JP4704624B2

JP4704624B2 - Rice transplanter

Info

Publication number: JP4704624B2
Application number: JP2001233360A
Authority: JP
Inventors: 秀樹松岡
Original assignee: Yanmar Co Ltd
Current assignee: Yanmar Co Ltd
Priority date: 2001-08-01
Filing date: 2001-08-01
Publication date: 2011-06-15
Anticipated expiration: 2021-08-01
Also published as: JP2003042261A

Description

【０００１】
【発明の属する技術分野】
本発明は例えば苗載台及び苗植付爪を備えて連続的に苗植作業を行う田植機に関する。
【０００２】
【発明が解決しようとする課題】
従来、ギヤミッションでは高い動力伝達効率となるが、有段変速により操作性を向上し得ない不具合がある。また、油圧式無段変速機構は初速がゼロから発進させるゼロ発進可能な無段変速により優れた操作性を得られるが、動力伝達効率に限界があり、低速での動力損失が大きくなる不具合がある。また、Ｖベルト及びプーリを用いたベルト式無段変速機構は高効率の無段変速を行えるが、初速がゼロから発進させるゼロ発進を行えない不具合がある。例えば田植機などにおいて、湿田（泥土路面）での走破性、スムーズな圃場の出入、ショックの少ない変速動作、クラッチが不要な発進動作、作業または田面などの状況に適応した速度調節などが要求され、高い動力伝達効率、及びゼロ発進可能な無段変速、及び簡単な変速操作が望まれている。さらに、油圧変速機構の出力とギヤ伝動出力とを遊星ギヤ機構のデフ作用により合成出力してエンジン出力を変速伝達させることにより、高い動力伝達効率並びにゼロ発進可能な無段変速を得られるが、遊星ギヤ機構からの合成出力が停止（ゼロ）を挾んで前後進（正逆転）できるように速度設定した場合、前記合成出力の逆転側の変速領域を小さくして後進出力させ、前記合成出力の正転側の変速領域を大きくして前進出力させ、一般の作業速度において、油圧変速出力が高効率になるように構成することができるが、例えば油圧変速機構の油の粘性が温度（連続運転または気温）などにより変化すると、合成出力の停止（ゼロ）位置が後進側または前進側に移動し、変速操作位置が停止になっているときに前進または後進の出力が生じる不具合がある。そこで、合成出力の停止（ゼロ）位置を自動的に調節するための電気的な制御が必要になり、構造が複雑で製造コストが高くなる等の問題がある。
【０００３】
【課題を解決するための手段】
然るに、本発明は、前輪及び後輪を有し且つエンジンを搭載した走行車と、前記走行車に連結した植付部と、前記エンジンからの動力を変速して出力する油圧ポンプ・油圧モータ式の油圧変速機構と、前記エンジンからの動力及び前記油圧変速機構の変速出力を合成する遊星ギヤ機構と、前記遊星ギヤ機構の合成出力が一方向の回転力として伝達される合成出力軸、走行出力軸及びＰＴＯ出力軸を有するミッションケースとを備え、前記合成出力軸における一方向の回転力を、前記走行出力軸と前記ＰＴＯ出力軸とに伝達して、前記走行出力軸にて前記後輪を駆動し、前記ＰＴＯ出力軸にて前記植付部を駆動するように構成してなる田植機であって、前記油圧変速機構の変速出力を逆転方向に出力制御することで前記合成出力軸の回転数がゼロとなるように構成する一方、前記合成出力軸には、前記合成出力軸における一方向の回転力を前進、中立、後進の出力に切換えて前記走行出力軸に伝達する前進ギヤ・後進ギヤ機構を備えているもので、ゼロ発進時の出力トルクを容易に確保し得、微速走行性能を容易に向上し得、しかも作業速度で伝達ギヤの高い動力伝達効率の出力を有効に利用し得、泥土路面での作業能率の向上などを容易に図り得ると共に、油圧変速機構の出力特性または変速操作機構の組立誤差などに対し、油圧変速操作の停止（ゼロ速度）位置と合成出力軸のゼロ回転位置とにずれが生じても、油圧変速操作を停止にしたときに合成出力軸が回転して前後進する不具合を容易になくし得るものである。
【０００４】
また、ゼロ発進可能な無段変速と高い動力伝達効率を、簡単な油圧変速とギヤ組成とで容易に達成し得、走行性能及び変速操作性の向上などを容易に図り得るものである。
【０００５】
【０００６】
【０００７】
【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は全体の側面図、図２は同平面図、図３は車体フレームの側面図、図４は同平面図を示し、図中１は作業者が搭乗する走行車であり、エンジン２を車体フレーム３に搭載させ、ミッションケース４側方にフロントアクスルケース５を介して水田走行用前輪６を支持させると共に、前記ミッションケース４後方のリヤアクスルケース７に水田走行用後輪８を支持させる。そして前記エンジン２等を覆うボンネット９両側に予備苗載台１０を取付けると共に、作業者が搭乗する車体カバー１１によって前記ミッションケース４等を覆い、前記車体カバー１１後側上方にシートフレーム１２を介して運転席１３を取付け、その運転席１３の前方で前記ボンネット９後部に操向ハンドル１４を設ける。
【０００８】
また、図中１５は５条植え用の苗載台１６並びに複数の苗植付爪１７などを具備する植付部であり、前高後低の合成樹脂製の前傾式苗載台１６を下部レール１８及びガイドレール１９を介して植付ケース２０に左右往復摺動自在に支持させると共に、一方向に等速回転させるロータリケース２１を前記植付ケース２０に支持させ、該ケース２１の回転軸芯を中心に対称位置に一対の爪ケース２２・２２を配設し、その爪ケース２２・２２先端に苗植付爪１７・１７を取付ける。
【０００９】
また、前記植付ケース２０前側のヒッチブラケット２３をトップリンク２４及びロワーリンク２５を含む昇降リンク機構２６を介し走行車１後側に連結させ、前記リンク機構２６を介して植付部１５を昇降させる油圧昇降シリンダ２７をロワーリンク２５に連結させ、前記前後輪６・８を走行駆動して移動すると同時に、左右に往復摺動させる苗載台１６から一株分の苗を植付爪１７によって取出し、連続的に苗を植える田植作業を行うように構成する。
【００１０】
また、図中２８は主変速レバー、２９は植付昇降レバー、３０はブレーキペダル、３１は変速ペダル、３２はデフロックペダル、３３は感度調節レバー、３４は植付部１５任意高さ位置に停止させるストップレバー、３５はユニットクラッチレバー３５であり、操向ハンドル１４位置近傍に変速及び昇降レバー２８・２９やブレーキ及び変速ペダル３０・３１を配設すると共に、運転席１３位置近傍に感度調節及びストップ及びユニットクラッチの各レバー３３・３４・３５やデフロックペダル３２を配設している。
