JP3567484B2

JP3567484B2 - Combine harvesting transmission with traveling speed control

Info

Publication number: JP3567484B2
Application number: JP09680694A
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: 1994-05-11
Filing date: 1994-05-11
Publication date: 2004-09-22
Anticipated expiration: 2019-09-22
Also published as: JPH07298758A

Description

【発明の属する技術分野】
【０００１】
この発明は、走行変速制御装置を備えたコンバインの刈取伝動装置に関する。
【従来の技術】
【０００２】
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。
【発明が解決しようとする課題】
【０００３】
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り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。
【課題を解決するための手段】
【０００５】
この発明は、エンジンＥからの動力を走行用ミッションケ−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−５２の動作によって回転速度が変速される油圧モ−タ４９ｂを設け、該油圧モ−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−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−５２が操作されて前記油圧モ−タ４９ｂの駆動回転が変速されるように連動する構成とし、前記走行レバ−４６を手動操作して前記油圧無段変速装置１を変速させる手動変速状態と、車体１８に設けたコントロ−ラ５５により走行レバ−４６を自動操作して前記油圧無段変速装置１を変速させる自動変速制御状態とに切換可能に構成するに、制御モ−タ５６によって連動される操作ギヤ５７を走行レバ−４６の回動支軸盤４６ｂと圧着盤５９との間において左右のブレ−キライニング５８，５８で挟んで設け、前記圧着盤５９を前記回動支持盤４６ｂ側に押圧する押圧ばね６１を設けると共に、片側を軸固定にもう片側を遊動自在とした一組の押圧カム盤６２Ａ，６２Ｂの相互の凸爪部６２ａを突き合わせて前記押圧ばね６１を押圧するように構成して、前記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−６２ｂの回動操作により、該遊動自在の押圧カム盤６２Ｂの凸爪部６２ａと前記軸固定の押圧カム盤６２Ａの凸爪部６２ａとを相互に突き合わせて押圧ばね６１によるブレ−キライニング５８，５８の押圧作用によって操作ギヤ５７と走行レバ−４６とを圧着連動させる構成とし、この操作ギヤ５７と走行レバ−４６とが圧着連動する位置において自動制御スイッチ６３の接点がＯＮして前記制御モ−タ５６が駆動するように構成したことを特徴とする走行変速制御装置を備えたコンバインの刈取伝動装置の構成とする。
【作用、及び発明の効果】
【０００６】
この発明は、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ミッションケ−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−タ４９ｂが駆動回転されるとともに、トラニオンレバ−５２の動作によって油圧モ−タ４９ｂの回転速度が変速され、該油圧モ−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−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−５２が操作されて前記油圧モ−タ４９ｂの駆動回転が変速される。
【０００７】
よって、この発明は、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−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も可能となる。
【０００８】
また、カムレバ−６２ｂを回動操作して押圧カム盤６２の凸爪部６２ａ，６２ａを相互に突き合わせることにより、遊動自在の押圧カム盤６２Ｂが横方向に押されて押圧ばね６１が押圧され、この押圧ばね６１によって圧着盤５９と走行レバ−４６の回動支持盤４６ｂとの間に挟まれた操作ギヤ５７とブレ−キライニング５８，５８とが圧着される。このときカムレバ−６２ｂの回動により自動制御スイッチ６３がＯＮしてコントロ−ラ５５の制御によって制御モ−タ５６が駆動し、油圧無段変速装置１のトラニオンレバ−５１の制御を行い自動変速制御状態となる。しかも、自動変速制御状態といえどもブレ−キライニング５８，５８の押圧力に打ち勝つ走行レバ−４６の操作力により、手動変速操作を優先させうるので安全である。
【０００９】
また、この自動変速制御状態から手動変速状態に切り替えるときは、カムレバ−６２ｂを元の位置に復帰させることにより制御モ−タ５６の駆動が停止すると共に、遊動自在の押圧カム盤６２Ｂの回動により凸爪部６２ａ，６２ａによる押圧ばね６１の押圧力が解除されフリ−状態となり、回動荷重が低減した走行レバ−４６を軽い操作力によって回動させて手動変速を行わせることができる。
【発明の実施の形態】
【００１０】
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。
【００１１】
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。
【００１２】
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。
【００１３】
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。
【００１４】
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。
【００１５】
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。
【００１６】
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。
【００１７】
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。
【００１８】
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。
【００１９】
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。
【００２０】
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。
【００２１】
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。
【００２２】
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。
【００２３】
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。
【００２４】
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。
【００２５】
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。
【００２６】
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。
【００２７】
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。
【００２８】
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。
【００２９】
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−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走行用ミッションケ−ス
