JP4988111B2

JP4988111B2 - Combine

Info

Publication number: JP4988111B2
Application number: JP2001299314A
Authority: JP
Inventors: 茂實日高
Original assignee: Yanmar Co Ltd
Current assignee: Yanmar Co Ltd
Priority date: 2001-09-28
Filing date: 2001-09-28
Publication date: 2012-08-01
Anticipated expiration: 2021-09-28
Also published as: JP2003104075A

Description

【０００１】
【発明の属する技術分野】
本発明は例えば刈取部及び脱穀部を備えて連続的に穀稈を刈取って脱穀処理するコンバインに関する。
【０００２】
【発明が解決しようとする課題】
従来、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。そこでコンバインなど作業車において、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るもので、そのため油圧変速機構に遊星ギヤ機構を組合せて油圧変速機構単体使用での動力損失など無くして、油圧を用いた場合の操作性とギヤ（機構）を用いた場合の高い伝達効率と両立させた複合変速機構を形成する手段がある。
【０００３】
しかし乍ら、従来この複合変速機構にあっては油圧変速機構を構成する油圧ポンプに可変容量形を用い油圧モータに定容量形を用いて、油圧ポンプの斜板を操作する操作アームが−１から中立を介し＋１まで変化させるときに、複合変速機構の出力を０回転から最高回転まで変化させる関係とさせると共に、この複合変速機構の出力を正逆転切換機構で正逆に切換えて、前進及び後進で走行を行う構成とするため、別途正逆転切換機構の設置を必要とするなどの構造上の複雑さがあるばかりでなく、前後進時には前後進操作レバーなどで正逆転切換機構をその都度切換動作させるなどの操作上の煩わしさがあった。
【０００４】
【課題を解決するための手段】
したがって、請求項１に係る発明は、エンジンの駆動力を伝える油圧変速機構と伝達ギヤの各出力を合成して変速出力する複合変速機構を備え、１組の油圧ポンプ及び油圧モータにて前記油圧変速機構を形成し、油圧ポンプのポンプ軸をエンジンに連結させて、エンジン出力を油圧変速機構に伝達させると共に、油圧ポンプの斜板角制御によって複合変速機構の合成出力軸を一方向に変速回転させるコンバインにおいて、前記油圧モータのモータ軸にサンギヤを係合軸支させ、前記ポンプ軸にキャリヤギヤを連結させ、前記キャリヤギヤにプラネタリギヤを回転自在に設け、前記サンギヤにプラネタリギヤを噛合させ、前記プラネタリギヤに噛合させるリングギヤを設け、前記合成出力軸に前記リングギヤを係合軸支させ、前記油圧ポンプ及び油圧モータの無段油圧変速出力と、前記キャリヤギヤの回転出力とを合成し、ゼロ乃至最大速の一方向の回転力として前記合成出力軸に伝えるように構成し、前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角を最大逆転角にした場合は、前記合成出力軸における一方向の回転力がゼロになり、前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角をゼロにした場合は、前記合成出力軸における一方向の回転力が前進方向の最高効率状態になるように構成しているものであるから、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向上させ、しかも負荷の大きい作業においても高い動力伝達効率の出力を有効に利用して作業能率の向上など容易に図るものである。
【０００５】
また、請求項２に係る発明は、請求項１に記載のコンバインにおいて、前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角を最大正転角にした場合は、前記合成出力軸における一方向の回転力が前進最高速状態になるように構成しているものであるから、油圧ポンプの斜板角を操作する簡単な操作で、前記合成出力軸を一方向（正転）に変速回転させて、前進走行でのスムーズ且つ容易な変速などを可能にするものである。
【０００６】
【０００７】
【０００８】
【発明の実施の形態】
以下、本発明の実施例を図面に基づいて詳述する。図１はコンバインの全体側面図、図２は同平面図であり、図中１は左右一対の走行部材である走行クローラ２を装設するトラックフレーム、３は前記トラックフレーム１に架設する機台、４はフィードチェン５を左側に張架し扱胴６及び処理胴７を内蔵している脱穀部、８は刈刃９及び穀稈搬送機構１０などを備える刈取部、１１は刈取フレーム１２を介して刈取部８を昇降させる油圧シリンダ、１３は排藁チェン１４終端を臨ませる排藁処理部、１５は脱穀部４からの穀粒を揚穀筒１６を介して搬入する穀物タンク、１７は前記タンク１５の穀粒を機外に搬出する排出オーガ、１８は丸形操向ハンドル１９及び運転席２０などを備える運転台、２１は運転席２０下方に設けるエンジンであり、連続的に穀稈を刈取って脱穀するように構成している。
【０００９】
また、図中２２は走行クローラ２を駆動するミッションケース、２３は運転台１８左側に設けるサイドコラムであり、主変速レバー２４・副変速レバー２５・刈取クラッチレバー２６・脱穀クラッチレバー２７をサイドコラム２３に設けている。
【００１０】
図３、図４に示す如く、前記ミッションケース２２の一側に可変容量形油圧ポンプ２８及び油圧モータ２９で形成する１組の無段油圧変速機構３０を設け、該変速機構３０の変速入力用ポンプ軸３１をエンジン２に連結させて、エンジン２出力を油圧変速機構３０に伝達させると共に、ミッションケース２２内に突出させるポンプ軸３１に小径の伝達ギヤ３２を係合軸支させ、ＰＴＯ出力プーリ３３を有するＰＴＯ出力軸３４に伝達ギヤ３２の動力を伝えるように構成している。
【００１１】
また、前記ミッションケース２２内に突出させる油圧変速機構３０のモータ軸３５にサンギヤ３６を係合軸支させ、前記の小径の伝達ギヤ３２に大径のキャリヤギヤ３７を常に噛合させ、サンギヤ３６のボス部にキャリヤギヤ３７を遊転軸支させるもので、キャリヤギヤ３７に３枚のプラネタリギヤ３８を軸３９を介して回転自在に設け、サンギヤ３６にプラネタリギヤ３８を噛合させると共に、プラネタリギヤ３８に噛合させるリングギヤ４０を設け、各ギヤ３６・３８・４０によって遊星ギヤ機構４１を形成する。
【００１２】
さらに、前記サンギヤ３６とミッションケース２２に合成出力軸４２の両端を回転自在に軸支させ、前記リングギヤ４０を合成出力軸４２に係合軸支させるもので、図１１乃至図１３に示す如く油圧変速機構３０の油圧ポンプ２８及び油圧モータ２９の無段油圧変速出力である正逆回転出力と、伝達ギヤ３２及びキャリヤギヤ３７の回転出力（一方向の一定回転）とを、遊星ギヤ機構４１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４２に伝える。