【００１１】
さらに、図中３６は１条分均平用センタフロート、３７は２条分均平用サイドフロート、３８は肥料ホッパ３９内の肥料を送風機４０の送風力でフレキシブル形搬送ホース４１を介しフロート３６・３７の側条作溝器４２に排出させる５条用側条施肥機である。
【００１２】
図３乃至図５に示す如く、前記車体フレーム３は前部フレーム４３と中間フレーム４４と後部フレーム４５とに３分割させ、左右一対の前部フレーム４３にエンジン２を、左右一対の中間フレーム４４にフロントアクスルケース５を、左右一対の後部フレーム４５にリヤアクスルケース７及びエンジン２に燃料を供給する燃料タンク４６などを設けるもので、前部フレーム４３の前側と中間に前フレーム４７とベースフレーム４８を連結させて平面視４角枠状に形成し、固定ブラケット４９とベースフレーム４８に防振ゴムを介しエンジン２を上載させる。
【００１３】
また、前記後部フレーム４５の中間立上り部５０間をパイプフレーム５１と門形フレーム５２とで略平行に連結させると共に、リヤアクスルケース７に左右下端を固設する門形フレーム５３の後端を一体連結させ、前記の左右の立上り部５０間に燃料タンク４６を配設する。
【００１４】
さらに、前部フレーム４３後端と後部フレーム４５前端に左右中間フレーム４４の前後端をボルト５４を介して取外し自在に固定させると共に、左右中間フレーム４４の下面にボルト５５を介して左右フロントアクスルケース５を取外し自在に固定させ、前記ミッションケース４に左右フロントアクスルケース５を接続固定させる。
【００１５】
図６乃至図９に示す如く、前記ミッションケース４の前面左側にパワーステアリングケース５６を設け、かつケース４の右側に無段油圧変速機構５７を設け、油圧変速機構５７の変速入力用ポンプ軸５８を車体前方向に突出させ、エンジン２下側で前後方向の伝達軸５９にポンプ軸５８を連結させると共に、エンジン２の出力軸６０に伝達ベルト６１を介して前記伝達軸５９を連結させ、エンジン２出力を油圧変速機構５７に伝達する。
【００１６】
また、前記ミッションケース４とリヤアクスルケース７を車体の前後方向の中心ライン上でパイプ製の連結フレーム６２によって一体連結させ、ミッションケース４後方にリヤ出力軸６３及びＰＴＯ出力軸６４を突出させ、リヤアクスルケース７前方に突出させるリヤ入力軸６５にリヤ伝達軸６６を介し前記リヤ出力軸６３を連結させ、走行出力軸６３から左右の後輪８に動力を伝える。またリヤアクスルケース７上部の軸受６７に設ける中介軸６８に自在継手軸６９を介して前記ＰＴＯ出力軸６４を連結させ、前記植付ケース２０の入力軸に自在継手軸を介して中介軸６８を連結させ、ＰＴＯ出力軸６４から植付部１５に動力を伝える。
【００１７】
さらに、図１０乃至図１９に示す如く、前記ミッションケース４は、本体胴部７０と、前蓋部７１と、後蓋部７２を備え、前記胴部７０の前後に各蓋部７２を着脱自在にボルト固定させ、密閉箱形に形成すると共に、前記胴部７０の内部を前後に分割する仕切り壁部７３を設ける。また、前蓋部７１前面に前記油圧変速機構５７を取付け、ミッションケース４内に突出させるポンプ軸５８に小径の伝達ギヤ７４を係合軸支させ、伝達ギヤ７４を前蓋部７１にベアリング軸受し、後蓋部７２後面に固定させるチャージポンプ７５に伝達ギヤ７４の動力をパイプ軸７６を介して伝える。
【００１８】
また、前記ミッションケース４内に突出させる油圧変速機構５７のモータ軸７７にサンギヤ７８を係合軸支させ、サンギヤ７８を前蓋部７１にベアリング軸受すると共に、前記の小径の伝達ギヤ７４に大径のキャリヤギヤ７９を常に噛合させ、サンギヤ７８のボス部にキャリヤギヤ７９を遊転軸支させるもので、キャリヤギヤ７９に３枚のプラネタリギヤ８０を軸８１を介して回転自在に設け、サンギヤ７８にプラネタリギヤ８０を噛合させると共に、プラネタリギヤ８０に噛合させるリングギヤ８２を設け、各ギヤ７８・８０・８２によって遊星ギヤ機構８３を形成する。
【００１９】
また、前記サンギヤ７８と後蓋部７２に合成出力軸８４の前後を回転自在に軸支させ、前記リングギヤ８２を合成出力軸８４に係合軸支させるもので、油圧変速機構５７の油圧ポンプ８５及び油圧モータ８６の無段油圧変速出力である正逆回転出力と、伝達ギヤ７４及びキャリヤギヤ７９の減速回転出力（一方向の一定回転）とを、遊星ギヤ機構８３のデフ作用によって合成し、ゼロ乃至最大速の一方向の回転力として合成出力軸８４に伝える。
【００２０】
さらに、前記合成出力軸８４に前進ギヤ８７と後進ギヤ８８を遊転軸支させ、合成出力軸８４に各ギヤ８７・８８をスライダ８９によって選択的に係合させ、前進または中立または後進の出力に切換えると共に、仕切り壁部７３と後蓋部７２に前記リヤ出力軸６３をベアリング軸受する。また、差動ギヤ９０を介して左右の前車軸９１に動力を伝えるフロント出力軸９２と、ＰＴＯ変速ギヤ９３を係合軸支させるカウンタ軸９４を設け、図２０の状態下で、前記のリヤ及びフロント出力軸６３・９２に出力ギヤ９５・９６を介して後進ギヤ８８の後進動力を伝え、前後輪６・８を後進駆動させると共に、リヤ出力軸６３に移動ギヤ９７及び植付ギヤ９８を遊転軸支させ、副変速スライダ９９によって各ギヤ９７・９８をリヤ出力軸６３に選択的に係合させる。
【００２１】
また、カウンタ軸９４の高速用ギヤ１００を介して前進ギヤ８７に移動ギヤ９７を常に噛合させると共に、カウンタ軸９４の低速用のＰＴＯ変速ギヤ９３に植付ギヤ９８を常に噛合させ、図２１の状態下で、各ギヤ１００・９３・９８を介して前進ギヤ８７の動力を前記各出力軸６３・９２に伝え、前後輪６・８を苗の植付け作業速度で前進駆動する。また、図２２の状態下で、移動ギヤ９７と植付ギヤ９８の両方が遊転状態となり、植付爪１７などを作業者が手で回転させて詰った苗の除去などを行えるように、ＰＴＯ出力軸６４の手動回転を可能にすると共に、図２３の状態下で、前進ギヤ８７の動力を各ギヤ１００・９７を介して各出力軸６３・９２に伝え、圃場間の路上移動などの高速の移動速度で前後輪６・８を前進駆動する。
【００２２】
