism having non-uniform characteristics, it is difficult to make the discharge amounts of the hydraulic pump and the motor equal to each other, and there are disadvantages such as an inability to effectively recover the lost horsepower and an increase in load.
[0003]
[Means for Solving the Problems]
Therefore, according to the present invention, the traveling unit is driven by the shift output of the hydraulic pump of the hydraulic transmission mechanism at a speed equal to or lower than the highest speed, and the input and output of the hydraulic transmission mechanism near the highest speed. In a work vehicle in which the side is directly connected by a constant speed mechanism, the hydraulic motor of the hydraulic transmission mechanism has a variable output structure, and before the direct connection operation of the constant speed mechanism is performed, the variable output of the hydraulic motor is fixed on the low speed side. By making the output of the motor variable, the shift range of the hydraulic transmission mechanism can be expanded, but the output of the hydraulic transmission mechanism tends to be unstable. Therefore, when the drive of the traveling unit (and the working unit) is started by the output of the hydraulic transmission mechanism, the output of the hydraulic motor is locked to the low speed side. Thus, the driving of the traveling unit (and the working unit) can be started, and the driving operability and handleability can be improved.
[0004]
In addition, the output of the hydraulic motor is made variable by the output operation of the constant speed mechanism, and when the input side of the hydraulic pump and the output side of the hydraulic motor are directly connected, the output of the hydraulic motor is adjusted. By setting it to free, the output of the hydraulic motor is adjusted so that the main circuit oil pressure is minimized according to the discharge amount on the hydraulic pump side, and the discharge amounts of the hydraulic pump and the motor can be easily matched, and the main hydraulic circuit oil pressure can be adjusted. Can be smoothly reduced to the charge pressure, and the horsepower loss of the hydraulic transmission mechanism can be effectively recovered.
[0005]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. 1 is an overall perspective view of the combine, FIG. 2 is a right side view thereof, and FIG. 3 is an explanatory plan view. In FIG. 1, reference numeral 1 denotes a pair of left and right track frames on which a pair of left and right traveling crawlers 2 are mounted. And 4 is a threshing unit which is a threshing machine which stretches a feed chain 5 on the left side and has a built-in handling cylinder 6 and a processing cylinder. Reference numeral 7 denotes a raising mechanism 8 and a cutting blade 9. A mowing unit including a grain culm transport mechanism 10 and the like, 11 is a hydraulic lifting cylinder that raises and lowers the mowing unit 7 via a mowing frame 12, 13 is a straw processing unit that faces the end of a straw chain 14, and 15 is a threshing unit 4. A grain tank for carrying the grains of the tank 15 through a fryer, 16 and 17 a discharge auger for carrying the grains of the tank 15 out of the machine, 18 a driving cabin provided with a driving handle 19 and a driving seat 20, 21 Is installed below the driving cabin 18. That an engine is configured to threshing continuously harvests culms.
[0006]
Further, as shown in FIGS. 4 to 8, a transmission case 22 is disposed between the left and right traveling crawlers 2 in front of the machine base 3, and the transmission case 22 and the engine 21 are provided in front and back substantially in series. In addition to transmitting the driving force of the engine 21 to the traveling crawler 2 via the thruster 4, the left and right support stands 23 and 24 are erected on the upper surface of the machine 3 in front of the threshing unit 4, and the support stands 23 and 24 are harvested via the cutting frame 12. The part 7 is provided so as to be able to move up and down and to move laterally. A counter case 25 is provided on the upper surface of the machine base 3 on the rear side of the support bases 23 and 24, and the driving force of the engine 21 is transmitted to the threshing unit 4 and the cutting unit 7 via the counter case 25.
[0007]
Further, the cabin front frame 26 is erected on the machine base 3 on the side of the transmission case 22, and the front portion of the step frame 27 of the cabin 18 is provided above the front frame 26 via the rotation fulcrum shaft 28. The cabin 18 is rotatably supported in the front, and the left support frame 29 is erected on the right support stand 24, and the gantry 3 between the right cabin frame 30 is erected on the machine 3. The engine 21 is provided on the upper surface, and the engine 21 is covered with the engine room cover 31. Further, the upper portions of the left and right rear frames 29 and 30 are connected to each other above the cover 31 by a cabin horizontal frame 32, a hook lever 33 is provided on the cabin horizontal frame 32, and the rear portion of the step frame 27 of the cabin 18 is mounted on the horizontal frame 32. And fixed by a hook lever 33 so as to be freely detachable, a horizontal connection frame 34 is fixed between the right support base 24 and the front frame 26, and an inclined connection frame 35 is fixed between the horizontal connection frame 34 and the horizontal frame 32. Then, the frame rigidity is secured by the connection frames 34 and 35. Further, an auger support 36 is connected to the left rear frame 29, and an auger rest 37 is provided on the upper side, and the discharge auger 17 provided to be able to move up and down and pivot is supported at the main body storage position of the auger rest 37.
[0008]
Further, as shown in FIGS. 9 to 14, the transmission case 22 for driving the traveling crawler 2 includes a pair of hydraulic traveling pumps 38 and a hydraulic traveling motor 39 to provide a hydraulic continuously variable transmission mechanism for traveling main transmission. And a turning member 43 that forms a hydraulic stepless transmission mechanism for turning by providing a pair of a hydraulic turning pump 41 and a hydraulic turning motor 42, and the output shaft 44 of the engine 21. The pumps 38 and 41 are connected to each other via an input shaft 45 of the transmission case 22 to drive the pumps 38 and 41.
[0009]
The drive shaft 49 of the traveling motor 39 is connected to the driving wheels 49 of the left and right traveling crawlers 2 via a subtransmission mechanism 47 and a differential mechanism 48 in an interlocking manner. Each planetary gear mechanism 50 includes one sun gear 51, three planetary gears 52 meshing on the outer periphery of the sun gear 51, and a ring gear 53 meshing with the planetary gears 52. .
[0010]
The planetary gear 52 is rotatably supported by a free shaft 54 of a sun gear 51 and a carrier 56 of an axle 55 on the same axis as the carrier, so that the left and right carriers 56 are opposed to each other with the left and right sun gears 51 interposed therebetween. Has internal teeth meshing with each planetary gear 52 and is rotatably supported on an axle 55. The axle 55 is extended and the drive wheel 49 is axially supported.
[0011]
The traveling speed change member 40 controls the forward / reverse rotation and the rotation speed of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. The traveling speed change member 40 controls the rotation of the traveling motor 39 by the motor shaft 46 and the auxiliary transmission mechanism 47. Are transmitted to the left and right ring gears 53 via the low and high speed gears 57 and 58, the brake shaft 59 and the branch shaft 60 to rotate the left and right carriers 56. A parking brake 61 is provided on the brake shaft 59, and a mowing drive pulley 62 for transmitting torque to the mowing unit 7 is provided on the motor shaft 46, and the mowing unit 7 is driven at a vehicle speed tuning speed.
