JP3644448B2

JP3644448B2 - Combine harvester gearing

Info

Publication number: JP3644448B2
Application number: JP2002381874A
Authority: JP
Inventors: 久幸里路; 雅一広瀬
Original assignee: Iseki and Co Ltd
Current assignee: Iseki and Co Ltd
Priority date: 2002-12-27
Filing date: 2002-12-27
Publication date: 2005-04-27
Anticipated expiration: 2020-04-27
Also published as: JP2003174818A

Description

【０００１】
【発明の属する技術分野】
この発明は、コンバインの刈取伝動装置に関する。
【０００２】
【従来の技術】
従来から、コンバインにおける刈取装置への動力の供給は、車体側に設けた駆動側プーリから刈取装置の入力軸に設けた従動側プーリへ、通常の伝動ベルト又は無段変速ベルト等を張設して伝動するものが一般的である。
【０００３】
【発明が解決しようとする課題】
しかし、このようにベルトにより動力を伝動する場合、駆動側プーリと従動側プーリ及びその間に張設した伝動ベルト等により構成される伝動機構が必要となる適正なベルトラインや軸間距離及びスペースの確保等制約される条件が多いため、レイアウト設定上の自由度が少なく伝動構成上苦労を伴う。
【０００４】
そこで、この発明は、走行装置の油圧無段変速装置とは別体に設けた油圧ポンプと油圧モータからなる変速装置によって刈取装置を駆動するとともに、刈取装置の回転速度を車速に追従させるようにするものである。
【０００５】
【課題を解決するための手段】
この発明は、エンジンＥからの動力を走行用のミッションケース３内に無段変速可能に変速伝動する油圧無段変速装置１を設けるとともに、前記油圧無段変速装置１によって変速されずに駆動される刈取装置駆動用の油圧ポンプ４９ａを設け、該刈取装置駆動用の油圧ポンプ４９ａからの送油によって駆動回転し且つトラニオンレバー５２の動作によって回転速度が変速される油圧モータ４９ｂを設け、該油圧モータ４９ｂの回転によって刈取装置８の刈刃装置３４と引起装置３５を駆動するとともに刈取装置８の上部搬送装置４２と下部搬送装置４３とを駆動する構成とし、走行レバー４６の操作によって前記油圧無段変速装置１が無段変速操作されると前記刈取装置駆動用の油圧ポンプ４９ａのトラニオンレバー５２が操作されて前記油圧モータ４９ｂの駆動回転が変速され、且つ、走行レバー４６の中立操作によって走行停止されたとき前記刈取装置駆動用の油圧ポンプ４９ａのトラニオンレバー５２は前記油圧モータ４９ｂが低回転速度で駆動回転される状態に操作されるように連動する構成とし、前記ミッションケ−ス３内の副変速ギヤ１９を切り替える副変速レバ−４８の低速側への切り替え操作に連動して前記油圧モ−タの出力トルクが自動的に下がるように構成したことを特徴とするコンバインの刈取伝動装置の構成とする。
【０００６】
上記構成としたものなので、エンジンＥからの動力は、油圧無段変速装置１によって無段変速可能に変速伝動されて走行用のミッションケース３内に伝動され、走行装置１２が駆動されるとともに、前記油圧無段変速装置１によって変速されずに刈取装置駆動用の油圧ポンプ４９ａが駆動され、該刈取装置駆動用の油圧ポンプ４９ａによって油圧モータ４９ｂが駆動回転されるとともに、トラニオンレバー５２の動作によって油圧モータ４９ｂの回転速度が変速され、該油圧モータ４９ｂの回転によって刈取装置８の刈刃装置３４と引起装置３５が駆動されるとともに刈取装置８の上部搬送装置４２と下部搬送装置４３とが駆動される。そして、走行レバー４６の操作によって前記油圧無段変速装置１が無段変速操作されるとともに前記刈取装置駆動用の油圧ポンプ４９ａのトラニオンレバー５２が操作されて前記油圧モータ４９ｂの駆動回転が変速され、且つ、走行レバー４６の中立操作によって走行停止されたとき前記刈取装置駆動用の油圧ポンプ４９ａのトラニオンレバー５２は前記油圧モータ４９ｂが低回転速度で駆動回転される状態に操作される。また、前記ミッションケ−ス３内の副変速ギヤ１９を切り替える副変速レバ−４８の低速側への切り替え操作に連動して前記油圧モ−タの出力トルクが自動的に下がる。
【０００７】
【発明の効果】
この発明によると、刈取装置８の刈刃装置３４と引起装置３５と上部搬送装置４２及び下部搬送装置４３が、車速を変速する無段変速装置１とは別に設けた刈取装置駆動用の油圧ポンプ４９ａと油圧モータ４９ｂとによって駆動する構成としたものにおいて、油圧無段変速装置１により変速された車速に追従させて刈取回転速度を変速し穀稈の刈取性能を向上させることができる。また、刈取回転速度を車速に追従させて変速させる構成でありながら、走行停止時において刈取装置８を一定回転速度で駆動する構成としたものなので、従来、微速走行のときに刈取装置８も微速回転速度となって不具合を生じていたのを改善し、刈取性能を向上させることができる。また、走行用のミッションケ−ス３内の副変速ギヤ１９を切り替える副変速レバ−４８の低速側への切り替え操作に連動して油圧モ−タの出力トルクが自動的に下がり、作物条件や刈取条件に応じて出力トルクを変更させることができる。
【０００８】
【発明の実施の形態】