【００１３】
また、前記合成出力軸４２を１対のギヤ４３を介して副変速ギヤ軸４４に連結させると共に、副変速ギヤ部４４ａを構成する１対の低速ギヤ４５及び高速ギヤ４６を介して駐車ブレーキ４７を有する駐車ブレーキ軸４８に副変速ギヤ軸４４を連結させ、左右サイドクラッチ４９・５０を有する左右サイドクラッチ軸５１・５２、左右伝達軸５３・５４を介して左右前車軸５５・５６に駐車ブレーキ軸４８を連結させて、走行クローラ２の駆動スプロケット５７を駆動して車体の前後進及び左右旋回を行うように構成している。
【００１４】
そして図３、図５乃至図９に示す如く、前記油圧ポンプ２８及び油圧モータ２９の斜板５８・５９に制御軸６０・６１を介して油圧変速操作アーム６２・６３を連結させ、該アーム６２・６３をロッドなどを介し主変速レバー２４に連結させて、主変速レバー２４の操作でもって斜板５８・５９の傾斜角を変更して合成出力軸４２の回転制御を行うように構成している。
【００１５】
そして、主変速レバー２４を中立位置Ｎと前進最高速位置Ｆ２間で操作する場合には、油圧モータ２９の斜板５９の傾斜角θａを一定保持させた状態で油圧ポンプ２８の斜板５８の傾斜角のみを最大逆転角−αから最大正転角＋α間で変化させて車体の移動速度を０から最高速度Ｖ２まで変速させる前進走行を行う一方、主変速レバー２４を中立位置Ｎと後進最高速位置Ｒ間で操作する場合には、油圧ポンプ２８の斜板５８の傾斜角を最大逆転角−αに保った状態で、油圧モータ２９の斜板５９のみを一定傾斜角θａと低速側（斜板５９を立てる方向）の一定傾斜角θｂとの間で変化させて車速の移動速度を０から最高速度Ｖ１まで変速させる後進走行を行う。
【００１６】
つまり、図５、図９に示す如く、主変速レバー２４を中立位置Ｎに操作し、油圧ポンプ２８斜板５８を傾斜角−α、油圧モータ２９斜板５９を傾斜角θａで油圧変速機構３０を駆動するとき、図１０（１）に示す如く、サンギヤ３６は最高回転で時計回りに逆転してプラネタリギヤ３８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３２によってキャリヤギヤ３７を回転させることにより、プラネタリギヤ３８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４０の回転をゼロにし、合成出力軸４２を停止維持する（図９のＡ位置、移動速度は０）。
【００１７】
また図６に示す如く、主変速レバー２４を前進１速位置Ｆ１に操作し、油圧ポンプ２８の斜板５８を傾斜角０（立設状態）、油圧モータ２９の斜板５９を傾斜角θａで油圧変速機構３０を駆動するとき、図１０（２）に示す如く、サンギヤ３６は停止し、伝達ギヤ３２によってキャリヤギヤ３７を回転させ、プラネタリギヤ３８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３２のギヤ動力により合成出力軸４２を回転させる（図９のＢ位置、移動速度は前進Ｖ１位置で、最高効率状態）。
【００１８】
さらに図７に示す如く、主変速レバー２４を前進２速位置Ｆ２に操作し、油圧ポンプ２８の斜板５８を傾斜角＋αで油圧モータ２９の斜板５９を傾斜角θａで油圧変速機構３０を駆動するとき、図１０（３）に示す如く、サンギヤ３６は最高回転で反時計回りに正転し、プラネタリギヤ３８を時計方向に自転させ乍ら伝達ギヤ３２でキャリヤギヤ３７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３６からの油圧変速力と伝達ギヤ３２動力を加算して合成出力軸４２を回転させる（図９のＣ位置、移動速度は前進Ｖ２位置で、最高速状態）。
【００１９】
また図８に示す如く、主変速レバー２４を後進位置Ｒに操作し、油圧ポンプ２８の斜板５８を傾斜角−αで油圧モータ２９の斜板５９を傾斜角θｂ（θｂ＜θａ）で油圧変速機構３０を駆動するとき、図１０（１）の状態より油圧モータ２９（サンギヤ３６）の回転が減速し、合成出力軸４２の回転は前進時の正転状態より逆転する（図９のＤ位置、移動速度は後進Ｖ１位置で後進走行状態）。
【００２０】
そして、例えば、一般的な入力動力１００に対して、ギヤ３２の損失が２で、油圧変速の損失が３０の条件下において、図１４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３１に戻ってギヤ３２側の伝達動力が１５０になると、ギヤ３２の損失が３で、油圧変速機構３０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１５のように、前記油圧変速機構３０の伝達動力をゼロにする中速で走行時、ギヤ３２側の伝達動力が１００になり、ギヤ３２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１６のように、高速で走行時、油圧伝達動力が４０で、ギヤ３２側の伝達動力が６０の場合、ギヤ３２の損失が１で、油圧変速機構３０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、油圧モータ操作アーム６３の角度を設定に保ち、例えば、図１１のように、油圧ポンプ変速操作アーム６２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３５が−Ｎ乃至０乃至＋Ｎ回転になるようにし、図１２のように、前記アーム６２の角度に関係なくギヤ３２側をＮ回転させた場合、図１３のように、前記アーム６２の角度に対して合成出力軸４２が０乃至２Ｎ回転になるように、ギヤ３２・３７及び遊星ギヤ機構４１を組成して車体を前進走行させるように構成している。
【００２１】
また、油圧ポンプ操作アーム６２の角度が−１状態で、油圧モータ操作アーム６３の角度を設定より中立側に戻すとき、合成出力軸４２が逆転し０乃至Ｎ回転となるように設けて、車体を後進走行させるように構成している。
【００２２】
以上からも明らかなように、エンジン２の駆動力を伝える油圧変速機構３０と伝達ギヤ３２の各出力を合成して変速出力する複合変速機構６４を備えた作業車において、１組の可変容量形の油圧ポンプ２８及び油圧モータ２９で油圧変速機構３０を形成し、油圧ポンプ２８の斜板５８角制御によって複合変速機構６４の合成出力軸４２を正転方向に変速回転させると共に、油圧モータ２９の斜板５９角制御によって複合変速機構６４の合成出力軸４２を逆転方向に変速回転させるように設けたことによって、別途複雑な前後進切換機構（正逆転切換機構）など設ける必要なく可変容量形油圧モータ２９の斜板５９を調節するレバー或いはペダルの簡単な操作で前後進の切換えを容易に行うと共に、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向上させ、しかも負荷の大きい作業においても高い動力伝達効率の出力を有効に利用して作業能率の向上など容易に図ることができる。