さらに、図１１のように、ＰＴＯ変速軸１０１及びＰＴＯ変速機構１０２を介してＰＴＯ変速ギヤ９３の動力をＰＴＯ出力軸６４に伝え、株間変速自在に植付部１５を駆動すると共に、ミッションケース４に内設させるチェン１０３を介してＰＴＯ出力軸６４に施肥出力軸１０４を連結させ、植付部１５と同調させて施肥機３８を駆動する。また、図１２のように、ミッションケース４にオイルゲージ１０５を設けると共に、図１３のように、前記各スライダ８９・９９を同一のシフトフォーク１０６に係止させ、変速レバー２８の５位置切換によって前後進及び副変速（低高速）の切換を行う。また、図１５乃至図１７のように、油圧ポンプ８５の斜板１０７に制御軸１０８を介して油圧変速操作アーム１０９を連結させ、該アーム１０９にロッド１１０を介して変速ペダル３１を連結させると共に、ペダル３１の足踏み解除によってペダル３１を自動的に停止（速度ゼロ）位置に復帰動作させるバネ１１１を前記アーム１０９に連結させ、また定速作動部材であるオイルダンパ１１２を前記アーム１０９に連結させ、踏み込んでいたペダル３１から足を離したとき、オイルダンパ１１２の抵抗とバネ１１１の復動力によりペダル３１が緩やかな略一定速度で戻って除々に低速になる動作を行わせる。なお、オイルダンパ１１２に代え、ガススプリングなどによって定速作動部材を形成してもよい。
【００２３】
さらに、図２４のように、前記ペダル３１から足を離している状態でバネ１１１によってペダル３１が停止（速度ゼロ）位置に戻っているとき、サンギヤ７８は最高回転で時計回りに逆転してプラネタリギヤ８０を反時計回りに自転させる動作を行わせると同時に、また伝達ギヤ７４によってキャリヤギヤ７９を回転させることにより、プラネタリギヤ８０を時計方向に公転させて反時計回りに自転させる動作を行わせ、リングギヤ８２の回転をゼロにし、合成出力軸８４を停止維持する。また、ペダル３１をバネ１１１に抗して中位置（中速域）に足で踏んだとき、サンギヤ７８は停止し、伝達ギヤ７４によってキャリヤギヤ７９を回転させ、プラネタリギヤ８０を時計方向に自転させ乍ら時計方向に公転させ、伝達ギヤ７４のギヤ動力により合成出力軸８４を回転させる。また、ペダル３１を最大に踏み込んだとき、サンギヤ７８は最高回転で反時計回りに正転し、プラネタリギヤ８０を時計方向に自転させ乍ら伝達ギヤ７４でキャリヤギヤ７９を回転させることによって時計方向に公転させ、サンギヤ７８からの油圧変速力と伝達ギヤ７４動力を加算して合成出力軸８４を回転させるもので、図２５のように、エンジン２動力を伝達ギヤ７４と油圧変速機構５７とに伝えて遊星ギヤ機構８３により合成して出力させ、ミッションケース４で前後進切換とＰＴＯ変速を行い、後進、低速前進（圃場植付走行）、高速前進（路上移動走行）の各動作を行わせる。
【００２４】
そして、例えば、一般的な入力動力１００に対して、ギヤ７４の損失が２で、油圧変速の損失が３０の条件下において、図２６のように、低速で走行時、エンジン２の入力動力を１００とし、油圧伝達動力を５０にした場合、油圧伝達動力の５０がポンプ軸５８に戻ってギヤ７４側の伝達動力が１５０になると、ギヤ７４の損失が３で、油圧変速機構５７の損失が１５となり、出力動力が８２の割合で得られる。また、図２７のように、前記油圧変速機構５７の伝達動力をゼロにする中速で走行時、ギヤ７４側の伝達動力が１００になり、ギヤ７４の損失が２となり、出力動力が９８の割合で得られる。また、図２８のように、高速で走行時、油圧伝達動力が４０で、ギヤ７４側の伝達動力が６０の場合、ギヤ７４の損失が１で、油圧変速機構５７の損失が１２となり、出力動力が８７の割合で得られるもので、例えば、図２９のように、油圧変速操作アーム１０９の角度を−１乃至０乃至１に変化させることにより、モータ軸７７が−１０００乃至０乃至１０００回転になるようにし、図３０のように、前記アーム１０９の角度に関係なくギヤ７４側を１０００回転させた場合、図３１のように、前記アーム１０９の角度に対して合成出力軸８４が０乃至２０００回転になるように、ギヤ７４・７９及び遊星ギヤ機構８３を組成する。
【００２５】
また、前記アーム１０９の全制御範囲を−１乃至０乃至１としたとき、図１８に示す如く、前記アーム１０９の低速（ゼロ速度）側及び高速側の制御動作をボルト型低速及び高速ストッパ１１３・１１４によって規制し、図３２のように、前記各ストッパ１１３・１１４によって調節自在な実際のアーム１０９の操作範囲を−０．８乃至０．６にして、０乃至１．４m/sの作業速度を得ることにより、油圧変速機構５７の組立誤差などによって生じる出力特性のバラツキに対して前記各ストッパ１１３・１１４により調整すると共に、例えば前記アーム１０９の−１乃至−０．８の位置を調整域とし、速度をゼロにすることができ、仮りにアーム１０９が−１でも速度がゼロにならない不具合をなくしている。図３３及び図３４のように、一般的な作業速度において、油圧変速機構５７とギヤ７４側の動力分担比が６０パーセント以上にし、油圧変速機構５７の有効動力に対し、ギヤ７４側の有効動力の割合を大きくし、湿田での走破性を向上させ、湿田での作業能率を向上させ、また耕盤の段差に対して余裕の脱出能力を持たせる。
【００２６】
上記から明らかなように、エンジン２の駆動力を伝える油圧変速機構５７と伝達ギヤ７４を設け、油圧変速機構５７と伝達ギヤ７４の各出力を合成して変速出力を形成し、前記伝達ギヤ７４を用いて高い動力伝達効率の出力を得、前記油圧変速機構５７を用いてゼロ発進可能な無段変速の出力を得、簡単な変速操作で状況に応じた速度調節を行い、変速機能の向上並びに取扱い操作性の向上などを図ると共に、油圧変速機構５７の正転または逆転の各出力により、油圧変速機構５７と伝達ギヤ７４の各出力を合成して変速出力する合成出力軸８４を一方向に回転させ、ゼロ発進時の出力トルクを容易に確保し、微速走行性能を容易に向上させ、しかも作業速度で伝達ギヤ７４の高い動力伝達効率の出力を有効に利用し、泥土路面での作業能率の向上などを図る。
【００２７】
また、０乃至最大車速の中間の伝達速度になる減速比に伝達ギヤ７４を形成し、ゼロ発進可能な無段変速の操作を行わせ乍ら、高い動力伝達効率の伝達ギヤ７４の出力によって一定の速度を維持する連続作業を行い、走行性能の向上並びに作業能率の向上などを図ると共に、油圧変速機構５７と伝達ギヤ７４の各出力の割合を、発進時に略等しくし、発進に必要な大きな出力トルクを確保し乍ら、無段変速の操作によりゼロ発進並びに微速移動の各動作をスムーズに行わせ、例えば圃場または運搬トラックの荷台などへの出入或いは畦越え走行などの超低速の走行性の向上を図る。
【００２８】
また、発進時以外の低速乃至高速走行のとき、油圧変速機構５７に対して伝達ギヤ７４の出力割合を大きくし、高い動力伝達効率の伝達ギヤ７４の出力によって一定の速度を維持する連続作業を行い、走行性能の向上並びに作業能率の向上などを図ると共に、０乃至最大車速の中間以上で油圧変速機構５７の正逆転の切換を行い、ゼロ発進時の出力トルクを確保し、微速走行性能を向上させ、しかも作業速度で伝達ギヤ７４の高い動力伝達効率の出力を有効に利用し、泥土路面での作業能率の向上などを図る。
【００２９】