以下に、この発明の実施例を図面に基づいて説明する。コンバインの車台１０の下部側に、土壌面を走行する左右一対の走行クローラ１１を有する走行装置１２を配設し、該車台１０上に、フィードチェン１３に挟持して供給される穀稈を脱穀し、この脱穀により選別回収された穀粒を一時貯留するグレンタンク１４を備えた脱穀装置１５を配設する。この脱穀装置１５の前方側に立毛穀稈を分草し引き起こして刈り取ると共に、この刈り取った穀稈を後方側へ搬送しながら横倒れ姿勢に変更して該フィードチェン１３へ受け渡しする刈取装置８を、土壌面に対して上下昇降自在となるよう該車台１０の前端部へ懸架する。また、該刈取装置８の一側にコンバインの操作制御を行う操作装置１６と、この操作のための操作席１７とを設け、この操作席１７の下方にエンジンＥを配設して車体１８を構成する。
【０００９】
エンジンＥからの動力を、油圧ポンプとモータを直結形態とした油圧無段変速装置１（以下ＨＳＴ装置という）の直結可変ポンプ１ａ側へ伝達し、このＨＳＴ装置１の出力部側面を走行用ミッションケース３の入力部側面に取り付けると共に、直結可変ポンプ１ａと油圧直結した直結モータ１ｂの出力軸２とミッションケース３の入力軸４とを連結して構成する。
【００１０】
このミッションケース３は、該入力軸４に軸回転して高・中・低に変速する副変速Ｇとしての三連ギヤ１９を左右摺動可能に軸承し、この三連ギヤ１９と噛合する高速ギヤ２０、中速ギヤ２１、低速ギヤ２２を各々カウンタ軸２３に軸止させると共に、このカウンタ軸２３から複数段のギヤトレーンによる変速連動機構Ｍを介して、最終段の左右のスプロケット軸２４の一端部に軸止した左右のスプロケットギヤ２５へ連動させ、このスプロケット軸２４の他端部をミッションケース３から外方側へ突出して、この他端部に軸止したスプロケット２６によって前記左右の走行クローラ１１を駆動させる構成とする。
【００１１】
該ミッションケース３の入力部側面と反対の側面から入力軸４の端部を突出させ、この軸端部に刈取装置８を駆動させる単体の油圧ポンプ６とこの油圧ポンプ６の逆転を防止するワンウェイクラッチ５とを一体的に組み合わせ連結して構成する。刈取装置８の入力部に入力ギヤケース２７を設け、この入力ギヤケース２７から外方側へ突出させた入力軸９の一端部に、該油圧ポンプ６からの送油によつて刈取装置８を駆動する単体の油圧モータ７を連結し、この入力軸９の他端部と下方側へ延長する刈取伝動軸２８の上端部とを傘歯車２９によって噛合連動させ、この刈取伝動軸２８を内装した縦長の刈取伝動ケース３０の上端部を入力ギヤケース２７と接続しその下端部を横長の下部伝動ケース３１に接続させると共に、刈取伝動軸２８の下端部と下部伝動ケース３１に内装した下部伝動軸３２とを傘歯車３３によって噛合連動させて、入力軸９から下部伝動軸３２へ動力を伝達して刈刃装置３４及び引起装置３５等を駆動させる構成とする。
【００１２】
一方、入力軸９と平行に入力ギヤケース２７から外方側へ突出させた上部伝動軸３６の一端部と入力軸９の中間部とを一対の伝動歯車３７によって噛合連動させ、この上部伝動軸３６を内装した上部伝動ケース３８の一端部を入力ギヤケース２７と接続し、その他端部を搬送伝動ケース３９に接続させると共に、上部伝動軸３６の他端部と搬送伝動ケース３９に内装した搬送伝動軸４０とを傘歯車４１によって噛合連動させて、入力軸９から搬送伝動軸４０へ動力を伝達して上部搬送装置４２及び下部搬送装置４３等を駆動させる構成とする。
【００１３】
前記油圧ポンプ６から、切替レバーを刈取クラッチ４４ａとして使用する切替バルブ４４を介して油圧モータ７へ油圧配管すると共に、油圧ポンプ６と切替バルブ４４との間にリリーフバルブ４５を接続配管した構成とすることにより、前記ミッションケース３に固定された油圧ポンプ６から油圧ホースの配管のみで刈取装置８の入力ギヤケース２７に固定された油圧モータ７へ動力を伝達することができるので、従来におけるベルト伝動等の如く、必要とする適正なベルトラインや軸間距離及びスペースの確保等、レイアウト設定のための制約条件に拘束されず自由度が増大して伝動構成が容易となる。
【００１４】
前記操作装置１６の一側にＨＳＴ装置１を前進・中立・後進に変速操作する走行レバー４６を配設し、この走行レバー４６が中立位置のときは、ＨＳＴ装置１の出力軸２が停止することにより油圧ポンプ６も停止するので、無駄な油圧運転による消耗を防止することができる。エンジンＥからの動力を、走行レバー４６の操作によりＨＳＴ装置１の油圧可変ポンプ１ａと油圧可変モータ１ｂとにより変速させて、この変速された動力をミッションケース３の入力軸４へ伝動し、このミッションケース１に内装された副変速Ｇ及び変速連動機構Ｍを経て、左右のスプロケット軸２４によりスプロケット２６を介して走行クローラ１１を駆動し車体１８を変速走行させる。一方、入力軸４の駆動により油圧ポンプ６を連動し、この油圧ポンプ６の油圧力により切替バルブ４４が連通側に切り替えられているときは油圧モータ７を駆動することにより、刈取装置８の入力軸９を介して車速の変速に応じて刈取回転速度を追従変速させて、穀稈の刈取性能を向上させることができる。
【００１５】
倒伏した穀稈等悪条件の刈り取り時に、刈取装置８の各部の詰まり等により伝動系がロックされたときは、リリーフバルブ４５によって油圧力を逃がすことにより、従来のベルト伝動時におけるようなベルトのスリップによる不安定な安全装置と違って、刈取装置８の有効的確な安全装置とすることができると共に、該走行レバー４６の操作により車体１８が後進するときは該入力軸４が逆転することになるので、この逆転時にワンウェイクラッチ５の作用により油圧ポンプ６の逆転を防止して保護することができる。
【００１６】