[0012]
As described above, the driving force of the traveling motor 39 transmitted to the ring gear 53 via the branch shaft 60 is transmitted to the left and right carriers 56 via the left and right planetary gear mechanisms 50 and the rotation transmitted to the left and right carriers 56. To the left and right drive wheels 49 to drive the left and right traveling crawlers 2 in the same direction at the same speed.
[0013]
Further, a turning member 43 formed by a hydraulic stepless speed change mechanism for turning controls the forward / reverse rotation of the turning motor 42 and the rotation speed by changing the swash plate angle of the turning pump 41, and controls the steering output brake. 63, a clutch shaft 66 for providing a steering output clutch 65, and left and right input gears 67 and 68 which are always meshed with the left and right sun gears 51. A clutch shaft 66 is connected via a steering output clutch 65, and left and right input gears 67 and 68 are connected to the clutch shaft 66 via a forward rotation gear 69 and a reverse rotation gear 70. When the rotational force of the motor 42 is transmitted to the right sun gear 51 via the forward rotation gear 69, and the rotation of the motor 42 is transmitted to the left sun gear 51 via the reverse rotation gear 70, the rotation motor 42 rotates forward (reverse rotation). The left sun gear 51 is rotated in the reverse direction (forward rotation) and the right sun gear 51 is rotated in the forward direction (reverse rotation) at the same left and right rotation speeds, and the left and right traveling crawlers 2 are driven in the opposite directions at the same speed.
[0014]
Thus, when the traveling motor 39 is driven in a state in which the turning motor 42 is stopped and the left and right sun gears 51 are stationary, the rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 at the same speed, and the left and right planetary gears are rotated. The right and left traveling crawlers 2 are driven at the same rotational speed in the same rotational direction on the left and right via the carrier 56 of the mechanism 50, and the body travels straight in the front-rear direction. On the other hand, when the traveling motor 39 is stopped and the left and right ring gears 53 are stationary and the swing motor 42 is driven forward and reverse, the left planetary gear mechanism 50 rotates forward or reverse, and the right planetary gear mechanism 50 Rotates in the reverse or forward direction, drives the left and right traveling crawlers 2 in the reverse direction, and turns the machine body to the left or right. Further, by driving the turning motor 42 while driving the traveling motor 39, the body turns left and right to correct the course, and the turning radius of the body is determined by the output rotation speed of the turning motor 42. .
[0015]
Further, a fan shaft 71 is connected to the input shaft 45, and a cooling fan 72 of a radiator for water cooling of the engine 21 is driven by the fan shaft 71, and the pump shafts 73 and 74 of the traveling and swirling pumps 38 and 41 are connected to the pump shafts 73 and 74. The fan shaft 71 is connected via a gear group 75, the input shaft 45 is connected to each of the pumps 38 and 41, and the pump shaft 73 of the traveling pump 38 and the motor shaft 46 of the traveling motor 39 are connected to a constant speed clutch 76. Is provided, and when the constant speed clutch 76 is engaged, the pump shaft 73 and the motor shaft 46 are gear-connected via the constant speed shaft 77, without passing through the traveling speed change member 40, The rotation of the input shaft 45 is transmitted to the auxiliary transmission mechanism 47, and the right and left traveling crawlers 2 are driven by the constant speed rotation of the engine 21. I make. Note that a charge pump 78 is provided on the swivel pump shaft 74 and driven.
[0016]
Further, as shown in FIG. 15, a main transmission cylinder 80 for adjusting the output by changing the angle of the swash plate 79 of the traveling pump 38, a transmission valve 82 connected to the main transmission lever 81 and the steering handle 19 for switching, and a traveling pump. A valve 83 for decelerating the output 38 by a fixed amount is provided, and the charge pump 78 is hydraulically connected to the main transmission cylinder 80 via the valves 82 and 83. The main transmission lever 81 switches the transmission valve 82, and the main transmission cylinder 80 to change the angle of the swash plate 79 of the traveling pump 38 to change the rotation speed of the motor shaft 46 of the traveling motor 39 in a stepless manner or to perform a traveling speed change operation of reverse rotation. The swash plate 7 is adjusted in proportion to the amount of operation of the main shift lever 81 by performing a feedback operation in which the shift valve 82 returns to neutral by the angle adjustment operation. The angle is varied, by varying the rotation speed of the traveling motor 39 to change the vehicle speed.
[0017]
Further, an auxiliary transmission cylinder 85 for adjusting the output by changing the angle of the swash plate 84 of the traveling motor 39 is provided, and the auxiliary transmission cylinder 85 is hydraulically connected to the charge pump 78 via an electromagnetic auxiliary transmission valve 86. Is neutral, the sub transmission cylinder 85 is short-circuited to the transmission case 22 as an oil tank, the swash plate 84 angle of the traveling motor 39 is changed by the main circuit oil pressure, and the swash plate 84 angle is changed by switching the sub transmission valve 86. The output is forcibly changed to change the output of the traveling motor 39 to high speed or low speed.
[0018]
Further, a swing cylinder 88 for adjusting the output by changing the angle of the swash plate 87 of the swing pump 41 is provided. The swing cylinder 89 is connected to the steering handle 19 and the main shift lever 81 for switching, and a solenoid automatic steering valve 90 is provided. The charge pump 78 is hydraulically connected to the swivel cylinder 88, the swivel valve 89 is switched by the steering handle 19, and the swivel cylinder 88 is operated to change the angle of the swash plate 87 of the swivel pump 41. A left-right turning operation for continuously changing or reversing the rotation speed is performed, and a feedback operation for returning the turning valve 89 to neutral by the angle adjusting operation of the swash plate 87 is performed. The angle of the swash plate 87 is changed proportionally, and the rotation speed of the turning motor 42 is changed to change the left-right turning angle.
[0019]
When the main shift lever 81 is operated to a position other than the neutral position and the steering handle 19 is operated to a position other than the straight traveling, the hydraulic output of the traveling pump 38 is adjusted in proportion to the operation direction and the operation amount of the main shift lever 81. In addition to changing the forward / backward speed or the speed of the hydraulic motor 39 to change the forward / backward speed (vehicle speed), the output of the swing pump 41 is changed in proportion to the operation amount of the main shift lever 81. The turning radius is automatically reduced, and the turning radius is automatically increased by the low speed running speed change. The turning radius of the left and right running crawlers 2 is maintained substantially constant by the constant operation of the steering wheel 19 regardless of the running speed. Then, the work traveling speed is changed, and the course is adjusted so that the aircraft follows the uncut culm row. On the other hand, when the turning radius (steering angle) is reduced (increased) by changing the output of the turning pump 41 and the output of the traveling pump 38 by controlling the valves 82 and 89 in proportion to the operation amount of the steering handle 19, the traveling speed is reduced. (Vehicle speed) is reduced in proportion to the speed difference between the left and right traveling crawlers 2 and the vehicle is turned left and right. The driving speed of the left and right traveling crawlers 2 is changed to correct the alignment path and to make a headland. The direction change by the spin turn in, and the harvesting work of cutting and threshing the stalk continuously. When the main shift lever 81 is neutral, the turning valve 89 is maintained neutral regardless of the operation of the steering handle 19, the hydraulic output of the turning pump 41 is maintained at substantially zero, and the turning motor 42 is stopped.