また、伝達ギヤ７４の伝動比率が全体の半分以上のときを作業速度にし、高い動力伝達効率の伝達ギヤ７４の出力によって一定の速度を維持する連続作業を行い、走行性能の向上並びに作業能率の向上などを図ると共に、０乃至最大車速の間で、油圧変速機構５７の逆転出力域を、正転出力域よりも大きくし、ゼロ発進及び微速走行の性能を向上させ、しかも作業速度で伝達ギヤ７４の高い動力伝達効率の出力を有効に利用し、泥土路面での作業能率の向上などを図る。
【００３０】
また、エンジン２の駆動力を油圧変速機構５７のポンプ軸５８に入力させ、油圧変速機構５７のモータ軸７７と、前記ポンプ軸５８に連結させる伝達ギヤ７４とを、遊星ギヤ機構８３を介して合成出力軸８４に連結させ、油圧伝動と伝達ギヤ７４伝動を合成して出力させる作業車において、油圧変速機構５７の変速可能範囲で、合成出力軸８４を一方向に回転させるように、伝達ギヤ７４及び遊星ギヤ機構８３を設け、ゼロ発進可能な無段変速と高い動力伝達効率を、簡単な油圧変速とギヤ組成とで達成し、走行性能及び変速操作性の向上などを図ると共に、油圧変速機構５７の油圧変速操作アーム１０９によって合成出力軸８４の回転を調節し、前記操作アーム１０９の低速出力側の最大操作位置よりも高速出力側にずらせて合成出力軸８４のゼロ回転位置を設定し、油圧変速機構５７の出力特性または変速操作機構の組立誤差などに対し、操作アーム１０９の最低速（ゼロ速度）位置と合成出力軸８４のゼロ回転位置とにずれが生じても、操作アーム１０９を最低速に操作したときに合成出力軸８４が回転する不具合をなくす。
【００３１】
また、油圧変速機構５７の出力制御を、自動的に復動させるペダル３１の一方向操作で行い、前記ペダル３１の足踏み操作により油圧変速機構５７を無段変速動作させ、両手による操向ハンドル１４操作並びに自由自在な速度調節を行い、例えば一方の手で操向ハンドル１４を操作し乍らもう一方の手で変速レバーを操作する従来の煩わしい運転を不要にし、操舵及び変速操作性の向上などを図ると共に、前後進切換用のギヤ８７・８８及びＰＴＯ出力用のギヤ９３を、合成出力軸８４の出力側に設け、合成出力軸８４の入力側をクラッチ等で動力切断することなく、合成出力軸８４をゼロ回転にするだけで前記ギヤ８７・８８・９３の切換を行い、エンジン２の出力を断続させるクラッチ等を不要にし、前後進操作またはＰＴＯ変速などを行い、しかも前記各ギヤ８７・８８・９３を近接させて前後進切換とＰＴＯ変速を同一の操作機構を兼用して行い、かつ前記各ギヤ８７・８８・９３の設置構造のコンパクト化及び簡略化などを図る。
【００３２】
【発明の効果】
以上実施例から明らかなように本発明は、前輪６及び後輪８を有し且つエンジン２を搭載した走行車１と、走行車１に連結した植付部１５と、エンジン２からの動力を変速して出力する油圧ポンプ８５・油圧モータ８６式の油圧変速機構５７と、エンジン２からの動力及び油圧変速機構５７の変速出力を合成する遊星ギヤ機構８３と、遊星ギヤ機構８３の合成出力が一方向の回転力として伝達される合成出力軸８４、走行出力軸６３及びＰＴＯ出力軸６４を有するミッションケース４とを備え、合成出力軸８４における一方向の回転力を、走行出力軸６３とＰＴＯ出力軸６４とに伝達して、走行出力軸６３にて後輪８を駆動し、ＰＴＯ出力軸６４にて植付部１５を駆動するように構成してなる田植機であって、油圧変速機構５７の変速出力を逆転方向に出力制御することで合成出力軸８４の回転数がゼロとなり、油圧変速機構５７の変速出力が正転方向最大の状態で合成出力軸８４が最高回転状態となるように構成する一方、合成出力軸８４には、当該合成出力軸８４における一方向の回転力を前進、中立、後進の出力に切り換えて走行出力軸６３に伝達する前進ギヤ・後進ギヤ機構４ａを備えるものである。
このため、ゼロ発進時の出力トルクを容易に確保でき、微速走行性能を容易に向上でき、しかも作業速度で伝達ギヤ７４の高い動力伝達効率の出力を有効に利用でき、泥土路面での作業能率の向上などを容易に図ることができると共に、油圧変速機構５７の出力特性または変速操作機構の組立誤差などに対し、油圧変速操作の停止（ゼロ速度）位置と合成出力軸８４のゼロ回転位置とにずれが生じても、油圧変速操作１０９を停止にしたときに合成出力軸８４が回転して前後進する不具合を容易になくすことができるものである。
【００３３】
また、ゼロ発進可能な無段変速と高い動力伝達効率を、簡単な油圧変速とギヤ組成とで容易に達成でき、走行性能及び変速操作性の向上などを容易に図ることができるものである。
【００３４】
【００３５】
【図面の簡単な説明】
【図１】田植機の全体側面図。
【図２】田植機の全体平面図。
【図３】走行車体の側面図。
【図４】走行車体の平面図。
【図５】車体フレームの側面図。
【図６】駆動部の側面説明図。
【図７】駆動部の平面説明図。
【図８】サイドクラッチ操作系の側面説明図。
【図９】サイドクラッチ操作系の平面説明図。
【図１０】ミッションケースの断面図。
【図１１】同拡大図。
【図１２】遊星ギヤ機構の説明図。
【図１３】ミッションケースの部分図。
【図１４】遊星ギヤ機構の断面図。
【図１５】変速ペダル部の前方からの斜視図。
【図１６】変速ペダル部の後側上方からの斜視図。
【図１７.】ミッションケースのギヤ配列説明図。
【図１８】油圧変速操作アーム部の側面図。
【図１９】ギヤ変速の中立状態の説明図。
【図２０】ギヤ変速の後進状態の説明図。
【図２１】ギヤ変速の植付走行状態の説明図。
【図２２】ギヤ変速のＰＴＯ空転状態の説明図。
【図２３】ギヤ変速の移動走行状態の説明図。
【図２４】遊星ギヤ機構の回転説明図。
【図２５】エンジンの出力説明図。
【図２６】低速走行のエンジン出力説明図。
【図２７】中速走行のエンジン出力説明図。
【図２８】高速走行のエンジン出力説明図。
【図２９】油圧変速機構の出力説明図。
【図３０】伝達ギヤ側の出力説明図。
【図３１】合成出力軸の出力説明図。
【図３２】変速ペダルの変速説明図。
【図３３】油圧変速出力とギヤ変速出力の相関図。
【図３４】図３３の出力と油圧損失及びギヤ損失の相関図。
【符号の説明】
２エンジン
３１変速ペダル
５７油圧変速機構
５８ポンプ軸
７４伝達ギヤ
７７モータ軸
８３遊星ギヤ機構
８４合成出力軸
８７前進ギヤ
８８後進ギヤ
９３ＰＴＯ変速ギヤ
１０９油圧変速操作アーム[0001]
BACKGROUND OF THE INVENTION
The present invention relates to, for example, a rice transplanter that includes a seedling stage and a seedling planting claw and performs seedling planting work continuously.