また、図３に示す如く、該リリーフバルブ４５にリリーフセット圧を強弱に調節できる調節レバー４５ａを設け、この調節レバー４５ａと前記操作装置１６の一側に配設したトルク変更レバー４７とをリンク機構４７ａにより連結することによって、このトルク変更レバー４７の操作により作物条件や刈取条件による油圧モータ７の出力トルクを変更して、例えば刈取装置８に刈取穀稈が詰まり易い倒伏状態や雑草が多いときなどにはリリーフセット圧を弱にしてトルクを下げ、刈取穀稈が通常の立毛状態で雑草が少ないときなどではリリーフセット圧を強にしてトルクを上げることにより、出力トルクの上限規制値を変更することができるので、従来におけるベルト伝動等のように作物条件や刈取条件によって一定の出力トルクによって規制されることがなく、刈り取りの際に穀稈が詰まり易いような条件のときにはトルクを下げておくことにより、少しの詰まりでリリーフが効き刈取装置８が停止して詰まりの解除も容易であると共に、破損等も防止することができる。
【００１７】
なお、前記ミッションケース３の副変速Ｇが、副変速ギヤ１９により高速側から低速側へ切り替えられたときは、刈取装置８に穀稈が詰まり易い条件が多いことから、該トルク変更レバー４７の代わりに、副変速ギヤ１９を切り替えるために該操作装置１６の一側に配設された副変速レバー４８に該リンク機構４７ａを連結させて、この副変速レバー４８の低速側への切り替え操作に連動して油圧モータ７の出力トルクを自動的に下げて、作物条件や刈取条件に応じて忘れることなく的確に出力トルクを変更させるようにすることもできる。
【００１８】
また、刈取装置８への油圧駆動による動力伝達を、上記実施例とは異なり、図４に示す如く、油圧分離形態の油圧無段変速装置４９（以下ＨＳＴ装置という）の分離可変ポンプ４９ａを、前記ＨＳＴ装置１の直結可変ポンプ１ａの入力側とは反対の側面に取り付けると共に、この直結可変ポンプ１ａの軸端部に分離可変ポンプ４９ａとこの分離可変ポンプ４９ａの逆転を防止するワンウェイクラッチ５０とを一体的に組み合わせて連結構成し、直結可変ポンプ１ａのトラニオン制御用トラニオンレバー軸５１と分離可変ポンプ４９ａのトラニオン制御用トラニオンレバー５２とを同期連動可能に一体的に結合し、この結合されたトラニオンレバー５１，５２と前記走行レバー４６とをリンク機構４６ａにより連結して構成する。
【００１９】
刈取装置８の入力ギヤケース２７に設けた入力軸９の一端部に、該分離可変ポンプ４９ａからの送油によって駆動する分離モータ４９ｂを連結し、前記の如く、入力軸９から刈取伝動軸２８を経て下部伝動軸３２への伝動により刈刃装置３４及び引起装置３５等を駆動すると共に、一方で、入力軸９から上部伝動軸３６を経て搬送伝動軸４０への伝動により上部搬送装置４２及び下部搬送装置４３等を駆動し、分離可変ポンプ４９ａから分離モータ４９ｂへ送油する油圧配管を、その途中にリリーフバルブ５３と切替バルブ５４とを介して接続配管して構成する。該走行レバー４６の操作によりＨＳＴ装置１の直結可変ポンプ１ａのトラニオンレバー５１に、ＨＳＴ装置４９の分離可変ポンプ４９ａのトラニオンレバー５２を連動作用させることにより、車速の変速に応じて刈取回転速度を追従変速させて穀稈の刈取性能を向上させることができると共に、従来におけるベルト伝動等に比して伝動構成上の制約条件に拘束されず自由度が増大して、伝動構成が容易となる。倒伏した穀稈等悪条件の刈り取り時に刈取装置８の各部の詰まり等により伝動系がロックされたときは、リリーフバルブ５３によって油圧力を逃がすことにより刈取装置８の有効的確な安全装置とすることができると共に、直結可変ポンプ１ａと分離可変ポンプ４９ａとを同一軸上に二連構成とすることで配管等の油圧伝動構成を単純化することができる。
【００２０】
また、該直結可変ポンプ１ａのトラニオンレバー５１と分離可変ポンプ４９ａのトラニオンレバー５２との一体的な同期連動結合を、図５に示す如く、トラニオンレバー５２をトラニオンレバー５１に対してθだけ傾けて結合することにより、トラニオンレバー５１が中立状態に位置して走行装置１２の駆動が停止しても、刈取装置８はトラニオンレバー５２がθだけ傾いているため低回転速度で駆動するので、車速の変速に応じて刈取回転速度を追従変速させる構成でありながら、車速停止時においても刈取装置８は一定回転速度で駆動されるため、従来、微速走行のときには刈取装置８も微速回転速度となって不具合を生じていた刈取性能を改善向上させることができる。
【００２１】
また、前記走行レバー４６を手動操作してＨＳＴ装置１を駆動させる手動制御走行と、車体１８に内装したコントローラ５５により走行レバー４６を自動操作してＨＳＴ装置１を駆動させる自動制御走行とを適宜に切り替えて走行させる場合、従来では、自動制御時にＨＳＴ装置１を制御モータ５６の動力により一連の操作ギヤ５７を駆動し、走行レバー４６の回動支軸盤４６ａと操作ギヤ５７とを摩擦圧着させるブレーキライニング５８を介して前記トラニオンレバー５１を操作制御するようにしているが、この自動制御時において危険防止の面から手動制御を優先させる構成としており、この構成により手動制御の際に走行レバー４６の操作が非常に重くなるという難点があった。
【００２２】
このため、図６及び図７に示す如く、該制御モータ５６によって連動される一連の操作ギヤ５７を、走行レバー４６の回動支軸盤４６ｂと圧着盤５９との間に各々ブレーキライニング５８を挟んで支持軸６０に支承し、圧着盤５９を該回動支軸盤４６ｂに押圧する押圧ばね６１を設けると共に、この押圧ばね６１を、相互の凸爪部６２ａを突き合わせて押圧させるよう片側を軸固定に片側を遊動自在とした一組の押圧カム盤６２Ａ，６２Ｂにより押圧させる構成とし、片側の遊動自在の押圧カム盤６２Ｂから外周方向へ突出させたカムレバー６２ｂの回動操作により、この押圧カム盤６２の凸爪部６２ａを相互に突き合わせて押圧ばね６１とブレーキライニング５８の押圧作用により、操作ギヤ５７と走行レバー４６とを圧着連動させる位置において、制御モータ５６を駆動させる自動制御スイッチ６３の接点をＯＮさせるべく係合配置して構成する。この自動制御スイッチ６３と制御モータ５６とを該コントローラ５５へ接続する。