[0020]
Further, as shown in FIG. 14 to FIG. 22, the output shaft 44 of the engine 21 is protrudingly provided on the front side and the rear side, the input shaft 45 is connected to the front side of the output shaft 44, and the operation is performed on the rear side of the output shaft 44. An output pulley 91 is provided, and a counter case 25 is provided on the upper surface of the machine base 3 in front of the threshing unit 4 on the left side of the engine 21, and an input pulley 92, a vehicle speed tuning pulley 93, a threshing pulley 94, a cutting pulley 95, and a sorting pulley 96 are countered. The input pulley 92 on the rear side of the case 25 is connected to the work output pulley 91 via a tension threshing clutch 97 via a belt 98, and the driving force of the engine 21 is transmitted to the counter case 25. Also, the vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected to the mowing drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support stand 24 with the belt 100, and is erected on the front upper surface of the machine base 3. The cutting input case 101 is rotatably supported on the support bases 23 and 24, the cutting frame 12 is connected to the case 101, and the cutting unit 7 is rotated around the case 101 to move up and down. The cutting input pulley 103 is pivotally supported via the cutting input shaft 102, and the cutting pulley 95 on the left side of the counter case 25 is connected to the cutting input pulley 103 by the belt 104, and the driving force is transmitted to each section of the cutting section 7.
[0021]
A threshing pulley 94 on the front side of the counter case 25 is connected to a belt 106 to a drive input pulley 105 of the handling cylinder 6, and a driving force is transmitted from a sorting pulley 96 to a sorting machine and a swing sorting mechanism below the handling cylinder 6 to thresh. A feed chain input shaft 107 is provided on the left side surface of the counter case 25, and power is transmitted from the input shaft 107 to a drive sprocket 108 of the feed chain 5 which can move outward. Further, a discharge drive pulley 109 is provided in front of the grain tank 15, and the pulley 109 is connected to the work output pulley 91 by a belt via a discharge clutch 110, and the output of the engine 21 is transmitted to the discharge auger 17 to transmit the grain of the tank 15. Let the grains drain.
[0022]
Further, the handle case input shaft 111 is pivotally supported on the counter case 25, the shaft 111 is extended in the front-rear direction, and a threshing pulley 94 is provided on the front side of the shaft 111 outside the front surface of the counter case 25. An input pulley 92 is provided on the rear side of the outer shaft 111, and a constant rotational power of the engine 21 is input to the handle input shaft 111 to rotate the engine 21 at a constant speed. A tuning input shaft 112 is supported on the right side of the counter case 25, and a vehicle speed tuning pulley 93 is provided on the right side of the shaft 112 on the right outside of the counter case 25, and a belt is provided between the pulleys 62 and 93 via an idle pulley 99. 100 is tensed, and vehicle speed tuning power is input from the transmission case 22 to the counter case 25.
[0023]
Further, a constant speed shaft 114, which is a counter shaft or a sorting input shaft for connecting the right side of the handle cylinder input shaft 111 to the bevel gear 113, and a vehicle speed tuning shaft 115 provided substantially in front of the shaft 114, are mounted on the counter case 25. A low-speed gear 117 and a high-speed gear 118, which are supported by a shaft and form a cutting speed change mechanism 116, are provided between the shafts 114 and 115. 117 and 118 are selectively engaged with the vehicle speed tuning shaft 115 to perform the reaping shift. Further, a one-way clutch 120 for transmitting the vehicle speed tuning rotational force of the tuning input shaft 112 to the gears 117 and 118 is provided on the tuning input shaft 112, and the power from the vehicle speed tuning pulley 93 is transmitted by the one-way clutch 120. -The vehicle speed tuning shaft 115 is configured to be rotated via 118.
[0024]
Further, a pouring gear 122 and a high-speed cut gear 123 forming a constant mowing speed mechanism 121 are provided between the shafts 114 and 115, and the switching sliders 124 for pouring driving or high-speed cutting driving of the cutting unit 7 are used to control the shafts 114 and 115. The gears 122 and 123 are selectively engaged with each other, and the mowing unit 7 is poured and driven so that the culm of the mowing unit 7 is conveyed to the feed chain 5 irrespective of the running state. The cutting unit 7 drives the cutting unit 7 at a constant rotation speed faster than the maximum speed of the vehicle speed synchronization to cut the lodging culm.
[0025]
Further, the left end of the constant speed shaft 114 is projected to the lower rear side on the left side of the counter case 25, and the selection pulley 96 is pivotally supported at the left end of the shaft 114. Further, a mowing transmission shaft 125 is axially supported on the lower front side on the left side of the counter case 25, and the right side of the shaft 125 is connected to a vehicle speed tuning shaft 115 via a torque limiter 126 so that the shaft 125 protrudes to the left side of the counter case 25. The cutting support shaft 95 is supported at the left end, the cutting drive shaft 127 is connected to the gear 128 by the cutting drive shaft 102, and the cutting input pulley 103 is supported by the cutting drive shaft 127. A case of a gear 128 is rotatably provided around the longitudinal axis on the base 23 via a fulcrum shaft 129, the left side of the cutting input case 101 is fixed to the case of the gear 128, and the gear 128 is provided in each case 101, A cutting power is input from the left end side of the cutting input shaft 102, and a cutting power transmission shaft 130 inserted into the cutting frame 12 on the right end side of the case 101. While causing the driving of the reaper 7, the reaper 7 substantially horizontally to the fuselage left pivot shaft 129 around rotated move, the maintenance of each case 22, 25 near the inboard like.
[0026]
Further, the feed chain input shaft 107 is supported on the upper left side of the counter case 25, and the input shaft 107 is connected to a feed chain drive shaft 132 provided with a feed chain clutch 131 by a chain 133. Is provided by a feed chain transmission mechanism 134 for transmitting the gears by changing the rotation speed of the vehicle speed tuning shaft 115, and the mechanism 134 is formed to be continuously variable by a planetary gear mechanism 138 including a sun gear 135, a planetary gear 136, and a ring gear 137. A sun gear 135 is engaged with the constant speed shaft 114, and a ring gear 137 that idles and supports the constant speed shaft 114 is connected to the vehicle speed tuning shaft 115 with a gear 139, and a bearing body 140 that idles and supports the planetary gear 136 is fixed. The idler is supported by the speed shaft 114, A gear 141 is connected to the feed chain drive shaft 132 through a clutch 131 to form a gear 141, and the feed chain 5 speed is changed from a constant low speed to a high speed while maintaining the minimum rotation required for conveying the grain. It is configured to be synchronized and changeable.