【００２３】
また、油圧モータ２９の斜板５８角を一定保持させ、油圧ポンプ２８の斜板５８角を正逆に制御して複合変速機構６４の合成出力軸４２を正転方向で変速回転させることによって、油圧ポンプ２８の斜板５８角を単一のレバーなどによって操作するだけでの簡単な操作で合成出力軸４２を一方向（正転）に変速回転させて、前進走行でのスムーズ且つ容易な変速などを容易に可能とさせることができる。
【００２４】
さらに、油圧ポンプ２８の斜板５８角を逆転側最大出力位置（合成出力軸４２が０回転）に保持させ、油圧モータ２９の斜板５８角を設定より中立側に制御して、複合変速機構６４の合成出力軸４２を逆転方向で変速回転させることによって、油圧モータ２９の斜板５８角を単一のレバーなどによって操作するだけの簡単な操作で合成出力軸４２の反対側一方向（逆転）に変速回転させて、後進走行でのスムーズ且つ容易な変速などを容易に可能とさせることができる。
【００２５】
また、油圧ポンプ２８の斜板５８角制御で前進での走行変速を行うと共に、油圧モータ２９の斜板５８角制御で後進での走行変速を行うことによって、１組の油圧ポンプ２８及び油圧モータ２９からなる油圧変速機構３０のみを用いて、ゼロ発進や効率良好な出力などを確保した前後進走行を容易に可能とさせて、走行性能を向上させることができる。
【００２６】
【発明の効果】
以上実施例から明らかなように、請求項１に係る発明は、エンジン２の駆動力を伝える油圧変速機構３０と伝達ギヤ３２の各出力を合成して変速出力する複合変速機構６４を備え、１組の油圧ポンプ２８及び油圧モータ２９にて前記油圧変速機構３０を形成し、油圧ポンプ２８のポンプ軸３１をエンジン２に連結させて、エンジン２出力を油圧変速機構３０に伝達させると共に、油圧モータ２９の斜板５９角制御によって複合変速機構６４の合成出力軸４２を一方向に変速回転させるコンバインにおいて、前記油圧モータのモータ軸３５にサンギヤ３６を係合軸支させ、ポンプ軸３１にキャリヤギヤ３７を連結させ、キャリヤギヤ３７にプラネタリギヤ３８を回転自在に設け、サンギヤ３６にプラネタリギヤ３８を噛合させ、プラネタリギヤ３８に噛合させるリングギヤ４０を設け、前記合成出力軸４２にリングギヤ４０を係合軸支させ、油圧ポンプ２８及び油圧モータ２９の無段油圧変速出力と、キャリヤギヤ３７の回転出力とを合成し、ゼロ乃至最大速の一方向の回転力として合成出力軸４２に伝えるように構成し、油圧モータ２９の斜板５９の傾斜角θａを一定保持させた状態で油圧ポンプ２８の斜板５８の傾斜角を最大逆転角−αにした場合は、合成出力軸４２における一方向の回転力がゼロになり、油圧モータ２９の斜板５９の傾斜角θａを一定保持させた状態で油圧ポンプ２８の斜板５８の傾斜角をゼロにした場合は、合成出力軸４２における一方向の回転力が前進方向の最高効率状態Ｖ１になるように構成しているものであるから、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向上させ、しかも負荷の大きい作業においても高い動力伝達効率の出力を有効に利用して作業能率の向上など容易に図ることができるものである。
【００２７】
また、請求項２に係る発明は、油圧モータ２９の斜板５９の傾斜角θａを一定保持させた状態で油圧ポンプ２８の斜板５８の傾斜角を最大正転角＋αにした場合は、合成出力軸４２における一方向の回転力が前進最高速状態Ｖ２になるように構成しているものであるから、油圧ポンプ２８の斜板５８角を操作する簡単な操作で、前記合成出力軸４２を一方向（正転）に変速回転させて、前進走行でのスムーズ且つ容易な変速などを容易に可能にできるものである。
【００２８】
【００２９】
【図面の簡単な説明】
【図１】コンバインの全体側面図。
【図２】コンバインの全体平面図。
【図３】走行駆動系の説明図。
【図４】遊星ギヤ機構部の説明図。
【図５】合成出力軸の０回転状態を示す説明図。
【図６】合成出力軸の最高効率回転状態を示す説明図。
【図７】合成出力軸の最高回転状態を示す説明図。
【図８】合成出力軸の回転状態を示す説明図。
【図９】主変速レバーと油圧変速機構との関係を示す説明図。
【図１０】遊星ギヤ機構の回転説明図。
【図１１】油圧変速機構の出力説明図。
【図１２】伝達ギヤ側の出力説明図。
【図１３】合成出力軸の出力説明図。
【図１４】低速走行のエンジン出力説明図。
【図１５】中速走行のエンジン出力説明図。
【図１６】高速走行のエンジン出力説明図。
【符号の説明】
２エンジン
２８油圧ポンプ
２９油圧モータ
３０油圧変速機構
３２伝達ギヤ
５８斜板
５９斜板
６４複合変速機構[0001]
BACKGROUND OF THE INVENTION
The present invention relates to the Konbai down to threshing process harvests continuously culms comprise e.g. reaper and threshing unit.
[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. Therefore, work vehicles such as combiners require smooth entry / exit of the field, shifting operation with less shock, starting operation that does not require a clutch, speed adjustment adapted to the situation such as work or the surface, etc., high power transmission efficiency, and zero start A continuously variable transmission that is possible and a simple gear shifting operation are desired. Therefore, the operability when using hydraulic pressure without the power loss due to the combined use of the planetary gear mechanism with the hydraulic transmission mechanism and the use of the hydraulic transmission mechanism alone There is a means for forming a complex transmission mechanism that is compatible with high transmission efficiency when a gear (mechanism) is used.
[0003]