【００２３】
車速を自動制御走行に切り替えるときは、カムレバー６２ｂを回動操作して押圧カム盤６２の凸爪部６２ａを相互に突き合わせることにより、押圧カム盤６２Ｂが横方向に押され押圧ばね６１を押圧し、この押圧ばね６１で押圧される圧着盤５９と走行レバー４６との間に挟まれた操作ギヤ５７とブレーキライニング５８とを同時に圧着させると共に、このときカムレバー６２ｂの回動により自動制御スイッチ６３がＯＮしてコントローラ５５の制御により制御モータ５６を駆動させ、ＨＳＴ装置１のトラニオンレバー５１の制御を行い自動制御走行させる。これらの構成では、自動制御走行時といえどもブレーキライニング５８の押圧力に打ち勝つ走行レバー４６の操作力により、手動制御走行を優先させうるので安全である。
【００２４】
この自動制御走行から手動制御走行に切り替えるときは、カムレバー６２ｂを元の位置に復帰させることにより制御モータ５６の駆動が停止されると共に、押圧カム盤６２Ｂの回動により凸爪部６２ａによる押圧ばね６１の押圧力が解除されフリー状態となり回動荷重が低減した走行レバー４６を、軽い操作力によって回動させて手動制御走行を行わせることができる。なお、押圧カム盤６２の作用を電磁クラッチ等によって自動的に制御させるようにしてもよい。
【００２５】
また、ＨＳＴ装置１のトラニオンレバー５１を制御する自動制御操作と走行レバー４６による手動制御操作との切り替えを、上記実施例とは異なり、図９に示す如く、制御モータ６４の駆動軸６４ａに軸固定の押圧カム盤６４Ａと軸遊転の押圧カム盤６５Ｂとを相対して位置させ、この押圧カム盤６５Ａに設けた凸爪部６５ａと押圧カム盤６５Ｂに設けた凹爪部６５ｂとを各々噛合させると共に、この押圧カム盤６５Ｂと、駆動軸６４ａの軸端に座金６６で受け止められた固定盤６７との間に、両側をブレーキライニング６８で挟まれた操作回動盤６９を位置させ、この操作回動盤６９のギヤ部と、走行レバー４６の操作によりＨＳＴ装置１のトラニオンレバー５１を制御する回動支軸盤７０のギヤ部とを噛合配置させて構成し、押圧カム盤６５Ｂはその幅方向にシフタ溝６５ｃを設け、このシフタ溝６５ｃに嵌合するシフタ７１を回動可能にシフタモータ７２に軸止し、このシフタ７１の回動により接点をＯＮ・ＯＦＦさせるリミットスイッチ７３をシフタ７１の回動に係合させて配置する構成とする。
【００２６】
図１０に示す如く、自動制御スイッチ７４のＯＮにより制御モータ６４を駆動させると同時にシフタモータ７２を駆動するリレー７５を作動させ、このシフタモータ７２の駆動をリミットスイッチ７３によりＯＮ・ＯＦＦさせるよう接続した電気回路を設け、この電気回路の自動制御スイッチ７４により制御モータ６４を駆動させると同時にシフタモータ７２を駆動させて、シフタ７１により押圧カム盤６５Ｂを隙間ｔだけ操作回動盤６９側へ押し付けることにより、押圧カム盤６５Ｂはブレーキライニング６８の摩擦力により回動を阻止され、この回動阻止により押圧カム盤６５Ａの凸爪部６５ａによって押圧カム盤６５Ｂの凹爪部６５ｂに作用する横方向への分力によって、更に押圧カム盤６５Ｂがブレーキライニング６８を介して操作回動盤６９を強力に押圧して操作回動盤６９を制御モータ６４の駆動軸６４ａによって回動させ、この操作回動盤６９によって回動支軸盤７０を回動させて走行レバー４６と共にＨＳＴ装置１のトラニオンレバー５１を回動制動して自動制御走行させる。
【００２７】
自動制御走行から手動制御走行へ切り替えるときは、自動制御スイッチ７４をＯＦＦさせることにより、制御モータ６４とシフタモータ７２がＯＦＦとなり、制御モータ６４の駆動軸６４ａに操作回動盤６９をロックしていた押圧カム盤６５Ｂの押圧力が解除されてフリー状態となるので、操作回動盤６９と噛合する回動支軸盤の回動荷重が軽くなり、これによって手動制御走行時における走行レバー４６の手動操作が軽くなり、円滑に手動制御走行を行わせることができる。
【図面の簡単な説明】
【図１】コンバインの全体を示す側面図。
【図２】走行用の油圧無段変速装置から刈取装置への油圧伝動構成を示すブロック図。
【図３】図２における油圧伝動構成のリリーフバルブ制御機構を示すブロック図。
【図４】走行用と刈取用の両油圧無段変速装置の同期連動制御状態を示すブロック図。
【図５】図４における油圧無段変速装置の非同期連動制御状態を示すブロック図。
【図６】走行用の油圧無段変速装置の制御機構を示す側断面図。
【図７】走行用の油圧無段変速装置の制御機構を示す正面図。
【図８】走行用の油圧無段変速装置の制御回路を示すブロック図。
【図９】走行用の油圧無段変速装置の制御機構を示す側面図。
【図１０】走行用の油圧無段変速装置の電気回路を示すブロック図。
【符号の説明】
１油圧無段変速装置
３ミッションケース
８刈取装置
１９副変速ギヤ
３４刈刃装置
３５引起装置
４２上部搬送装置
４３下部搬送装置
４６走行レバー
４８副変速レバ−
４９ａ油圧ポンプ
４９ｂ油圧モータ
５２トラニオンレバー
Ｅエンジン[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a harvesting transmission device for a combine.