[0002]
[Problems to be solved by the invention]
Conventionally, gear transmission has high power transmission efficiency, but there is a problem that the operability cannot be improved by stepped shifting. In addition, the hydraulic continuously variable transmission mechanism has excellent operability due to the continuously variable transmission that can start from zero, with the initial speed starting from zero, but there is a limit to the power transmission efficiency and there is a problem that the power loss at low speed increases. is there. A belt type continuously variable transmission mechanism using a V-belt and a pulley can perform a highly efficient continuously variable transmission, but there is a problem that the initial speed cannot start from zero. For example, rice transplanters are required to run on wet fields (muddy roads), smoothly enter and exit the field, shift operation with little shock, start-up operation that does not require a clutch, speed adjustment adapted to the situation such as work or paddy surface, etc. Therefore, high power transmission efficiency, continuously variable transmission capable of zero start, and simple gear shifting operation are desired. Furthermore, by combining and outputting the output of the hydraulic transmission mechanism and the gear transmission output by the differential action of the planetary gear mechanism to transmit the engine output, a high power transmission efficiency and a continuously variable transmission capable of zero start can be obtained. When the speed is set so that the combined output from the planetary gear mechanism can move forward and backward (forward / reverse) with the stop (zero) in mind, the reverse shift side of the combined output is reduced and the reverse output is performed. It is possible to increase the forward shift region and output forward, so that the hydraulic shift output can be configured to be highly efficient at normal working speeds. When the speed changes, the combined output stop (zero) position moves backward or forward, and forward or reverse output occurs when the shift operation position is stopped. There is a condition. Therefore, electrical control for automatically adjusting the stop (zero) position of the composite output is required, and there is a problem that the structure is complicated and the manufacturing cost is increased.
[0003]
[Means for Solving the Problems]
However, the present invention relates to a traveling vehicle having front wheels and rear wheels and mounted with an engine, a planting portion connected to the traveling vehicle, and a hydraulic pump / hydraulic motor type that shifts and outputs power from the engine. A hydraulic transmission mechanism, a planetary gear mechanism that synthesizes power from the engine and a shift output of the hydraulic transmission mechanism, a combined output shaft that transmits a combined output of the planetary gear mechanism as a unidirectional rotational force, and a traveling output A transmission case having a shaft and a PTO output shaft, and transmitting a rotational force in one direction on the combined output shaft to the travel output shaft and the PTO output shaft, and the rear output on the travel output shaft. A rice transplanter configured to drive and drive the planting unit with the PTO output shaft, and the rotation of the combined output shaft by controlling the shift output of the hydraulic transmission mechanism in the reverse direction. Number is ZE On the other hand, the composite output shaft is provided with a forward gear / reverse gear mechanism that transmits a rotational force in one direction of the composite output shaft to forward, neutral, and reverse outputs and transmits the output to the travel output shaft. provided by those which give easily ensure output torque at zero start, easily improving the fine speed running performance obtained. Moreover obtained by effectively utilizing the output of the high power transmission efficiency transmission gear at a working speed, mud It is easy to improve the work efficiency on the road surface, and the stop position (zero speed) of the hydraulic speed change operation and the zero rotation position of the composite output shaft against the output characteristics of the hydraulic speed change mechanism or the assembly error of the speed change mechanism Even if a deviation occurs, it is possible to easily eliminate the problem that the combined output shaft rotates and moves forward and backward when the hydraulic shift operation is stopped.
[0004]
In addition, a continuously variable transmission capable of starting at zero and a high power transmission efficiency can be easily achieved by a simple hydraulic transmission and a gear composition, and traveling performance and shift operability can be easily improved.
[0005]
[0006]
[0007]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings. 1 is a side view of the whole, FIG. 2 is a plan view of the same, FIG. 3 is a side view of a vehicle body frame, FIG. 4 is a plan view of the body, and 1 is a traveling vehicle on which an operator rides. Mounted on the vehicle body frame 3, the front wheel 6 for paddy field traveling is supported on the side of the transmission case 4 via the front axle case 5, and the rear wheel 8 for paddy field traveling is supported on the rear axle case 7 behind the transmission case 4. The spare seedling stage 10 is attached to both sides of the bonnet 9 that covers the engine 2 and the like, and the mission case 4 and the like are covered by a vehicle body cover 11 on which an operator rides, and a seat frame 12 is disposed on the rear upper side of the vehicle body cover 11 via a seat frame 12. A driver's seat 13 is attached, and a steering handle 14 is provided at the rear of the bonnet 9 in front of the driver's seat 13.
[0008]
In the figure, reference numeral 15 denotes a planting part having a seedling mounting table 16 for five-row planting and a plurality of seedling planting claws 17. The planting case 20 is supported by the planting case 20 through the lower rail 18 and the guide rail 19 so as to be slidable in the left and right directions, and a rotary case 21 that rotates at a constant speed in one direction is supported by the planting case 20. A pair of nail cases 22 and 22 are arranged at symmetrical positions around the axis, and seedling planting nails 17 and 17 are attached to the tips of the nail cases 22 and 22.
[0009]
Further, the hitch bracket 23 on the front side of the planting case 20 is connected to the rear side of the traveling vehicle 1 through an elevating link mechanism 26 including a top link 24 and a lower link 25, and the planting unit 15 is moved up and down via the link mechanism 26. The hydraulic lifting cylinder 27 is connected to the lower link 25, and the front and rear wheels 6 and 8 are driven to move, and at the same time, the seedlings 16 are slid back and forth, and one seedling is planted by the planting claws 17. It is configured to carry out rice transplanting work to take out and plant seedlings continuously.
[0010]
In the figure, 28 is a main transmission lever, 29 is a planting lift lever, 30 is a brake pedal, 31 is a transmission pedal, 32 is a differential lock pedal, 33 is a sensitivity adjustment lever, and 34 is stopped at an arbitrary height position of the planting part 15. The stop lever 35 is a unit clutch lever 35. The shift and elevating levers 28 and 29, the brakes and the shift pedals 30 and 31 are disposed in the vicinity of the steering handle 14, and the sensitivity adjustment and adjustment are performed in the vicinity of the position of the driver seat 13. Stop and unit clutch levers 33, 34 and 35 and a differential lock pedal 32 are provided.
[0011]
Further, in the figure, 36 is a center float for leveling of one strip, 37 is a side float for leveling of two strips, 38 is a float 36 through the flexible conveying hose 41 with fertilizer in the fertilizer hopper 39 by the blowing force of the blower 40. -It is a 5-way side strip fertilizer machine which makes it discharge to 37 side strip groover 42.
[0012]
3 to 5, the vehicle body frame 3 is divided into a front frame 43, an intermediate frame 44, and a rear frame 45. The engine 2 is connected to the pair of left and right front frames 43, and the pair of left and right intermediate frames 44. A front axle case 5, a pair of left and right rear frames 45 are provided with a rear axle case 7 and a fuel tank 46 for supplying fuel to the engine 2. A front frame 47 and a base frame 48 are provided between the front side and the middle of the front frame 43. Are connected to form a quadrangular frame shape in plan view, and the engine 2 is mounted on the fixed bracket 49 and the base frame 48 via vibration-proof rubber.
[0013]
In addition, the intermediate rising portion 50 of the rear frame 45 is connected in a substantially parallel manner by the pipe frame 51 and the portal frame 52, and the rear end of the portal frame 53 in which the left and right lower ends are fixed to the rear axle case 7 is integrally connected. The fuel tank 46 is disposed between the left and right rising portions 50.
[0014]
Further, the front and rear ends of the left and right intermediate frame 44 are detachably fixed to the rear end of the front frame 43 and the front end of the rear frame 45 via bolts 54, and the left and right front axle cases are fixed to the lower surface of the left and right intermediate frames 44 via bolts 55. The left and right front axle case 5 is connected and fixed to the transmission case 4.