[0027]
A hydraulic cutting speed change cylinder 142 for operating the cutting speed change slider 119, a hydraulic cutting constant speed cylinder 143 for operating the switching slider 124, and a hydraulic threshing cylinder 144 for turning on the threshing clutch 97 are mounted on the top cover of the counter case 25. A constant-speed valve 147 for actuating a constant-speed cylinder 146 for engaging the constant-speed clutch 76, a constant-speed valve 147 for operating the partial-cutting cylinder 142, and A constant harvesting speed valve 149 for operating the speed cylinder 143 and a threshing valve 150 for operating the threshing cylinder 144 are hydraulically connected to the charge pump 78 in parallel.
[0028]
Further, as shown in FIG. 15 and FIGS. 23 to 28, the threshing clutch 97 is pivotally supported by a tension arm 151, and the tension arm 151 is rotatably supported by a support shaft 152 of the counter case 25 to be freely bent. The piston rod 155 of the threshing cylinder 144 is connected to the tension arm 151 via the two links 153 and 154, and the thrusting clutch 97 is engaged by the pushing (extending) operation of the piston rod 155 to tension the belt 98. The thrusting clutch 97 is disengaged by the pulling (retreating) operation of the piston rod 155 to loosen the belt 98. Further, a spring 156 for elastically pressing the threshing clutch 97 to the disengagement side is connected to the link 154, and a throttle valve 157 is provided on the return side of the oil passage on the piston rod 155 advancing side of the double-acting threshing cylinder 144. Is advanced at a low speed to turn on the threshing clutch 97, while the piston rod 155 is retracted at a high speed to turn off the threshing clutch 97.
[0029]
As is apparent from the above description, in a work vehicle provided with a counter case 25 which is a transmission case for distributing power from the engine 21 to the traveling crawler 2 which is a traveling unit and the threshing unit 4 and the reaping unit 7 which are working units. An oil passage base 145 that forms a part of the case 25 is provided with a threshing clutch 97 as a work clutch or a plurality of hydraulic cylinders 142, 143, and 144 for a work shift, both inside and outside the counter case 25. Hydraulic cylinders 142, 143, 144 can be used for switching, so that the hydraulic switching structure can be made compact and maintenance performance can be improved, and the pistons 160, 161 of the hydraulic cylinders 142, 143 for work shifting can be replaced by a counter case. 25, and a piston cylinder of a hydraulic cylinder 144 for the threshing clutch 97. The gear 155 is externally provided on the counter case 25, and a switching structure such as a speed change or clutch provided inside and outside the counter case 25 can be compactly arranged around the oil passage base 145 which is a part of the counter case 25, The support rigidity of the hydraulic cylinders 142, 143, 144 against the switching reaction force can be easily secured by attaching the oil passage base 145, and the assembling / removing property and the maintenance property can be improved.
[0030]
Further, the piston rod 155 of the hydraulic cylinder 144 for the threshing clutch 97 is connected to the tension arm 151 of the belt clutch forming the threshing clutch 97. By increasing the capacity of the hydraulic cylinder 144, the tension force required for the belt clutch is increased. The hydraulic cylinder 144 for the threshing clutch 97 is made double-acting to hydraulically operate both the engagement and disengagement of the belt clutch. By increasing the capacity of the cylinder 144, a sufficient tension force for the belt clutch can be obtained, and the compactness and the maintenance can be improved. Further, the hydraulic cylinder 144 for the threshing clutch 97 is driven by using the hydraulic charge pump 78, and the tension force can be easily adjusted by the hydraulic pressure of the charge pump 78, the diameter of the piston 155 of the hydraulic cylinder 144, and the ratio of the tension arm 151. The tension adjustment is not required, the maintenance is improved, and the piston rod 155 of the hydraulic cylinder 144 for the threshing clutch 97 is made larger than the maximum extension of the belt 98. However, appropriate tension force can be easily secured without adjusting the tension.
[0031]
Further, as shown in FIGS. 15 and 27 to 32, an oil passage base 145 is detachably fixed to an upper surface of the counter case 25 by bolts 158 to close an upper surface opening 159 of the counter case 25 and to close the oil passage base. The above valves 148, 149, 150 are fixed to the upper surface side of 145, the respective cylinders 142, 143, 144 are fixed to the lower surface side of the oil passage base 145, and the threshing cylinder 144 is provided outside the counter case 25, The mowing transmission cylinder 142 and the mowing constant speed cylinder 143 are provided inside the counter case 25. In addition, the piston rods 160 and 161 project from opposite sides of the cylinders 142 and 143 in directions opposite to each other, and the speed change arms 164 are attached to arm stands 162 and 163 forming rear lids of the cylinders 142 and 143. The fulcrum shafts 166 and 167 at one end of the constant-speed arm 165 are rotatably inserted from below and axially supported, and the piston rods 160 and 161 are connected to the other ends of the arms 164 and 165.
[0032]
A fork shaft 168 is provided in the counter case 25 so as to be rotatable about the axis substantially in parallel with the vehicle speed tuning shaft 115, and a speed change fork 169 for switching the cutting speed change slider 119 and a constant speed fork 170 for switching the change slider 124 are provided. The fork shaft 168 is slidably provided in the axial direction, and the pins 171 and 172 provided between the arms 164 and 165 are engaged with the forks 169 and 170, respectively. 169 and 170, the piston rods 160 and 161 of the cylinders 142 and 143 are advanced or retracted by the control of the valves 148 and 149, and the arms 164 and 165 are swung around the fulcrum shafts 166 and 167. To move the shifting fork 169 from neutral to a high-speed or standard (low-speed) output side Write, and configured to move the constant speed fork 170 from the neutral fast cut or cast into a rotary output side.
[0033]
As shown in FIGS. 14, 29, and 30, a back pressure rod 174 is fixed to the piston rods 160 and 161 via a piston head 173, and a ring-shaped retraction piston 175 is provided on the outer periphery of the back pressure rod 174. The back pressure rod 174 is formed larger in diameter than the piston rods 160 and 161 and smaller than the piston head 173, and the outer diameter of the retreating piston 175 is formed larger in diameter than the piston head 173. Is neutral, the reciprocating piston 175 is brought into contact with the step 177 of the cylinders 142 and 143 by the A port 176 pressure oil of the charge pump 78, and the piston head 173 is retreated by the B port 178 pressure oil of the charge pump 78. The piston rods 160 and 161 return to the neutral position by hydraulic pressure To be supported. When the valves 148 and 149 are switched, the B port 178 is opened to the tank passage of the valves 148 and 149, so that the back pressure rod 174, the head 173, and the piston rods 160 and 161 are compressed by the A port 176 pressure oil. On the other hand, by opening the A port 176 to the tank passage of the valves 148 and 149, the head 173, the back pressure rod 174, the retreat piston 175, and the piston rods 160 and 161 retreat by the B port 178 pressure oil. The arms 164 and 165 are moved back and fixed to the neutral position in a pressurized state via the piston rods 160 and 161 and can return and support the sliders 119 and 124 to the neutral position without providing a spring or the like. . In addition, a lubrication port 179 is opened at the step 177 of the cylinders 142 and 143, and the port 179 is connected to the A port 176 or the B port 178.