However, in this conventional complex transmission mechanism, a variable displacement type is used for the hydraulic pump constituting the hydraulic transmission mechanism and a constant displacement type is used for the hydraulic motor, and an operation arm for operating the swash plate of the hydraulic pump is −1. When changing from neutral to +1, the output of the combined transmission mechanism is changed from 0 to the maximum rotation, and the output of the combined transmission mechanism is switched between forward and reverse by the forward / reverse switching mechanism to move forward and backward. In addition to the structural complexity of requiring a separate forward / reverse switching mechanism, the forward / reverse switching mechanism is required for each forward / reverse operation lever during forward / backward travel. There was a troublesome operation such as switching operation.
[0004]
[Means for Solving the Problems]
Accordingly, the invention comprises a composite transmission mechanism to shift output of each output of the hydraulic transmission mechanism for transmitting the driving force of the engine transmission gear synthesized and the hydraulic in the set of hydraulic pump and the hydraulic motor according to claim 1 A transmission mechanism is formed, the pump shaft of the hydraulic pump is connected to the engine, the engine output is transmitted to the hydraulic transmission mechanism, and the combined output shaft of the composite transmission mechanism is rotated in one direction by controlling the swash plate angle of the hydraulic pump. In the combine, the sun gear is engaged with the motor shaft of the hydraulic motor, the carrier gear is connected to the pump shaft, the planetary gear is rotatably provided on the carrier gear, the planetary gear is engaged with the sun gear, and the planetary gear is engaged. A ring gear for engaging the ring gear with the combined output shaft, A stepless hydraulic speed change output of the hydraulic motor, by combining the rotational output of the carrier gear, and configured to communicate to said composite output shaft as a one-way rotational force of zero to maximum speed, the inclination of the swash plate of the hydraulic motor When the inclination angle of the swash plate of the hydraulic pump is set to the maximum reversal angle while keeping the angle constant, the rotational force in one direction on the combined output shaft becomes zero, and the inclination angle of the swash plate of the hydraulic motor When the inclination angle of the swash plate of the hydraulic pump is set to zero while the pressure is held constant, the rotational force in one direction on the combined output shaft is configured to be in the maximum efficiency state in the forward direction. some because the output torque at zero start easily secured to improve the fine speed driving performance, yet those achieved such facilitate effectively improve work efficiency by using the output of the high power transmission efficiency even in a large work load is there.