[0015]
As shown in FIGS. 6 to 9, a power steering case 56 is provided on the front left side of the transmission case 4 and a continuously variable hydraulic transmission mechanism 57 is provided on the right side of the case 4. And the pump shaft 58 is connected to the transmission shaft 59 in the front-rear direction at the lower side of the engine 2, and the transmission shaft 59 is connected to the output shaft 60 of the engine 2 via the transmission belt 61. Two outputs are transmitted to the hydraulic transmission mechanism 57.
[0016]
Further, the transmission case 4 and the rear axle case 7 are integrally connected by a connecting frame 62 made of pipe on the center line in the longitudinal direction of the vehicle body, and the rear output shaft 63 and the PTO output shaft 64 are projected to the rear of the transmission case 4 so that the rear axle is The rear output shaft 63 is connected via a rear transmission shaft 66 to a rear input shaft 65 that protrudes forward of the case 7, and power is transmitted from the traveling output shaft 63 to the left and right rear wheels 8. Further, the PTO output shaft 64 is connected via a universal joint shaft 69 to an intermediate shaft 68 provided on the bearing 67 at the upper part of the rear axle case 7, and the intermediate shaft 68 is connected to the input shaft of the planting case 20 via a universal joint shaft. Power is transmitted from the PTO output shaft 64 to the planting unit 15.
[0017]
Further, as shown in FIGS. 10 to 19, the mission case 4 includes a main body barrel 70, a front lid portion 71, and a rear lid portion 72, and each lid portion 72 is detachably attached to the front and rear of the trunk portion 70. A partition wall portion 73 that divides the inside of the body portion 70 into the front and the rear is provided. Further, the hydraulic transmission mechanism 57 is attached to the front surface of the front lid portion 71, a small-diameter transmission gear 74 is supported on the pump shaft 58 that protrudes into the transmission case 4, and the transmission gear 74 is attached to the front lid portion 71 as a bearing bearing. Then, the power of the transmission gear 74 is transmitted via the pipe shaft 76 to the charge pump 75 that is fixed to the rear surface of the rear lid portion 72.
[0018]
Further, a sun gear 78 is supported on the motor shaft 77 of the hydraulic transmission mechanism 57 that protrudes into the transmission case 4, and the sun gear 78 is bearing-supported on the front lid 71, and the small-diameter transmission gear 74 is large. The carrier gear 79 having a diameter is always meshed with the boss of the sun gear 78 and the carrier gear 79 is supported on the free rotation shaft. And a ring gear 82 that meshes with the planetary gear 80 is provided, and the planetary gear mechanism 83 is formed by the gears 78, 80, and 82.
[0019]
Further, the sun gear 78 and the rear cover portion 72 are rotatably supported on the front and rear of the combined output shaft 84, and the ring gear 82 is supported on the combined output shaft 84 to be engaged with the hydraulic pump 85 of the hydraulic transmission mechanism 57. And the forward / reverse rotation output, which is a continuously variable hydraulic shift output of the hydraulic motor 86, and the reduced rotation output (one-way constant rotation) of the transmission gear 74 and the carrier gear 79 are combined by the differential action of the planetary gear mechanism 83 to obtain zero. Or transmitted to the combined output shaft 84 as a rotational force in one direction at the maximum speed.
[0020]
Furthermore, a forward gear 87 and a reverse gear 88 are supported on the combined output shaft 84 as idle shafts, and the gears 87 and 88 are selectively engaged with the combined output shaft 84 by a slider 89 to output forward, neutral or reverse. In addition, the rear output shaft 63 is bearing-bearing on the partition wall portion 73 and the rear lid portion 72. In addition, a front output shaft 92 that transmits power to the left and right front axles 91 via a differential gear 90 and a counter shaft 94 that supports the PTO transmission gear 93 are provided. Further, the reverse power of the reverse gear 88 is transmitted to the front output shafts 63 and 92 via the output gears 95 and 96, and the front and rear wheels 6 and 8 are driven to move backward, and the moving gear 97 and the planting gear 98 are connected to the rear output shaft 63. The idler shaft is supported, and the gears 97 and 98 are selectively engaged with the rear output shaft 63 by the auxiliary transmission slider 99.
[0021]
Further, the moving gear 97 is always meshed with the forward gear 87 via the high speed gear 100 of the counter shaft 94, and the planting gear 98 is always meshed with the low speed PTO transmission gear 93 of the counter shaft 94, as shown in FIG. Under this condition, the power of the forward gear 87 is transmitted to the output shafts 63 and 92 through the gears 100, 93 and 98, and the front and rear wheels 6 and 8 are driven forward at the seedling planting work speed. In addition, under the state of FIG. 22, both the moving gear 97 and the planting gear 98 are in an idle state, so that the planting claw 17 and the like can be manually rotated by the operator to remove the clogged seedlings. While enabling manual rotation of the PTO output shaft 64, the power of the forward gear 87 is transmitted to the output shafts 63 and 92 via the gears 100 and 97 under the state of FIG. The front and rear wheels 6 and 8 are driven forward at a high moving speed.
[0022]
Further, as shown in FIG. 11, the power of the PTO transmission gear 93 is transmitted to the PTO output shaft 64 via the PTO transmission shaft 101 and the PTO transmission mechanism 102 to drive the planting portion 15 so as to be able to shift between the stocks. The fertilizer output shaft 104 is connected to the PTO output shaft 64 via the chain 103 installed in the plant, and the fertilizer machine 38 is driven in synchronization with the planting unit 15. Further, as shown in FIG. 12, the transmission case 4 is provided with an oil gauge 105, and as shown in FIG. 13, the sliders 89 and 99 are locked to the same shift fork 106, and the shift lever 28 is switched by five positions. Switch between forward / reverse and sub-shift (low / high speed). Further, as shown in FIGS. 15 to 17, the hydraulic speed change operation arm 109 is connected to the swash plate 107 of the hydraulic pump 85 via the control shaft 108, and the speed change pedal 31 is connected to the arm 109 via the rod 110. The spring 111 for automatically returning the pedal 31 to the stop (zero speed) position when the pedal 31 is released is connected to the arm 109, and the oil damper 112, which is a constant speed operating member, is connected to the arm 109. When the foot is released from the pedal 31 that has been stepped on, the pedal 31 returns at a gentle and substantially constant speed due to the resistance of the oil damper 112 and the return force of the spring 111, and the operation gradually decreases. Instead of the oil damper 112, a constant speed operation member may be formed by a gas spring or the like.
[0023]
Further, as shown in FIG. 24, when the pedal 31 is returned to the stop (zero speed) position by the spring 111 with the foot away from the pedal 31, the sun gear 78 reverses clockwise at the maximum rotation and the planetary gear. At the same time, the carrier gear 79 is rotated by the transmission gear 74 to rotate the planetary gear 80 in the counterclockwise direction, and the planetary gear 80 is rotated in the clockwise direction to rotate counterclockwise. , And the composite output shaft 84 is stopped and maintained. When the pedal 31 is stepped on to the middle position (medium speed range) against the spring 111, the sun gear 78 stops, the carrier gear 79 is rotated by the transmission gear 74, and the planetary gear 80 is rotated clockwise. Then, the combined output shaft 84 is rotated by the gear power of the transmission gear 74. Further, when the pedal 31 is fully depressed, the sun gear 78 rotates in the counterclockwise direction at the maximum rotation, and the planetary gear 80 rotates in the clockwise direction while the carrier gear 79 is rotated in the clockwise direction while rotating in the clockwise direction. The combined output shaft 84 is rotated by adding the hydraulic transmission force from the sun gear 78 and the transmission gear 74 power, and the engine 2 power is transmitted to the transmission gear 74 and the hydraulic transmission mechanism 57 as shown in FIG. The planetary gear mechanism 83 synthesizes and outputs, and the mission case 4 performs forward / reverse switching and PTO speed change to perform reverse, low speed forward (farm planting travel), and high speed forward (road movement travel) operations.