[0034]
As is apparent from the above, the piston rods 160 and 161 of the double-acting type hydraulic mowing shift and mowing constant speed cylinders 142 and 143 and the retreating piston 175 have a double structure and are neutrally supported by applying pressure to both sides. The piston rods 160 and 161 and the retreating piston 175 can be held at the neutral position by hydraulic pressure by the neutral operation of the three-position switching valves 148 and 149, and the piston rods 160 and 161 protrude from one of the cylinders 142 and 143 main body. The double-acting cylinders 142 and 143 can properly switch between the three positions, and a compact and reliable switching mechanism can be formed. The switching structure of one or both of the cutting speed change mechanism 116 and the constant speed mechanism 121 can be simplified. In addition, the operability is improved.
[0035]
Further, as shown in FIG. 32, the fork 169/170 is supported at a neutral position by a detent ball 180, and a quadrangular transmission cam 181 is positioned at the apex angle in a direction perpendicular to the axial direction of the fork shaft 168. The pin 182 is inserted into the boss portion of the speed change fork 169, and the pin 182 is inserted through the fork shaft 168 and the speed change cam 181, and the oblong constant speed cam 183 obliquely intersected with the fork shaft 168 is provided on the boss portion of the speed change fork 170. The pin 184 is inserted through the fork shaft 168 and the constant speed cam 183. When the speed change fork 169 is switched to the standard (low speed) or high speed side of the mowing, the pin 182 comes into contact with the apex portion of the speed change cam 181 in the axial direction of the fork shaft 168, and the fork shaft 168 rotates around the axis. And the constant speed fork 170 is supported at the neutral position. On the other hand, by switching the constant-speed fork 170 to the high-speed cutting or pouring rotation side, the pin 184 is pushed by the constant-speed cam 180 to rotate the fork shaft 168 around the axis, and the fork shaft 168 is rotated in a direction orthogonal to the axis. The pin 182 is brought into contact with the vertex of the speed change cam 181 to prevent the speed change fork 169 from moving in the axial direction, thereby supporting the speed change fork 169 at the neutral position. As described above, the speed change fork 169 and the constant speed fork 170 are provided on one fork shaft 168, and the operations of the forks 169 and 170 are mutually restricted by the speed change cam 181 and the constant speed cam 183, and the gear 117 is simultaneously switched. -The occurrence of bites of 118, 122 and 123 is prevented.
[0036]
As is apparent from the above, in the combine including the mowing transmission mechanism 116 for changing the driving speed of the mowing unit 7 and the mowing constant speed mechanism 121 for driving the mowing unit 7 at a substantially constant speed, the mowing constant speed mechanism 121 is neutral. Sometimes, the switching of the reaping speed change mechanism 116 is enabled, and it is possible to eliminate the problem that the outputs of the different rotation speeds of the respective mechanisms 116 and 121 are simultaneously transmitted to the reaping unit 7. By transmitting the speed output to the reaping unit 7 with priority given to the output of the reaping transmission mechanism 116, the reaping unit 7 can be driven smoothly, the occurrence of drive troubles of the reaping unit 7 can be reduced, and driving operability is improved. By operating the constant speed fork 170, which is a constant rotation operating tool of the constant mowing speed mechanism 121, to a position other than neutral, the mowing transmission mechanism 116 is neutralized. When switching the output of the non-neutral 21, or return the cutting speed change mechanism 116 in a neutral, it can save the trouble of such as to ensure a neutral, improving the driving operability.
[0037]
Further, a speed change fork 169 as a speed change operation tool for switching the reaping speed change mechanism 116 and a constant speed fork 170 for switching the constant speed mechanism 121 are provided on a fork shaft 168 as the same operation shaft. Are provided with a speed change cam 181 and a constant speed cam 183, which are regulating mechanisms for mutually restraining the switching operation. The forks 169 and 170 are provided by sharing the same fork shaft 168. Can be easily assembled and adjusted, and the forks 169 and 170 can be easily connected by the cams 181 and 183, so that the speed change operation structure can be simplified and downsized, and the speed change operability can be improved. In addition, a camshaft 168 provided with a speed change and constant rotation forks 169 and 170 is rotatably provided, and the fork shaft 1 The cams 181 and 183 are formed by inserting the pins 182 and 184 into the through holes of the forks 169 and 170, and the cams 181 and 183 can be provided by effectively using the fork shaft 168. The cams 181 and 183 can be configured to have a high function with a simple structure by using the 182 and 184 and the through holes, and the speed change operation structure can be simplified and downsized, and the speed change operability can be improved.
[0038]
Further, as shown in FIGS. 17 and 20 to 22, a fastening seat 185 formed in the counter case 25 is fixedly fastened to the machine base 3 with a bolt 186, and a separation case 187 is detachably attached to the outside of the counter case 25. Bolts 188 are fixed and fixed, a part of the counter case 25 is formed by the separation case 187, and the outer surface of the counter case 25 is formed to be openable and closable by attaching and detaching the separation case 187. Each of the shafts 107, 114, 115, 125, and 132 is pivotally supported, and the opening area of the outer surface of the case 25 when the separation case 187 is removed is increased as compared with the opening 159 of the upper surface of the counter case 25. It is configured so that the attachment / detachment of 107/114/115/125/132 and the gear exchange can be performed.
[0039]
As is apparent from the above, in the work vehicle including the counter case 25 that distributes the power from the engine 21 to the traveling crawler 2 as the traveling unit and the threshing unit 4 and the reaping unit 7 as the working unit, Is provided with an opening 159 that can be opened and closed. By opening the opening 159, maintenance inside the counter case 25 can be performed through the opening 159, and handling can be improved. A separation case 187 forming a part of the counter case 25 is detachably provided as a lid on the outer side of the counter case 25, and the opening area of the outer side of the counter case 25 when the separation case 187 is removed is set to the upper surface. It is formed larger than the opening 159, and by removing the separation case 187, the counter case 25 Such gear or the shaft parts can be exchanged or damage check, it is possible to improve the maintainability.
[0040]
An opening 159 on the upper surface of the counter case 25 is opened and closed by an oil passage base 145 equipped with hydraulic cylinders 142, 143, 144 and hydraulic valves 148, 149, 150. Since the lid of the case 25 is also used, the cover can be made compact and the maintainability can be improved. In addition, the support members 23 and 24 of the reaper 7 and the separation case 187 are separately formed, and the counter case is provided. The fixing case 25 is fixed to the main unit, and the separating case 187 is fixed to the counter case 25. Therefore, the work of attaching or detaching the separating case 187 can be easily performed, and the handling property such as maintenance can be improved.