[0005]
According to a second aspect of the present invention, in the combine according to the first aspect, the inclination angle of the swash plate of the hydraulic pump is set to the maximum normal rotation angle while the inclination angle of the swash plate of the hydraulic motor is kept constant. In this case, since the rotational force in one direction on the composite output shaft is configured to be in the forward maximum speed state, the composite output shaft can be easily operated by operating the swash plate angle of the hydraulic pump. Is rotated in one direction (forward rotation) to enable smooth and easy gear shifting in forward travel.
[0006]
[0007]
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings. 1 is an overall side view of a combine, and FIG. 2 is a plan view thereof. In FIG. 1, 1 is a track frame on which a traveling crawler 2 as a pair of left and right traveling members is installed, and 3 is a machine base installed on the track frame 1 Reference numeral 4 denotes a threshing section that stretches the feed chain 5 on the left side and incorporates a handling cylinder 6 and a processing cylinder 7; 8, a reaping section that includes a cutting blade 9 and a culm conveying mechanism 10; and 11, a reaping frame 12. A hydraulic cylinder that raises and lowers the mowing unit 8 through 13, a waste disposal processing unit 13 that faces the end of the waste chain 14, 15 a grain tank that carries the grain from the threshing unit 4 through the milling cylinder 16, and 17 A discharge auger for unloading the grains in the tank 15, 18 is a driver's cab provided with a round steering handle 19 and a driver's seat 20, and 21 is an engine provided below the driver's seat 20. Configured to cut and thresh There.
[0009]
In the figure, 22 is a transmission case for driving the traveling crawler 2, and 23 is a side column provided on the left side of the cab 18. The main transmission lever 24, auxiliary transmission lever 25, mowing clutch lever 26, and threshing clutch lever 27 are connected to the side column. 23.
[0010]
As shown in FIGS. 3 and 4, a set of continuously variable hydraulic transmission mechanism 30 formed of a variable displacement hydraulic pump 28 and a hydraulic motor 29 is provided on one side of the transmission case 22. The pump shaft 31 is connected to the engine 2 so that the output of the engine 2 is transmitted to the hydraulic transmission mechanism 30, and the transmission shaft 32 having a small diameter is supported on the pump shaft 31 that protrudes into the transmission case 22, and the PTO output pulley The power of the transmission gear 32 is transmitted to a PTO output shaft 34 having 33.
[0011]
Further, a sun gear 36 is engaged with a motor shaft 35 of a hydraulic transmission mechanism 30 that protrudes into the transmission case 22, and a large-diameter carrier gear 37 is always engaged with the small-diameter transmission gear 32. The carrier gear 37 is supported on a rotating shaft, and three planetary gears 38 are rotatably provided on the carrier gear 37 via a shaft 39. The planetary gear 38 is engaged with the sun gear 36 and the ring gear 40 is engaged with the planetary gear 38. The planetary gear mechanism 41 is formed by the gears 36, 38, and 40.
[0012]
Further, both ends of the composite output shaft 42 are rotatably supported by the sun gear 36 and the transmission case 22, and the ring gear 40 is rotatably supported by the composite output shaft 42. As shown in FIGS. A forward / reverse rotation output, which is a continuously variable hydraulic shift output of the hydraulic pump 28 and the hydraulic motor 29 of the transmission mechanism 30, and a rotation output (constant rotation in one direction) of the transmission gear 32 and the carrier gear 37 are used as the differential of the planetary gear mechanism 41. It is synthesized by action and transmitted to the synthesized output shaft 42 as a rotational force in one direction from zero to the maximum speed.
[0013]
The combined output shaft 42 is connected to the auxiliary transmission gear shaft 44 through a pair of gears 43, and the parking brake 47 is connected through a pair of low-speed gear 45 and high-speed gear 46 constituting the auxiliary transmission gear portion 44a. The auxiliary transmission gear shaft 44 is connected to a parking brake shaft 48 having a left and right side clutch shafts 51 and 52 having left and right side clutches 49 and 50, and left and right front axles 55 and 56 via left and right transmission shafts 53 and 54. The shaft 48 is connected to drive the drive sprocket 57 of the traveling crawler 2 so that the vehicle body moves forward and backward and turns left and right.
[0014]
As shown in FIGS. 3 and 5 to 9, hydraulic shift operation arms 62 and 63 are connected to the swash plates 58 and 59 of the hydraulic pump 28 and the hydraulic motor 29 via control shafts 60 and 61, respectively. -63 is connected to the main speed change lever 24 via a rod or the like, and the rotation angle of the swash plates 58 and 59 is changed by the operation of the main speed change lever 24 to control the rotation of the composite output shaft 42. Yes.