[0002]
[Prior art]
Conventionally, power is supplied to the harvesting device in a combine by stretching a normal transmission belt or a continuously variable transmission belt from a driving pulley provided on the vehicle body side to a driven pulley provided on the input shaft of the harvesting device. It is common to transmit.
[0003]
[Problems to be solved by the invention]
However, when power is transmitted by the belt in this way, an appropriate belt line, an inter-axis distance and a space required for a transmission mechanism composed of a driving pulley and a driven pulley and a transmission belt stretched between them are required. Since there are many conditions that are restricted such as securing, there are few degrees of freedom in layout setting, and there is a difficulty in transmission configuration.
[0004]
Therefore, the present invention drives the reaping device by a transmission composed of a hydraulic pump and a hydraulic motor provided separately from the hydraulic continuously variable transmission of the traveling device, and causes the rotational speed of the reaping device to follow the vehicle speed. To do.
[0005]
[Means for Solving the Problems]
The present invention, provided with a hydraulic stepless transmission 1, the continuously variable capable change transmission the power of the transmission case 3 for traveling from the engine E, is driven without being changed by the hydraulic stepless transmission 1 A hydraulic pump 49a for driving the reaping device is provided, and a hydraulic motor 49b that is driven and rotated by oil feeding from the hydraulic pump 49a for driving the reaping device and whose rotational speed is changed by the operation of the trunnion lever 52 is provided. The configuration is such that the cutting blade device 34 and the pulling device 35 of the reaping device 8 are driven by the rotation of the motor 49b and the upper conveying device 42 and the lower conveying device 43 of the reaping device 8 are driven. When the continuously variable transmission 1 is operated continuously, the trunnion lever 52 of the hydraulic pump 49a for driving the reaping device is operated, and the oil When the drive rotation of the motor 49b is changed and the travel is stopped by the neutral operation of the travel lever 46, the trunnion lever 52 of the hydraulic pump 49a for driving the reaper device is driven and rotated at a low rotational speed. The output torque of the hydraulic motor is interlocked with the switching operation of the auxiliary transmission lever 48 for switching the auxiliary transmission gear 19 in the mission case 3 to the low speed side. It is set as the structure of the harvesting transmission device of the combine characterized by having comprised so that it may fall automatically .
[0006]
Since those configured as described above, power from the engine E is transmitted to the hydraulic stepless transmission CVT capable change transmission has been the transmission case 3 for traveling by 1, the running device 12 is driven, A hydraulic pump 49a for driving the cutting device is driven without being shifted by the hydraulic continuously variable transmission 1, and the hydraulic motor 49b is driven to rotate by the hydraulic pump 49a for driving the cutting device, and the trunnion lever 52 is operated. The rotational speed of the hydraulic motor 49b is changed, and the cutting blade device 34 and the pulling device 35 of the reaping device 8 are driven by the rotation of the hydraulic motor 49b, and the upper transport device 42 and the lower transport device 43 of the reaping device 8 are driven. Is done. Then, the hydraulic continuously variable transmission 1 is operated continuously by the operation of the travel lever 46, and the trunnion lever 52 of the hydraulic pump 49a for driving the reaping device is operated to change the drive rotation of the hydraulic motor 49b. When the traveling lever 46 is stopped by a neutral operation, the trunnion lever 52 of the hydraulic pump 49a for driving the reaping device is operated so that the hydraulic motor 49b is driven and rotated at a low rotational speed. Further, the output torque of the hydraulic motor is automatically lowered in conjunction with the switching operation of the auxiliary transmission lever 48 for switching the auxiliary transmission gear 19 in the mission case 3 to the low speed side.
[0007]
【The invention's effect】
According to the present invention , the cutting blade device 34, the pulling device 35, the upper conveying device 42, and the lower conveying device 43 of the reaping device 8 are provided separately from the continuously variable transmission 1 that changes the vehicle speed and are used to drive the reaping device. In the configuration driven by 49a and the hydraulic motor 49b, the cutting speed can be changed by following the vehicle speed changed by the hydraulic continuously variable transmission 1, and the cutting performance of the cereal can be improved. In addition, although the configuration is such that the cutting rotational speed follows the vehicle speed and shifts, the cutting device 8 is driven at a constant rotational speed when traveling is stopped. It is possible to improve the cutting performance by improving the rotational speed and causing the malfunction. Further, the output torque of the hydraulic motor automatically decreases in conjunction with the switching operation of the sub-shift lever 48 for switching the sub-transmission gear 19 in the traveling mission case 3 to the low speed side. The output torque can be changed according to the cutting conditions.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. A traveling device 12 having a pair of left and right traveling crawlers 11 traveling on the soil surface is disposed on the lower side of the combine chassis 10, and threshing the cereal grains that are supplied to the feed chain 13 while being sandwiched on the chassis 10. And the threshing apparatus 15 provided with the grain tank 14 which stores temporarily the grain selectively collected by this threshing is arrange | positioned. A reaping device 8 that weeds and raises napped cereals on the front side of the threshing device 15 and changes it to a sideways posture while transferring the reaped cereals to the rear side and delivers it to the feed chain 13. The suspension is suspended on the front end of the chassis 10 so as to be movable up and down with respect to the soil surface. In addition, an operating device 16 for controlling the operation of the combine and an operating seat 17 for this operation are provided on one side of the mowing device 8, and an engine E is disposed below the operating seat 17 to displace the vehicle body 18. Constitute.
[0009]
The power from the engine E is transmitted to the directly variable variable pump 1a side of a hydraulic continuously variable transmission 1 (hereinafter referred to as HST device) in which a hydraulic pump and a motor are directly connected. The output shaft 2 of the direct connection motor 1b that is hydraulically connected to the direct connection variable pump 1a and the input shaft 4 of the transmission case 3 are connected to each other and attached to the side surface of the input portion of the case 3.