[0041]
Further, as shown in FIG. 33, a threshing switch 190 for detecting a threshing operation of the work lever 189, a reaper switch 191 for detecting a reaping operation of the work lever 189, and a reaper shift for switching the reaper speed change slider 119 between low speed and high speed. A switch 192, a high-speed operation switch 193 and a reverse switch 194 for detecting switching between high-speed forward and reverse of the main shift lever 81, a manual flow switch 196 for detecting the stepping operation of the worker's flow pedal 195, and a low-speed / high-speed switch. A sub-transmission switch 197 for switching the sub-transmission is connected to a work controller 198 composed of a microcomputer.
[0042]
Further, a direct drive switch 199 for manually switching to an operation for driving the mowing unit 7 by a constant rotation output of the engine 21, an automatic switch 200 for turning on / off the manual input of the switch 199, a speed of the left and right traveling crawlers 2 (vehicle speed) ), Right and left vehicle speed sensors 201 and 202, a cereal stalk sensor 203 for detecting the presence or absence of a transported cereal culm of the mowing unit 7, and an input of a tuning input shaft 112 for inputting a driving force of vehicle speed tuning to the mowing unit 7. A cutting input sensor 204 for detecting the number of revolutions via a low-speed gear 117, cutting low-speed and cutting high-speed solenoids 205 and 206 for switching the cutting speed change cylinder 142 to low or high speed, and a feed chain for disengaging the feed chain clutch 131. A switching mechanism is provided by a feed chain solenoid 191 for operating a clutch cylinder and a constant rotation cylinder 143. A flow solenoid 208 for engaging the idler 124 with the flow gear 122 and a high-speed cut solenoid 209 for engaging the switching slider 124 with the high-speed cut gear 123 by the constant speed cylinder 143 are connected to the work controller 198. As described above, the mowing unit 7 is operated at the pouring speed, the high-speed cutting speed, or the vehicle speed tuning speed.
[0043]
A high-speed operation solenoid 211 that turns on the constant-speed clutch 76 when the high-speed operation switch 193 is turned on while the automatic switch 200 is on, and a sub-transmission cylinder by switching the sub-transmission switch 197. The operation controller includes a low-speed and high-speed solenoids 212 and 213 for sub-transmission for operating the traveling motor 39 at low speed or high-speed output, and a threshing clutch solenoid 214 for turning on the threshing clutch 97 by turning on the threshing switch 190. 198.
[0044]
Further, as shown in the flowchart of FIG. 34, when the threshing switch 190 is turned on by operating the work lever 189, the feed chain solenoid 207 is turned off, the feed chain clutch 131 is turned on, and the drive of the feed chain 5 is started, and The threshing clutch solenoid 214 is operated to turn on the threshing clutch 97, and the threshing unit 4 and the feed chain 5 are driven.
[0045]
When the harvesting switch 191 is turned on by operating the work lever 189, the main transmission driving force is transmitted to the harvesting unit 7 via the vehicle speed tuning pulley 93. At this time, when the pouring switch 196 is turned on by the stepping operation of the pouring pedal 195 and the pouring switch 196 is turned on, when the input rotational speed of the reaping unit 7 detected by the reaping input sensor 204 is equal to or less than the rotation setting by the pouring gear 122, the reaping is performed. The speed change slider 119 is moved to the neutral position to set the mowing speed change output of the mowing speed change mechanism 116 to neutral, thereby turning off the transmission of the vehicle speed tuning input shaft 122, and operating the pouring solenoid 208 to move the mowing portion 7 via the pouring gear 122. Is driven at a lower speed than the high-speed cut gear 123 at a constant speed.
On the other hand, when the pouring switch 196 is turned on and the input rotational speed of the reaping unit 7 for tuning the vehicle speed is equal to or higher than the rotation set by the pouring gear 122, the reaping transmission output of the reaping transmission mechanism 116 is neutralized and the The transmission is turned off, and the mowing unit 7 is driven at a constant speed at a maximum speed higher than that of the pouring gear 122 through the high-speed cut gear 123 by the operation of the high-speed cut solenoid 209.
[0046]
Further, when the reverse switch 194 is off and the axle 55 detected by the vehicle speed sensors 201 and 202 is stopped, the mowing speed change mechanism 116 is set to the neutral position and the vehicle speed tuning drive of the mowing unit 7 is stopped. On the other hand, when the axle 55 is driven, when the sub-shift output of the traveling motor 39 is at a low speed, and when the input rotation of the reaping unit 7 detected by the reaping input sensor 204 for tuning the vehicle speed is equal to or more than the rotation setting by the high-speed cut gear 123, Then, the high speed cut solenoid 209 is operated, the cutting speed change mechanism 116 is neutralized, and the high speed cutting operation for driving the cutting unit 7 at the highest speed and the constant speed via the high speed cutting gear 123 is performed.
[0047]
Also, when the sub-shift output of the traveling motor 39 is low, the input rotation of the mowing unit 7 is equal to or higher than a set value, the automatic switch 200 is on, and the direct drive switch 199 is turned on, the high-speed operation solenoid The constant speed clutch 76 is engaged by operating the 211, and the driving force of the engine 21 is directly transmitted from the constant speed clutch 76 to the subtransmission mechanism 47 without the intervention of the traveling speed change member 40, thereby performing a high-speed driving operation.
[0048]
When the direct drive switch 199 is off, the cutting speed change output of the cutting speed change mechanism 116 is switched to low speed or high speed by operating the cutting speed change switch 197, and the cutting speed is input via one of the gears 117 and 118 so that the cutting speed can be adjusted. 7 is driven at a low speed or a high speed to cut an upright grain stalk at a low speed or a lodging grain stalk at a high speed.
[0049]
Further, as shown in the flowchart of FIG. 35, when the key switch for operating the engine 21 is turned on to apply power to the work controller 198, the low-speed solenoid 212 is turned on to operate the sub-transmission valve 86, and the traveling motor 39 Swash plate 84 is switched to low speed. By operating the main transmission lever 81 to change the angle of the swash plate 79 of the travel pump 38 to travel, and by setting the sub transmission switch 197 to high speed, the sub transmission valve 86 is switched to high speed and the sub transmission switch 197 is operated. When the sub transmission valve 86 is switched to the low speed by operating the main transmission lever 81 to operate the traveling pump 38 at the highest speed, the volumetric efficiency of the traveling pump 38 becomes 90 to 95%. Near the maximum speed, the high speed operation switch 193 is turned on by the main shift lever 81, and when the maximum speed operation of the main speed lever 81 is detected, the low speed and high speed solenoids 212 and 213 are automatically turned off to change the sub speed. The valve 86 is kept neutral, the sub-transmission cylinder 85 is short-circuited to the oil tank side, and the piston of the cylinder 85 is free. The swash plate 84 of the traveling motor 39 is returned to the neutral side by the hydraulic pressure of the pump 38 so that the discharge hydraulic pressure of the traveling pump 38 becomes the hydraulic pressure of the charge pump 78, and the high-speed operation solenoid 211 is automatically turned on to set the vehicle speed constant. The speed valve 147 is switched, the vehicle speed constant speed cylinder 146 is operated to activate the constant speed clutch 76, and the driving force of the engine 21 is directly transmitted from the constant speed clutch 76 to the subtransmission mechanism 47 without passing through the traveling speed change member 40. Then, the left and right traveling crawlers 2 are driven. After switching the valve 147 with the piston of the cylinder 85 being free, the cylinder 85 may be fixed to the low speed side or may be free. After about 0.2 seconds have elapsed after the constant-speed clutch 76 is engaged, the sub-transmission valve 86 is neutralized, and the swash plate 84 of the traveling motor 39 is delayed to be free.