[0024]
Then, for example, with respect to the general input power 100, when the loss of the gear 74 is 2 and the loss of hydraulic shift is 30, the input power of the engine 2 is reduced when traveling at a low speed as shown in FIG. When the hydraulic transmission power is 50 and the hydraulic transmission power 50 returns to the pump shaft 58 and the transmission power on the gear 74 side becomes 150, the loss of the gear 74 is 3, and the hydraulic transmission mechanism 57 is lost. 15 and the output power is obtained at a rate of 82. Further, as shown in FIG. 27, when the vehicle travels at medium speed where the transmission power of the hydraulic transmission mechanism 57 is zero, the transmission power on the gear 74 side is 100, the loss of the gear 74 is 2, and the output power is 98. Obtained in proportion. Further, as shown in FIG. 28, when traveling at high speed, when the hydraulic transmission power is 40 and the transmission power on the gear 74 side is 60, the loss of the gear 74 is 1 and the loss of the hydraulic transmission mechanism 57 is 12. The power is obtained at a ratio of 87. For example, as shown in FIG. 29, by changing the angle of the hydraulic speed change operation arm 109 from −1 to 0 to 1, the motor shaft 77 rotates from −1000 to 0 to 1000 rotations. When the gear 74 side is rotated 1000 times regardless of the angle of the arm 109 as shown in FIG. 30, the composite output shaft 84 is 0 to 0 with respect to the angle of the arm 109 as shown in FIG. The gears 74 and 79 and the planetary gear mechanism 83 are composed so as to have 2000 rotations.
[0025]
Further, when the entire control range of the arm 109 is set to −1 to 0 to 1, as shown in FIG. 18, the control operation on the low speed (zero speed) side and the high speed side of the arm 109 is changed to the bolt type low speed and high speed stopper 113.・ Controlled by 114, and as shown in FIG. 32, the operation range of the actual arm 109 adjustable by the stoppers 113 and 114 is set to −0.8 to 0.6, and the work of 0 to 1.4 m / s is performed. By obtaining the speed, adjustment is made by the stoppers 113 and 114 with respect to variations in output characteristics caused by assembly errors of the hydraulic transmission mechanism 57, and the positions of the arms 109, for example, -1 to -0.8 are adjusted. The speed can be made zero, and the problem that the speed does not become zero even if the arm 109 is −1 is eliminated. As shown in FIGS. 33 and 34, at a general work speed, the power sharing ratio between the hydraulic transmission mechanism 57 and the gear 74 is set to 60% or more, and the effective power on the gear 74 side with respect to the effective power of the hydraulic transmission mechanism 57. Increase the ratio of the paddy field, improve the running performance in the wet field, improve the working efficiency in the wet field, and give the escape level enough for the step of the cultivator.
[0026]
As is clear from the above, a hydraulic transmission mechanism 57 and a transmission gear 74 that transmit the driving force of the engine 2 are provided, and outputs of the hydraulic transmission mechanism 57 and the transmission gear 74 are synthesized to form a transmission output. The output of high power transmission efficiency is obtained by using the hydraulic transmission mechanism, the output of continuously variable transmission capable of zero start is obtained by using the hydraulic transmission mechanism 57, the speed adjustment according to the situation is performed by a simple shift operation, and the speed change function is improved. In addition, the handling operability is improved, and the combined output shaft 84 for synthesizing the outputs of the hydraulic transmission mechanism 57 and the transmission gear 74 by the forward or reverse output of the hydraulic transmission mechanism 57 is used in one direction. To ensure that the output torque at the time of zero start is easily secured, the speed performance is easily improved, and the output of the high power transmission efficiency of the transmission gear 74 is effectively used at the work speed, and the work on the mud road surface efficiency Achieve such improvement.
[0027]
In addition, the transmission gear 74 is formed at a reduction ratio that becomes an intermediate transmission speed between 0 and the maximum vehicle speed, and the operation of the continuously variable transmission capable of zero start is performed, but the output of the transmission gear 74 with high power transmission efficiency is constant. In order to improve the running performance and work efficiency, the ratios of the outputs of the hydraulic transmission mechanism 57 and the transmission gear 74 are substantially equal at the time of start-up, and the large work required for start-up is performed. While ensuring the output torque, the zero-start and slow-speed movement operations are smoothly performed by continuously variable speed operation, for example, ultra-low-speed traveling such as entering / exiting the loading platform of the field or transport truck or traveling over the ridge. To improve.
[0028]
In addition, during low speed or high speed travel other than when starting, continuous operation is performed in which the output ratio of the transmission gear 74 is increased with respect to the hydraulic transmission mechanism 57 and a constant speed is maintained by the output of the transmission gear 74 having high power transmission efficiency. In addition to improving the running performance and work efficiency, switching between forward and reverse rotation of the hydraulic transmission mechanism 57 at the middle of 0 to the maximum vehicle speed or more to ensure the output torque at the time of zero start, In addition, the output of the high power transmission efficiency of the transmission gear 74 is effectively utilized at the work speed, and the work efficiency on the mud road surface is improved.
[0029]
Further, when the transmission ratio of the transmission gear 74 is more than half of the whole, the operation speed is set, and continuous operation is performed to maintain a constant speed by the output of the transmission gear 74 having high power transmission efficiency, thereby improving the running performance and improving the work efficiency. At the same time, the reverse rotation output range of the hydraulic transmission mechanism 57 is made larger than the normal rotation output range between 0 and the maximum vehicle speed, improving the performance of zero start and slow running, and at the transmission speed. The output of 74 high power transmission efficiency is used effectively, and the work efficiency on the mud road surface is improved.
[0030]
Further, the driving force of the engine 2 is input to the pump shaft 58 of the hydraulic transmission mechanism 57, and the motor shaft 77 of the hydraulic transmission mechanism 57 and the transmission gear 74 connected to the pump shaft 58 are connected via the planetary gear mechanism 83. In a work vehicle that is coupled to the combined output shaft 84 and combines and outputs the hydraulic transmission and the transmission gear 74 transmission, the transmission gear 84 is rotated in one direction within the shiftable range of the hydraulic transmission mechanism 57. 74 and a planetary gear mechanism 83 are provided to achieve zero-start continuously variable transmission and high power transmission efficiency with a simple hydraulic transmission and gear composition to improve running performance and transmission operability. The rotation of the combined output shaft 84 is adjusted by the hydraulic speed change operation arm 109 of the mechanism 57, and the combined output shaft 8 is shifted from the maximum operation position on the low speed output side of the operation arm 109 to the high speed output side. The zero rotation position is set, and the output speed of the hydraulic speed change mechanism 57 or the assembly error of the speed change operation mechanism causes a shift between the lowest speed (zero speed) position of the operation arm 109 and the zero rotation position of the composite output shaft 84. Even if it occurs, the problem that the composite output shaft 84 rotates when the operation arm 109 is operated at the lowest speed is eliminated.