[0010]
The transmission case 3 has a three-gear gear 19 as a sub-shift G that rotates on the input shaft 4 and shifts to high, middle, and low, and is slidably supported on the left and right sides. The gear 20, the medium speed gear 21, and the low speed gear 22 are respectively fixed to the counter shaft 23, and one end of the left and right sprocket shafts 24 at the final stage is connected from the counter shaft 23 via a gear shift interlocking mechanism M using a plurality of gear trains. The left and right traveling crawlers are interlocked with the left and right sprocket gears 25 that are fixed to the shaft, the other end of the sprocket shaft 24 protrudes outward from the transmission case 3, and the sprocket 26 that is fixed to the other end. 11 is driven.
[0011]
A one-way hydraulic pump 6 that projects the end of the input shaft 4 from the side opposite to the side of the input portion of the transmission case 3 and drives the cutting device 8 to the end of the shaft, and a one-way that prevents the hydraulic pump 6 from reversing. The clutch 5 is integrally combined and connected. An input gear case 27 is provided at the input portion of the reaping device 8, and the reaping device 8 is driven by oil feed from the hydraulic pump 6 at one end of the input shaft 9 that protrudes outward from the input gear case 27. A single hydraulic motor 7 is connected, and the other end portion of the input shaft 9 and the upper end portion of the cutting transmission shaft 28 extending downward are meshed with each other by a bevel gear 29, and the vertically long shaft incorporating the cutting transmission shaft 28 is incorporated. The upper end portion of the cutting transmission case 30 is connected to the input gear case 27 and the lower end portion thereof is connected to the horizontally long lower transmission case 31, and the lower end portion of the cutting transmission shaft 28 and the lower transmission shaft 32 built in the lower transmission case 31 are provided. The bevel gear 33 is engaged and interlocked to transmit power from the input shaft 9 to the lower transmission shaft 32 to drive the cutting blade device 34, the pulling device 35, and the like.
[0012]
On the other hand, one end portion of the upper transmission shaft 36 projecting outward from the input gear case 27 in parallel with the input shaft 9 and an intermediate portion of the input shaft 9 are meshed with each other by a pair of transmission gears 37. Is connected to the input gear case 27 and the other end is connected to the transport transmission case 39, and the other end of the upper transmission shaft 36 and the transport transmission shaft built in the transport transmission case 39 are connected. 40 is meshed and interlocked by a bevel gear 41 to transmit power from the input shaft 9 to the transport transmission shaft 40 to drive the upper transport device 42, the lower transport device 43, and the like.
[0013]
A hydraulic pipe is connected from the hydraulic pump 6 to the hydraulic motor 7 via a switching valve 44 using a switching lever as a cutting clutch 44a, and a relief valve 45 is connected between the hydraulic pump 6 and the switching valve 44. As a result, power can be transmitted from the hydraulic pump 6 fixed to the transmission case 3 to the hydraulic motor 7 fixed to the input gear case 27 of the reaping device 8 only by the piping of the hydraulic hose. As described above, the degree of freedom increases and the transmission configuration is facilitated without being restricted by the constraint conditions for layout setting, such as securing appropriate belt lines, inter-axis distances, and spaces required.
[0014]
A travel lever 46 for shifting the HST device 1 forward, neutral, and reverse is disposed on one side of the operation device 16. When the travel lever 46 is in the neutral position, the output shaft 2 of the HST device 1 stops. As a result, the hydraulic pump 6 is also stopped, so that it is possible to prevent consumption due to useless hydraulic operation. The power from the engine E is shifted by the hydraulic variable pump 1a and the hydraulic variable motor 1b of the HST device 1 by operating the travel lever 46, and the shifted power is transmitted to the input shaft 4 of the transmission case 3, Through the sub-gear G and the gear-shift interlocking mechanism M built in the transmission case 1, the traveling crawler 11 is driven via the sprocket 26 by the left and right sprocket shafts 24 to cause the vehicle body 18 to travel at a variable speed. On the other hand, the hydraulic pump 6 is interlocked by driving the input shaft 4, and when the switching valve 44 is switched to the communication side by the hydraulic pressure of the hydraulic pump 6, the hydraulic motor 7 is driven to input the cutting device 8. The cutting rotational speed can be changed in accordance with the shift of the vehicle speed via the shaft 9, so that the harvesting performance of the cereal can be improved.
[0015]
When the transmission system is locked due to clogging of each part of the reaping device 8 or the like during cutting of an unfavorable condition such as a fallen corn straw, the oil pressure is released by the relief valve 45, so that the belt as in the conventional belt transmission is released. Unlike the unstable safety device due to slipping, the reaping device 8 can be an effective and accurate safety device, and when the vehicle body 18 moves backward by operating the traveling lever 46, the input shaft 4 is reversed. Therefore, during the reverse rotation, the reverse rotation of the hydraulic pump 6 can be prevented and protected by the action of the one-way clutch 5.
[0016]
Further, as shown in FIG. 3, the relief valve 45 is provided with an adjustment lever 45a capable of adjusting the relief set pressure to be strong or weak, and the adjustment lever 45a and a torque change lever 47 disposed on one side of the operation device 16 are linked. By connecting with the mechanism 47a, the torque change lever 47 is operated to change the output torque of the hydraulic motor 7 according to the crop conditions and the cutting conditions. In some cases, the relief set pressure is reduced to lower the torque, and when the harvested cereals are in a normal napped state and there are few weeds, the relief set pressure is increased and the torque is increased to increase the upper limit regulation value of the output torque. Since it can be changed, it is regulated by a constant output torque depending on crop conditions and cutting conditions such as conventional belt transmission. When the conditions are such that the cereals are likely to be clogged during cutting, the torque is lowered so that the relief works with a little clogging and the reaping device 8 stops and the clogging is easily released. Further, damage and the like can be prevented.