[0050]
FIG. 36 shows the relationship between the angle of the swash plate 79 of the traveling pump 38 and the hydraulic stepless output speed. The calculated maximum speed when the volume efficiency when the swash plate 79 of the traveling pump 38 is tilted to the maximum is 100%. On the other hand, the loss horsepower (5 to 10%) when the swash plate 79 angle is the maximum is subtracted, and the actually measured speed actually output becomes a low speed. By setting the gear transmission ratio at which the motor shaft 46 and the motor shaft 46 are gear-connected such that the speed at the calculated maximum speed at which the volumetric efficiency of the traveling pump 38 is 100% and the speed at the output side of the motor shaft 46 are substantially equal, The traveling crawler 2 is driven via the clutch 76 at the calculated maximum speed. Further, when the pump shaft 73 and the motor shaft 46 are directly connected via the constant speed clutch 76, the auxiliary transmission valve 86 becomes neutral, and the angle of the swash plate 84 of the traveling motor 39 changes freely by hydraulic pressure. The rotational load is kept to a minimum, and the hydraulic loss horsepower of the traveling transmission member 40 is effectively recovered.
[0051]
As apparent from the above description, in a working vehicle including the traveling speed change member 40 that is a hydraulic speed change mechanism that changes the driving speed and the constant speed clutch 76 that is a constant speed mechanism driven at substantially constant speed, the hydraulic pressure of the traveling speed change member 40 The traveling motor 39 has a variable output structure. Before the direct connection operation of the constant speed clutch 76 is performed, the output of the hydraulic traveling motor 39 is fixed at a low speed, and traveling is performed by making the output of the hydraulic traveling motor 39 variable. Although the speed change range of the speed change member 40 can be expanded, the output of the traveling speed change member 40 tends to be unstable. Therefore, when the driving of the traveling crawler 2 and the mowing unit 7 is started by the output of the traveling transmission member 40, the output of the hydraulic traveling motor 39 is locked at a substantially constant level. The driving of the traveling crawler 2 and the reaping unit 7 can be started by the stable output of the member 40, and the driving operability and the handling property are improved, and the output of the hydraulic traveling motor 39 can be varied by the output operation of the constant speed clutch 76. When the input side of the hydraulic travel pump 38 is directly connected to the output side of the hydraulic travel motor 39, the output of the hydraulic travel motor 39 is adjusted to be free to reduce the discharge amount on the hydraulic travel pump 38 side. Accordingly, the output of the hydraulic traveling motor 39 is adjusted so that the main circuit hydraulic pressure becomes minimum, and the discharge amounts of the hydraulic traveling pump 38 and the motor 39 are easily matched. So that it is, the main hydraulic circuit oil pressure to the charge pressure can be reduced smoothly, it is possible to effectively recover the loss horsepower of the hydraulic transmission mechanism.
[0052]
Further, a traveling transmission member 40 which is a hydraulic transmission mechanism for driving the traveling crawler 2 which is a traveling unit by converting the power of the engine 21 into a hydraulic continuously variable transmission output, and directly connecting an input side and an output side of the traveling transmission member 40. In a work vehicle provided with a constant speed clutch 76, which is a constant speed mechanism, the transmission ratio on the constant speed clutch 76 side is set so that the calculated maximum speed of the traveling transmission member 40 is obtained. By setting the gear transmission ratio on the constant speed clutch 76 side so that the volumetric efficiency of the traveling transmission member 40 substantially matches the output of about 100% (or several percentages higher), for example, the volumetric efficiency of the traveling transmission member 40 is increased. Is higher than 90% to 95%, the output becomes unstable, the output loss of 5 to 10% occurs, and the oil temperature rises. When the speed is increased to 90 to 95%), the direct connection operation of the constant speed clutch 76 is performed, the output loss when operating at the maximum speed is reduced, and the loss horsepower of the hydraulic shift is reduced from near the maximum speed to the speed. The speed can be smoothly increased to the calculated maximum speed to provide a stable maximum speed with an inexpensive structure to improve driving performance.
[0053]
The traveling speed change member 40 is provided with a hydraulic traveling pump 38 having a variable output structure and a hydraulic traveling motor 39 having a variable output structure. After the output of the hydraulic traveling motor 39 is made variable, the constant speed clutch 76 is directly connected. The operation may be performed to reduce a shock due to a speed difference when switching from the output of the traveling speed change member 40 to the output of the constant speed clutch 76, and to reduce the hydraulic pressure while the output is performed via the constant speed clutch 76. The operating oil pressure of the traveling motor 39 is reduced to the oil pressure of the charge pump 78, the driving load of the traveling transmission member 40 in the idle operation state is reduced, and the driving performance at the maximum speed by the constant speed clutch 76 is improved.
[0054]
Further, as shown in FIGS. 9 and 12, the constant speed clutch 76 is provided on the pump shaft 73 of the traveling pump 38, but the constant speed clutch 76 can be provided on the constant speed shaft 77 instead of the pump shaft 73. At the same time, a vehicle speed constant speed valve 147 is arranged on one side of the pump shaft 73 which is a lock-up constant speed shaft, and a hydraulic pipe between the constant speed cylinder 146 incorporated in the constant speed clutch 76 and the valve 147 is not required. Further, a gear for multi-speed shifting may be incorporated in the gear connection portion of the constant speed clutch 76 to switch the lock-up speed of the constant speed clutch 76 to multiple speeds.
[0055]
【The invention's effect】
As is clear from the above embodiment, the present invention drives the traveling unit 2 and the working unit 7 by the shift output of the hydraulic pump 38 of the hydraulic shift mechanism 40 at a speed equal to or lower than the highest speed, as in claim 1. In a work vehicle in which the input side and the output side of the hydraulic transmission mechanism 40 are directly connected by the constant speed mechanism 76 near the highest speed, the hydraulic motor 39 of the hydraulic transmission mechanism 40 has a variable output structure, and the direct connection operation of the constant speed mechanism 76 is performed. Before the transmission, the variable output of the hydraulic motor 39 is fixed on the low-speed side. By changing the output of the hydraulic motor 39, the shift range of the hydraulic transmission mechanism 40 can be expanded. There is a problem that tends to be unstable. Therefore, when the driving of the traveling unit 2 (and the working unit 7) is started by the output of the hydraulic transmission mechanism 40, the output of the hydraulic motor 39 is locked to the low speed side. The drive of the traveling unit 2 (and the working unit 7) can be started by the stable output of the mechanism 40, and the driving operability and handling can be improved.