[0015]
When the main transmission lever 24 is operated between the neutral position N and the forward maximum speed position F2, the inclination angle θa of the swash plate 59 of the hydraulic motor 29 is kept constant and the swash plate 58 of the hydraulic pump 28 is maintained. Only the inclination angle is changed from the maximum reverse rotation angle -α to the maximum forward rotation angle + α to perform forward traveling in which the moving speed of the vehicle body is changed from 0 to the maximum speed V2, while the main transmission lever 24 is set to the neutral position N and the reverse maximum. When operating between the high speed positions R, only the swash plate 59 of the hydraulic motor 29 is kept at a constant inclination angle θa and a low speed side (with the inclination angle of the swash plate 58 of the hydraulic pump 28 kept at the maximum reverse rotation angle −α. The vehicle travels backward to change the moving speed of the vehicle speed from 0 to the maximum speed V1 by changing the angle between the swash plate 59 and the constant inclination angle θb.
[0016]
That is, as shown in FIGS. 5 and 9, the main transmission lever 24 is operated to the neutral position N, the hydraulic pump 28 swash plate 58 is inclined at −α, and the hydraulic motor 29 swash plate 59 is inclined at the inclination angle θa. 10 (1), the sun gear 36 rotates in the clockwise direction at the maximum rotation and rotates the planetary gear 38 counterclockwise. At the same time, the carrier gear 37 is moved by the transmission gear 32. By rotating, the planetary gear 38 is revolved clockwise to rotate counterclockwise, the rotation of the ring gear 40 is made zero, and the combined output shaft 42 is stopped and maintained (position A, moving speed in FIG. 9). Is 0).
[0017]
Further, as shown in FIG. 6, the main transmission lever 24 is operated to the first forward speed position F1, the swash plate 58 of the hydraulic pump 28 is tilted at an inclination angle 0 (upright state), and the swash plate 59 of the hydraulic motor 29 is tilted at an inclination angle θa. When the hydraulic transmission mechanism 30 is driven, as shown in FIG. 10 (2), the sun gear 36 is stopped, the carrier gear 37 is rotated by the transmission gear 32, and the planetary gear 38 is rotated in the clockwise direction while rotating in the clockwise direction. The combined output shaft 42 is rotated by the gear power of the transmission gear 32 (position B in FIG. 9, the moving speed is the forward V1 position and the maximum efficiency state).
[0018]
Further, as shown in FIG. 7, the main transmission lever 24 is operated to the forward second speed position F2, and the swash plate 58 of the hydraulic pump 28 is set to the inclination angle + α and the swash plate 59 of the hydraulic motor 29 is set to the inclination angle θa. When driving, as shown in FIG. 10 (3), the sun gear 36 rotates in the counterclockwise direction at the maximum rotation, the planetary gear 38 rotates in the clockwise direction, and the carrier gear 37 is rotated in the clockwise direction while rotating in the clockwise direction. , And the combined output shaft 42 is rotated by adding the hydraulic transmission force from the sun gear 36 and the power of the transmission gear 32 (position C in FIG. 9, the moving speed is the forward V2 position, the highest speed state).
[0019]
Further, as shown in FIG. 8, the main transmission lever 24 is operated to the reverse position R, and the swash plate 58 of the hydraulic pump 28 is hydraulically inclined at an inclination angle -α and the swash plate 59 of the hydraulic motor 29 is hydraulically inclined at an inclination angle θb (θb <θa). When the speed change mechanism 30 is driven, the rotation of the hydraulic motor 29 (sun gear 36) is decelerated from the state of FIG. 10 (1), and the rotation of the composite output shaft 42 is reversed from the normal rotation state during forward movement (D in FIG. 9). The position and moving speed are in the reverse travel state at the reverse V1 position).
[0020]
And, for example, with respect to the general input power 100, 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 31 and the transmission power on the gear 32 side becomes 150, the loss of the gear 32 is 3, and the hydraulic transmission mechanism 30 is lost. 15 and the output power is obtained at a rate of 82. Further, as shown in FIG. 15, when the vehicle travels at a medium speed where the transmission power of the hydraulic transmission mechanism 30 is zero, the transmission power on the gear 32 side is 100, the loss of the gear 32 is 2, and the output power is 98. Obtained in proportion. Further, as shown in FIG. 16, when traveling at high speed, when the hydraulic transmission power is 40 and the transmission power on the gear 32 side is 60, the loss of the gear 32 is 1, the loss of the hydraulic transmission mechanism 30 is 12, and the output The power is obtained at a ratio of 87, and the angle of the hydraulic motor operation arm 63 is maintained at a set value. For example, the angle of the hydraulic pump speed change operation arm 62 is changed from −1 to 0 to 1 as shown in FIG. Thus, when the motor shaft 35 is rotated from -N to 0 to + N and the gear 32 side is rotated N times regardless of the angle of the arm 62 as shown in FIG. The gears 32 and 37 and the planetary gear mechanism 41 are composed so that the vehicle body travels forward so that the combined output shaft 42 rotates 0 to 2N with respect to an angle of 62.