[0017]
When the auxiliary transmission G of the transmission case 3 is switched from the high speed side to the low speed side by the auxiliary transmission gear 19, there are many conditions in which the reaping device 8 is likely to be clogged, so that the torque change lever 47 Instead, the link mechanism 47a is connected to a sub-transmission lever 48 disposed on one side of the operating device 16 in order to switch the sub-transmission gear 19, so that the sub-transmission lever 48 can be switched to the low speed side. In conjunction with this, the output torque of the hydraulic motor 7 can be automatically reduced so that the output torque can be accurately changed without forgetting according to the crop conditions and the cutting conditions.
[0018]
In addition, unlike the above embodiment, the transmission of power to the reaping device 8 by hydraulic drive is, as shown in FIG. 4, a separation variable pump 49a of a hydraulic continuously variable transmission 49 (hereinafter referred to as an HST device) in a hydraulic separation mode. A separation variable pump 49a and a one-way clutch 50 for preventing reverse rotation of the separation variable pump 49a are attached to a side surface of the HST device 1 opposite to the input side of the direct connection variable pump 1a. The trunnion control trunnion lever shaft 51 of the direct connection variable pump 1a and the trunnion control trunnion lever 52 of the separation variable pump 49a are integrally coupled so as to be able to synchronize with each other. The trunnion levers 51 and 52 and the travel lever 46 are connected by a link mechanism 46a.
[0019]
A separation motor 49b that is driven by oil feed from the separation variable pump 49a is connected to one end of the input shaft 9 provided in the input gear case 27 of the reaping device 8, and the reaping transmission shaft 28 is connected to the input shaft 9 as described above. Then, the cutting blade device 34 and the pulling device 35 are driven by transmission to the lower transmission shaft 32, while the upper conveyance device 42 and the lower portion are driven by transmission from the input shaft 9 to the conveyance transmission shaft 40 through the upper transmission shaft 36. A hydraulic pipe that drives the transport device 43 and the like and feeds oil from the separation variable pump 49a to the separation motor 49b is configured by connecting piping through a relief valve 53 and a switching valve 54 in the middle thereof. By operating the travel lever 46, the trunnion lever 52 of the separation variable pump 49a of the HST device 49 is operated in conjunction with the trunnion lever 51 of the direct connection variable pump 1a of the HST device 1, so that the cutting rotation speed is adjusted according to the shift of the vehicle speed. It is possible to improve the reaping performance of the cereal by changing the follow-up speed, and the degree of freedom is increased without being restricted by the constraints on the transmission configuration as compared to the conventional belt transmission, and the transmission configuration is facilitated. When the transmission system is locked due to clogging of each part of the harvesting device 8 at the time of harvesting under adverse conditions such as lying grain cedar, the oil pressure is released by the relief valve 53 to make the harvesting device 8 an effective and safe safety device. In addition, the direct transmission variable pump 1a and the separation variable pump 49a can be configured in a duplex manner on the same shaft, thereby simplifying the hydraulic transmission configuration such as piping.
[0020]
Further, an integral synchronous interlocking connection between the trunnion lever 51 of the direct connection variable pump 1a and the trunnion lever 52 of the separation variable pump 49a is made by tilting the trunnion lever 52 by θ with respect to the trunnion lever 51 as shown in FIG. By coupling, even if the trunnion lever 51 is positioned in the neutral state and the driving of the traveling device 12 is stopped, the reaping device 8 is driven at a low rotational speed because the trunnion lever 52 is inclined by θ. Although the cutting rotation speed is changed in accordance with the speed change, the cutting apparatus 8 is driven at a constant rotation speed even when the vehicle speed is stopped. Therefore, conventionally, the cutting apparatus 8 has a low rotation speed when driving at a low speed. It is possible to improve and improve the cutting performance that has caused the problem.
[0021]
Further, manual control travel in which the travel lever 46 is manually operated to drive the HST device 1 and automatic control travel in which the travel lever 46 is automatically operated by the controller 55 built in the vehicle body 18 to drive the HST device 1 are appropriately performed. In the conventional case, the HST apparatus 1 is driven by a series of operation gears 57 by the power of the control motor 56 during automatic control, and the rotation support shaft 46a of the travel lever 46 and the operation gear 57 are friction-bonded. The trunnion lever 51 is operated and controlled via the brake lining 58 to be operated. In this automatic control, manual control is prioritized from the viewpoint of danger prevention, and this configuration allows the travel lever to be controlled during manual control. There was a difficulty that operation of 46 became very heavy.
[0022]
For this reason, as shown in FIGS. 6 and 7, a series of operation gears 57 interlocked by the control motor 56 are provided with brake linings 58 between the rotating spindle 46 b of the traveling lever 46 and the crimping plate 59. A pressing spring 61 is provided which is sandwiched and supported by the support shaft 60 and presses the pressure-bonding plate 59 against the rotating support plate 46b, and the pressing spring 61 is pressed on one side so as to press against each other with the protruding claw portions 62a. The shaft is fixed by a set of pressing cam boards 62A and 62B that are freely movable on one side, and this pressing is performed by rotating a cam lever 62b that protrudes from the freely movable pressing cam board 62B on one side. Positions where the operation gear 57 and the travel lever 46 are interlocked with each other by the pressing action of the pressing spring 61 and the brake lining 58 with the convex claw portions 62a of the cam panel 62 abutting each other. Oite, constructed by engaging arranged to turn ON the contacts of the automatic control switch 63 to drive the control motor 56. The automatic control switch 63 and the control motor 56 are connected to the controller 55.
[0023]
When the vehicle speed is switched to automatic control traveling, the cam lever 62b is turned to bring the convex claw portions 62a of the pressing cam panel 62 into contact with each other, thereby pressing the pressing cam panel 62B in the lateral direction and pressing the pressing spring 61. The operation gear 57 and the brake lining 58 sandwiched between the crimping plate 59 pressed by the pressing spring 61 and the travel lever 46 are simultaneously crimped, and at this time, the automatic control switch 63 is rotated by the rotation of the cam lever 62b. Is turned on, the control motor 56 is driven by the control of the controller 55, and the trunnion lever 51 of the HST device 1 is controlled to perform automatic control running. These configurations are safe because manual control travel can be prioritized by the operating force of the travel lever 46 that overcomes the pressing force of the brake lining 58 even during automatic control travel.