[0056]
The output of the hydraulic motor 39 is made free by the output operation of the constant speed mechanism 76. When the input side of the hydraulic pump 38 and the output side of the hydraulic motor 39 are directly connected, the hydraulic motor 39 By making the output adjustment of 39 free, the output of the hydraulic motor 39 is adjusted so that the main circuit oil pressure becomes minimum in accordance with the discharge amount on the hydraulic pump 38 side, and the discharge amounts of the hydraulic pump 38 and the motor 39 can be easily adjusted. The main hydraulic circuit hydraulic pressure can be smoothly reduced to the charge pressure, and the horsepower loss of the hydraulic transmission mechanism can be effectively recovered.
[Brief description of the drawings]
FIG. 1 is a perspective view of a combine.
FIG. 2 is a side view of the same.
FIG. 3 is an explanatory plan view of the same.
FIG. 4 is an explanatory side view of the front body.
FIG. 5 is an explanatory front view of the same.
FIG. 6 is an explanatory side view of a driving unit.
FIG. 7 is an explanatory front view of the same.
FIG. 8 is an explanatory plan view of the same.
FIG. 9 is a drive system diagram of the transmission case.
FIG. 10 is a plan view of the same.
FIG. 11 is a rear view of the same section.
FIG. 12 is an enlarged view of the previous figure.
FIG. 13 is an enlarged view of FIG.
FIG. 14 is an engine output system diagram.
FIG. 15 is a hydraulic circuit diagram.
FIG. 16 is a drive system diagram of a counter case.
FIG. 17 is a sectional plan view of the same.
FIG. 18 is an enlarged view of FIG.
FIG. 19 is a sectional side view of the same.
FIG. 20 is an external front view of the same.
FIG. 21 is a plan view of the same.
FIG. 22 is a side view of the same.
FIG. 23 is a plan view of a threshing clutch unit.
FIG. 24 is a rear view of the same.
FIG. 25 is a partial view of the same.
FIG. 26 is a sectional view of a threshing cylinder unit.
FIG. 27 is a bottom view of the oil passage base.
FIG. 28 is a sectional side view of the same.
FIG. 29 is a sectional view of a mowing transmission cylinder unit.
FIG. 30 is a sectional view of a constant cutting speed cylinder part.
FIG. 31 is a cross-sectional rear view of a fork shaft portion.
FIG. 32 is an explanatory view of the same.
FIG. 33 is a control circuit diagram.
FIG. 34 is a flowchart of the harvest operation control in the preceding figure.
FIG. 35 is a flowchart of the vehicle speed control.
FIG. 36 is a traveling pump output diagram.
[Explanation of symbols]
2 Traveling crawler (traveling part)
38 hydraulic traveling pump 39 hydraulic traveling motor 40 traveling transmission member (hydraulic transmission mechanism)
76 Vehicle speed constant speed clutch (constant speed mechanism)

Claims (2)

最高速手前以下の速度で、油圧変速機構の油圧ポンプの変速出力により、走行部を駆動すると共に、最高速付近で油圧変速機構の入力側と出力側を定速機構により直結させる作業車において、油圧変速機構の油圧モータを出力可変構造とし、定速機構の直結動作を行わせる前は低速側で油圧モータの出力可変を固定させることを特徴とする請求項１に記載の作業車。In a work vehicle that drives the traveling section by the shift output of the hydraulic pump of the hydraulic transmission mechanism at a speed less than or equal to the highest speed, and directly connects the input side and the output side of the hydraulic transmission mechanism near the highest speed by a constant speed mechanism, 2. The work vehicle according to claim 1, wherein the hydraulic motor of the hydraulic transmission mechanism has a variable output structure, and the variable output of the hydraulic motor is fixed on the low speed side before the direct connection operation of the constant speed mechanism is performed. 定速機構の出力操作により油圧モータの出力可変をフリーにすることを特徴とする請求項１に記載の作業車。2. The work vehicle according to claim 1, wherein the variable output of the hydraulic motor is made free by an output operation of the constant speed mechanism.
JP2002265013A 2002-09-11 2002-09-11 Working vehicle Pending JP2004100853A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2002265013A JP2004100853A (en) 2002-09-11 2002-09-11 Working vehicle
CNB02829582XA CN100415075C (en) 2002-09-11 2002-11-22 Combine
PCT/JP2002/012249 WO2004023862A1 (en) 2002-09-11 2002-11-22 Combine
KR1020057004015A KR100955857B1 (en) 2002-09-11 2002-11-22 Combine
AU2002355026A AU2002355026A1 (en) 2002-09-11 2002-11-22 Combine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2002265013A JP2004100853A (en) 2002-09-11 2002-09-11 Working vehicle

Publications (1)

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JP (1) JP2004100853A (en)
KR (1) KR100955857B1 (en)
CN (1) CN100415075C (en)
AU (1) AU2002355026A1 (en)
WO (1) WO2004023862A1 (en)

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Publication number Priority date Publication date Assignee Title
CN102356721B (en) * 2005-12-02 2016-01-27 株式会社久保田 Combine
CN103327803B (en) * 2011-01-20 2015-12-02 洋马株式会社 Combine
JP5953934B2 (en) * 2012-05-18 2016-07-20 井関農機株式会社 Combine
CN103707945B (en) * 2012-09-28 2018-02-13 克拉斯印度莫林达私人有限公司 United reaper
WO2016093201A1 (en) * 2014-12-09 2016-06-16 ヤンマー株式会社 Combine
DE102017106636A1 (en) * 2017-03-28 2018-10-04 Claas Selbstfahrende Erntemaschinen Gmbh Method for operating an agricultural harvesting machine
CN113428223B (en) * 2021-07-21 2022-03-11 合肥工业大学 Steering speed consistency control method of full hydraulic steering mechanical system

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Publication number Priority date Publication date Assignee Title
JPS58193616A (en) * 1982-05-06 1983-11-11 株式会社クボタ Grain stalk conveyor apparatus of straight flow type combine
JPS62163826A (en) * 1986-01-10 1987-07-20 Iseki & Co Ltd Driving transmission gear for running body
JPH08252022A (en) * 1996-04-08 1996-10-01 Yanmar Agricult Equip Co Ltd Tuning control mechanism of reaping part in combined harvester
CN2258691Y (en) * 1996-11-19 1997-08-06 江西省吉安地区机电科学技术研究所 Semi-feed rice combine harvester with small track and vertical table
JPH10229732A (en) * 1997-02-20 1998-09-02 Yanmar Agricult Equip Co Ltd Combine
JP2000074185A (en) * 1998-09-01 2000-03-07 Kayaba Ind Co Ltd Hydrostatic transmission device

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KR100955857B1 (en) 2010-05-04
CN1668184A (en) 2005-09-14
WO2004023862A1 (en) 2004-03-25
CN100415075C (en) 2008-09-03
KR20050042799A (en) 2005-05-10
AU2002355026A1 (en) 2004-04-30

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