[0021]
In addition, when the angle of the hydraulic pump operation arm 62 is −1 and the angle of the hydraulic motor operation arm 63 is returned to the neutral side from the setting, the composite output shaft 42 is reversely rotated so that 0 to N rotations are provided. Is configured to travel backward.
[0022]
As is clear from the above, in a work vehicle including a composite transmission mechanism 64 that combines the outputs of the hydraulic transmission mechanism 30 for transmitting the driving force of the engine 2 and outputs of the transmission gear 32 to output the transmission, a set of variable displacement type The hydraulic transmission mechanism 30 is formed by the hydraulic pump 28 and the hydraulic motor 29, and the combined output shaft 42 of the composite transmission mechanism 64 is shifted in the normal rotation direction by the swash plate 58 angle control of the hydraulic pump 28. By providing the combined output shaft 42 of the composite speed change mechanism 64 so as to shift and rotate in the reverse direction by swash plate 59 angle control, there is no need to separately provide a complicated forward / reverse switching mechanism (forward / reverse switching mechanism). A simple operation of a lever or pedal that adjusts the swash plate 59 of the motor 29 makes it easy to switch between forward and backward movements, and easily secures output torque at the time of zero start, which is very slow. Improve line performance, yet it is possible to achieve such facilitate effectively improve work efficiency by using the output of the larger high in work efficiency of power transmission load.
[0023]
Further, the swash plate 58 angle of the hydraulic motor 29 is kept constant, the swash plate 58 angle of the hydraulic pump 28 is controlled to be forward and reverse, and the combined output shaft 42 of the composite transmission mechanism 64 is rotated in the forward direction. Smooth and easy shifting in forward travel by rotating the composite output shaft 42 in one direction (forward rotation) with a simple operation simply by operating the 58 swash plate angle of the hydraulic pump 28 with a single lever or the like. Etc. can be easily made possible.
[0024]
Further, the swash plate 58 angle of the hydraulic pump 28 is held at the reverse rotation side maximum output position (the combined output shaft 42 rotates 0 times), and the swash plate 58 angle of the hydraulic motor 29 is controlled to the neutral side from the setting, thereby combining the composite transmission mechanism. By rotating the 64 composite output shafts 42 in the reverse rotation direction, the swash plate 58 angle of the hydraulic motor 29 can be operated in one direction opposite to the composite output shaft 42 (reverse rotation) by a simple operation such as a single lever. ), The smooth and easy shifting in the reverse traveling can be easily performed.
[0025]
In addition, a forward traveling shift is performed by the swash plate 58 angle control of the hydraulic pump 28, and a backward traveling shift is performed by the swash plate 58 angle control of the hydraulic motor 29, whereby one set of the hydraulic pump 28 and the hydraulic motor. By using only the hydraulic transmission mechanism 30 comprising 29, it is possible to easily perform forward / reverse traveling with zero start, efficient output, etc., and to improve traveling performance.
[0026]
【Effect of the invention】
As apparent from the above embodiments, the invention according to claim 1, comprising a composite transmission mechanism 64 to shift output Each output combined with the hydraulic mechanism 30 and the transmission gear 32 for transmitting the driving force of the engine 2, 1 The hydraulic transmission mechanism 30 is formed by a pair of the hydraulic pump 28 and the hydraulic motor 29, the pump shaft 31 of the hydraulic pump 28 is connected to the engine 2, the engine 2 output is transmitted to the hydraulic transmission mechanism 30, and the hydraulic motor in combine to shift rotate the combined output shaft 42 of the composite transmission mechanism 64 in one direction by the swash plate 59 angle control 29, the sun gear 36 is engaging shaft supported on the motor shaft 35 of the hydraulic motor, the carrier gear 37 to the pump shaft 31 , The planetary gear 38 is rotatably provided on the carrier gear 37, the planetary gear 38 is engaged with the sun gear 36, and the planetary gear 38 is engaged. 8 is provided, the ring gear 40 is engaged with the combined output shaft 42, and the continuously variable hydraulic output of the hydraulic pump 28 and the hydraulic motor 29 and the rotational output of the carrier gear 37 are combined to produce zero. Further, the swash plate 58 of the hydraulic pump 28 is configured to be transmitted to the combined output shaft 42 as a rotational force in one direction at the maximum speed, and the swash plate 58 of the hydraulic pump 28 is tilted with the tilt angle θa of the hydraulic motor 29 held constant. When the maximum reversal angle −α is set, the rotational force in one direction on the combined output shaft 42 becomes zero, and the swash plate 58 of the hydraulic pump 28 is maintained with the inclination angle θa of the swash plate 59 of the hydraulic motor 29 kept constant. When the inclination angle is zero, the rotational force in one direction on the combined output shaft 42 is configured to be in the maximum efficiency state V1 in the forward direction, so the output torque at the time of zero start can be easily achieved. Sure And improve the fine speed running performance, yet it is capable of easily achieved, such as improvement of the work efficiency by effectively utilizing the output of the high power transmission efficiency even in a large work load.