[0031]
Further, the output control of the hydraulic transmission mechanism 57 is performed by a one-way operation of the pedal 31 that automatically moves backward, the stepping operation of the pedal 31 causes the hydraulic transmission mechanism 57 to perform a continuously variable transmission operation, and the steering handle 14 with both hands. Operate and freely adjust the speed, for example, the steering handle 14 can be operated with one hand while the shift lever is operated with the other hand, and the conventional troublesome driving is eliminated, and the steering and shifting operability is improved. In addition, the forward / reverse switching gears 87 and 88 and the PTO output gear 93 are provided on the output side of the composite output shaft 84, and the input side of the composite output shaft 84 is combined without cutting the power with a clutch or the like. By simply turning the output shaft 84 to zero, the gears 87, 88, and 93 are switched, eliminating the need for a clutch that interrupts the output of the engine 2, and performing forward / reverse operation or PTO shifting. In addition, the gears 87, 88, 93 are brought close to each other to perform forward / reverse switching and PTO shift using the same operating mechanism, and the installation structure of the gears 87, 88, 93 is made compact and simplified. Etc.
[0032]
【The invention's effect】
As can be seen from the above embodiments, the present invention has a traveling vehicle 1 having front wheels 6 and rear wheels 8 and mounted with an engine 2, a planting portion 15 connected to the traveling vehicle 1, and power from the engine 2. The hydraulic transmission mechanism 57 of a hydraulic pump 85 and a hydraulic motor 86 type that outputs after shifting, the planetary gear mechanism 83 that combines the power from the engine 2 and the transmission output of the hydraulic transmission mechanism 57, and the combined output of the planetary gear mechanism 83 are A transmission case 84 having a composite output shaft 84, a travel output shaft 63, and a PTO output shaft 64 transmitted as a rotational force in one direction, and the rotational force in one direction in the composite output shaft 84 is converted to the travel output shaft 63 and the PTO. A rice transplanter configured to transmit to the output shaft 64, drive the rear wheel 8 with the travel output shaft 63, and drive the planting portion 15 with the PTO output shaft 64, and a hydraulic transmission mechanism 57 shift outputs By controlling the output in the rotation direction, the rotation speed of the combined output shaft 84 becomes zero, and the combined output shaft 84 is configured to be in the maximum rotation state with the shift output of the hydraulic transmission mechanism 57 being the maximum in the forward rotation direction. The composite output shaft 84 includes a forward gear / reverse gear mechanism 4 a that switches the rotational force in one direction of the composite output shaft 84 to forward, neutral, and reverse outputs and transmits the output to the travel output shaft 63.
For this reason, the output torque at the time of zero start can be easily secured, the slow running performance can be easily improved, and the output of the high power transmission efficiency of the transmission gear 74 can be effectively used at the work speed, and the work efficiency on the mud road surface And the stop position (zero speed) of the hydraulic speed change operation and the zero rotation position of the composite output shaft 84 with respect to the output characteristics of the hydraulic speed change mechanism 57 or the assembly error of the speed change operation mechanism. Even if a deviation occurs, it is possible to easily eliminate the problem of the composite output shaft 84 rotating and moving forward and backward when the hydraulic speed change operation 109 is stopped.
[0033]
In addition, a continuously variable transmission capable of starting at zero and a high power transmission efficiency can be easily achieved by a simple hydraulic transmission and gear composition, and it is possible to easily improve running performance and shift operability.
[0034]
[0035]
[Brief description of the drawings]
FIG. 1 is an overall side view of a rice transplanter.
FIG. 2 is an overall plan view of a rice transplanter.
FIG. 3 is a side view of a traveling vehicle body.
FIG. 4 is a plan view of a traveling vehicle body.
FIG. 5 is a side view of the vehicle body frame.
FIG. 6 is an explanatory side view of a drive unit.
FIG. 7 is an explanatory plan view of a drive unit.
FIG. 8 is an explanatory side view of a side clutch operation system.
FIG. 9 is an explanatory plan view of a side clutch operation system.
FIG. 10 is a cross-sectional view of a mission case.
FIG. 11 is an enlarged view of the same.
FIG. 12 is an explanatory diagram of a planetary gear mechanism.
FIG. 13 is a partial view of a mission case.
FIG. 14 is a cross-sectional view of a planetary gear mechanism.
FIG. 15 is a perspective view from the front of the shift pedal portion.
FIG. 16 is a perspective view from the upper rear side of the shift pedal portion.
FIG. 17 is an explanatory diagram of a gear arrangement of a mission case.
FIG. 18 is a side view of a hydraulic speed change operation arm portion.
FIG. 19 is an explanatory diagram of a neutral state of gear shifting.
FIG. 20 is an explanatory view of a reverse state of gear shifting.
FIG. 21 is an explanatory view of a gear shifting planting traveling state.
FIG. 22 is an explanatory diagram of a PTO idling state in gear shifting.
FIG. 23 is an explanatory diagram of a moving traveling state of gear shifting.
FIG. 24 is an explanatory diagram of rotation of the planetary gear mechanism.
FIG. 25 is an explanatory diagram of engine output.
FIG. 26 is an explanatory diagram of engine output at low speed running.
FIG. 27 is an explanatory diagram of engine output for medium speed running.
FIG. 28 is an explanatory diagram of engine output at high speed.
FIG. 29 is an explanatory diagram of an output of the hydraulic transmission mechanism.
FIG. 30 is an explanatory diagram of output on the transmission gear side.
FIG. 31 is an explanatory diagram of output of a composite output shaft.
FIG. 32 is an explanatory diagram showing a shift of the shift pedal.
FIG. 33 is a correlation diagram between a hydraulic shift output and a gear shift output.
FIG. 34 is a correlation diagram between the output of FIG. 33, hydraulic pressure loss, and gear loss.
[Explanation of symbols]
2 Engine 31 Shift pedal 57 Hydraulic transmission mechanism 58 Pump shaft 74 Transmission gear 77 Motor shaft 83 Planetary gear mechanism 84 Composite output shaft 87 Forward gear 88 Reverse gear 93 PTO transmission gear 109 Hydraulic transmission operation arm

Claims

A traveling vehicle having front and rear wheels and mounted with an engine; a planting unit coupled to the traveling vehicle; a hydraulic pump / hydraulic motor type hydraulic transmission mechanism that shifts and outputs power from the engine; A planetary gear mechanism that combines power from the engine and a shift output of the hydraulic transmission mechanism; a combined output shaft that transmits the combined output of the planetary gear mechanism as a one-way rotational force; a travel output shaft; and a PTO output shaft. A mission case with
A rotational force in one direction in the combined output shaft is transmitted to the travel output shaft and the PTO output shaft, the rear wheel is driven by the travel output shaft, and the planting portion is driven by the PTO output shaft. A rice transplanter configured to drive
While configuring the output speed of the hydraulic transmission mechanism in the reverse rotation direction so that the rotational speed of the combined output shaft becomes zero,
The composite output shaft is provided with a forward gear / reverse gear mechanism that switches a rotational force in one direction of the composite output shaft to forward, neutral, and reverse outputs and transmits the output to the travel output shaft. Rice transplanter.