[0024]
When switching from the automatic control travel to the manual control travel, the drive of the control motor 56 is stopped by returning the cam lever 62b to the original position, and the pressing spring by the convex claw 62a is rotated by the rotation of the pressing cam board 62B. It is possible to perform the manually controlled traveling by rotating the traveling lever 46 in which the pressing force 61 is released and the rotational load is reduced by a light operating force. The action of the pressing cam board 62 may be automatically controlled by an electromagnetic clutch or the like.
[0025]
Unlike the above embodiment, the automatic control operation for controlling the trunnion lever 51 of the HST device 1 and the manual control operation by the traveling lever 46 are switched on the drive shaft 64a of the control motor 64 as shown in FIG. The fixed pressing cam board 64A and the axially rotating pressing cam board 65B are positioned relative to each other, and a convex claw portion 65a provided on the pressing cam board 65A and a concave claw portion 65b provided on the pressing cam board 65B are respectively provided. In addition to being engaged, an operation rotating plate 69 sandwiched between both sides by a brake lining 68 is positioned between the pressing cam plate 65B and a fixed plate 67 received by a washer 66 at the shaft end of the drive shaft 64a. The gear portion of the operation rotating plate 69 and the gear portion of the rotating support shaft 70 that controls the trunnion lever 51 of the HST device 1 by the operation of the traveling lever 46 are configured to mesh with each other, and the press cam plate 5B is provided with a shifter groove 65c in the width direction, a shifter 71 fitted in the shifter groove 65c is pivotally fixed to the shifter motor 72, and a limit switch 73 for turning the contact ON / OFF by the rotation of the shifter 71. Is configured to engage with the rotation of the shifter 71.
[0026]
As shown in FIG. 10, the control motor 64 is driven by turning on the automatic control switch 74 and at the same time the relay 75 that drives the shifter motor 72 is actuated, and the drive connected to the switch 75 is turned on and off by the limit switch 73. By providing a circuit and driving the control motor 64 by the automatic control switch 74 of this electric circuit and simultaneously driving the shifter motor 72, the shift cam 71 pushes the pressing cam board 65B by the gap t toward the operation rotation board 69, The pressing cam board 65B is prevented from rotating by the frictional force of the brake lining 68, and by this rotation prevention, the convex claw part 65a of the pressing cam board 65A acts on the concave claw part 65b of the pressing cam board 65B in the lateral direction. The pressing cam panel 65B is further operated via the brake lining 68 by force. By strongly pressing the moving plate 69, the operation rotating plate 69 is rotated by the drive shaft 64 a of the control motor 64, and the rotating support shaft 70 is rotated by the operation rotating plate 69, together with the travel lever 46 and HST. The trunnion lever 51 of the apparatus 1 is rotationally braked to automatically control travel.
[0027]
When switching from automatic control travel to manual control travel, the automatic control switch 74 is turned off, so that the control motor 64 and the shifter motor 72 are turned off, and the operation rotating board 69 is locked to the drive shaft 64a of the control motor 64. Since the pressing force of the pressing cam panel 65B is released to be in a free state, the rotation load of the rotating support disk that meshes with the operation rotating disk 69 is reduced, and thus the manual operation of the traveling lever 46 during manual control traveling is reduced. The operation becomes lighter and it is possible to smoothly perform manual control running.
[Brief description of the drawings]
FIG. 1 is a side view showing an entire combine.
FIG. 2 is a block diagram showing a hydraulic transmission configuration from a traveling hydraulic continuously variable transmission to a reaping device.
3 is a block diagram showing a relief valve control mechanism having a hydraulic transmission configuration in FIG. 2. FIG.
FIG. 4 is a block diagram showing a synchronous interlocking control state of both a hydraulic and continuously variable transmission for traveling and mowing.
5 is a block diagram showing an asynchronous interlocking control state of the hydraulic continuously variable transmission in FIG. 4;
FIG. 6 is a side sectional view showing a control mechanism of a traveling hydraulic continuously variable transmission.
FIG. 7 is a front view showing a control mechanism of a traveling hydraulic continuously variable transmission.
FIG. 8 is a block diagram showing a control circuit of a traveling hydraulic continuously variable transmission.
FIG. 9 is a side view showing a control mechanism of a traveling hydraulic continuously variable transmission.
FIG. 10 is a block diagram showing an electric circuit of a traveling hydraulic continuously variable transmission.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Hydraulic continuously variable transmission 3 Mission case 8 Cutting device
19 auxiliary transmission gear
34 cutting blade device
35 pulling device
42 upper transfer device
43 Lower transfer device
46 travel lever
48 sub-shifting lever
49a hydraulic pump
49b hydraulic motor
52 trunnion lever E engine

Claims

Provided with a hydraulic stepless transmission 1, the continuously variable capable change transmission power from the engine E to the transmission case 3 for driving, cutting device driving driven without being changed by the hydraulic stepless transmission 1 A hydraulic pump 49a is provided, and a hydraulic motor 49b that is driven to rotate by oil feeding from the hydraulic pump 49a for driving the reaping device and whose rotational speed is changed by the operation of the trunnion lever 52 is provided. Is configured to drive the cutting blade device 34 and the pulling device 35 of the reaping device 8 and the upper conveying device 42 and the lower conveying device 43 of the reaping device 8, and the hydraulic continuously variable transmission 1 by operating the traveling lever 46. Is continuously operated, the trunnion lever 52 of the hydraulic pump 49a for driving the mowing device is operated, and the hydraulic motor 49 is operated. And the trunnion lever 52 of the hydraulic pump 49a for driving the reaper device is driven to rotate at a low rotational speed when the travel lever 46 is shifted and the travel is stopped by the neutral operation of the travel lever 46. The hydraulic motor output torque is automatically interlocked with the switching operation of the auxiliary transmission lever 48 for switching the auxiliary transmission gear 19 in the mission case 3 to the low speed side. Combine harvester transmission device characterized in that it is configured to be lowered .