[0027]
According to the second aspect of the present invention, when the inclination angle of the swash plate 58 of the hydraulic pump 28 is set to the maximum forward rotation angle + α while the inclination angle θa of the swash plate 59 of the hydraulic motor 29 is kept constant, Since the rotational force in one direction on the output shaft 42 is configured to be in the forward maximum speed state V2, the composite output shaft 42 can be easily operated by operating the swash plate 58 angle of the hydraulic pump 28. By rotating the gears in one direction (forward rotation), smooth and easy gear shifting in forward traveling can be easily performed.
[0028]
[0029]
[Brief description of the drawings]
FIG. 1 is an overall side view of a combine.
FIG. 2 is an overall plan view of the combine.
FIG. 3 is an explanatory diagram of a travel drive system.
FIG. 4 is an explanatory diagram of a planetary gear mechanism.
FIG. 5 is an explanatory diagram showing a 0 rotation state of a combined output shaft.
FIG. 6 is an explanatory diagram showing a maximum efficiency rotation state of a combined output shaft.
FIG. 7 is an explanatory diagram showing a maximum rotation state of a combined output shaft.
FIG. 8 is an explanatory diagram showing a rotation state of a combined output shaft.
FIG. 9 is an explanatory diagram showing a relationship between a main transmission lever and a hydraulic transmission mechanism.
FIG. 10 is an explanatory diagram of rotation of the planetary gear mechanism.
FIG. 11 is an output explanatory diagram of a hydraulic transmission mechanism.
FIG. 12 is an explanatory diagram of output on the transmission gear side.
FIG. 13 is an explanatory diagram of output of a composite output shaft.
FIG. 14 is an explanatory diagram of engine output during low-speed running.
FIG. 15 is an explanatory diagram of engine output for medium speed running.
FIG. 16 is an explanatory diagram of engine output at high speed.
[Explanation of symbols]
2 Engine 28 Hydraulic pump 29 Hydraulic motor 30 Hydraulic transmission mechanism 32 Transmission gear 58 Swash plate 59 Swash plate 64 Compound transmission mechanism

Claims

エンジンの駆動力を伝える油圧変速機構と伝達ギヤの各出力を合成して変速出力する複合変速機構を備え、１組の油圧ポンプ及び油圧モータにて前記油圧変速機構を形成し、油圧ポンプのポンプ軸をエンジンに連結させて、エンジン出力を油圧変速機構に伝達させると共に、油圧ポンプの斜板角制御によって複合変速機構の合成出力軸を一方向に変速回転させるコンバインにおいて、
前記油圧モータのモータ軸にサンギヤを係合軸支させ、前記ポンプ軸にキャリヤギヤを連結させ、前記キャリヤギヤにプラネタリギヤを回転自在に設け、前記サンギヤにプラネタリギヤを噛合させ、前記プラネタリギヤに噛合させるリングギヤを設け、前記合成出力軸に前記リングギヤを係合軸支させ、前記油圧ポンプ及び油圧モータの無段油圧変速出力と、前記キャリヤギヤの回転出力とを合成し、ゼロ乃至最大速の一方向の回転力として前記合成出力軸に伝えるように構成し、
前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角を最大逆転角にした場合は、前記合成出力軸における一方向の回転力がゼロになり、
前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角をゼロにした場合は、前記合成出力軸における一方向の回転力が前進方向の最高効率状態になるように構成している、
コンバイン。Comprising a composite transmission mechanism to shift output of each output of the hydraulic transmission mechanism and the transmission gear for transmitting the driving force of the engine synthesized and form the hydraulic transmission mechanism at a pair of hydraulic pumps and hydraulic motors, the hydraulic pump pumps In a combine that connects the shaft to the engine, transmits the engine output to the hydraulic transmission mechanism, and shifts and rotates the combined output shaft of the composite transmission mechanism in one direction by controlling the swash plate angle of the hydraulic pump .
A sun gear is engaged and supported on the motor shaft of the hydraulic motor, a carrier gear is connected to the pump shaft, a planetary gear is rotatably provided on the carrier gear, a planetary gear is engaged with the sun gear, and a ring gear is provided that is engaged with the planetary gear. The ring gear is engaged with and supported by the combined output shaft, and the continuously variable hydraulic shift output of the hydraulic pump and the hydraulic motor and the rotation output of the carrier gear are combined to generate a rotational force in one direction from zero to the maximum speed. Configured to communicate to the composite output shaft ,
When the inclination angle of the swash plate of the hydraulic pump is set to the maximum reversal angle while keeping the inclination angle of the swash plate of the hydraulic motor constant, the rotational force in one direction on the combined output shaft becomes zero,
When the inclination angle of the swash plate of the hydraulic pump is made zero while the inclination angle of the swash plate of the hydraulic motor is kept constant, the unidirectional rotational force on the combined output shaft becomes the highest efficiency state in the forward direction. Configured to be
Combine .

前記油圧モータの斜板の傾斜角を一定保持させた状態で前記油圧ポンプの斜板の傾斜角を最大正転角にした場合は、前記合成出力軸における一方向の回転力が前進最高速状態になるように構成している、
請求項１に記載のコンバイン。 When the inclination angle of the swash plate of the hydraulic pump is set to the maximum normal rotation angle while the inclination angle of the swash plate of the hydraulic motor is kept constant, the rotational force in one direction on the combined output shaft is the maximum forward speed state. Configured to be,
The combine according to claim 1.