８刈取装置
１８車体
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−
４６ｂ回動支軸盤
４９ａ油圧ポンプ
４９ｂ油圧モ−タ
５２トラニオンレバ−
５５コントロ−ラ
５６制御モ−タ
５７操作ギヤ
５８ブレ−キライニング
５９圧着盤
６１押圧ばね
６２Ａ押圧カム盤
６２Ｂ押圧カム盤
６２ａ凸爪部
６２ｂカムレバ−
６３自動制御スイッチ
Ｅエンジン TECHNICAL FIELD OF THE INVENTION
[0001]
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combine harvester transmission equipped with a traveling speed change control device .
[Prior art]
[0002]
Conventionally, power supply to a harvesting device in a combine is performed by stretching a normal transmission belt or a continuously variable transmission belt from a driving pulley provided on a vehicle body side to a driven pulley provided on an input shaft of the harvesting device. What is transmitted is common.
[Problems to be solved by the invention]
[0003]
However, in this manner when the transmission power by a belt, the drive pulley and the driven pulley and the proper belt line and the center distance and space Ri Do requires configured transmission mechanism by a transmission belt or the like stretched in the meantime There are many conditions that are restricted, such as securing the layout, so that the degree of freedom in setting the layout is small and the transmission configuration is difficult.
[0004]
Therefore, the present invention drives the reaping device by a transmission device including a hydraulic pump and a hydraulic motor provided separately from the hydraulic continuously variable transmission of the traveling device, and causes the rotation speed of the reaping device to follow the vehicle speed. Is what you do.
[Means for Solving the Problems]
[0005]
According to the present invention, there is provided a hydraulic continuously variable transmission 1 for transmitting the power from the engine E to the traveling transmission case 3 so as to be capable of continuously variable transmission, and is driven without being shifted by the hydraulic continuously variable transmission 1. A hydraulic pump 49a for driving the reaper is provided, and a hydraulic motor 49b that is driven and rotated by oil supply from the hydraulic pump 49a for driving the reaper and whose rotational speed is changed by the operation of the trunnion lever 52 is provided. The driving lever is driven by the rotation of the hydraulic motor 49b to drive the cutting blade device 34 and the raising device 35 of the mowing device 8 and the upper and lower conveying devices 42 and 43 of the mowing device 8. When the hydraulic continuously variable transmission 1 is continuously variable-speed operated by the operation of 46, the trunnion lever 52 of the hydraulic pump 49a for driving the reaper is operated to operate the hydraulic - a structure in which rotation of the motor 49b is interlocked so as to shift the manual transmission state to shift the hydraulic stepless transmission 1 by manually operating the driving lever -46, provided on the vehicle body 18 controller - La An operation gear 57 interlocked by a control motor 56 is provided so that the operation lever 57 can be switched to an automatic transmission control state in which the traveling lever 46 is automatically operated by 55 and the hydraulic continuously variable transmission 1 is shifted. The left and right brake linings 58, 58 are provided between the rotation supporting disk 46b and the pressure bonding plate 59, and a pressing spring 61 for pressing the pressure bonding plate 59 toward the rotation supporting disk 46b is provided. At the same time, a pair of pressing cam discs 62A and 62B, one of which is fixed to the axis and the other is freely movable, is configured to abut against each other to press the pressing spring 61 so as to press the pressing spring 61. By rotating the cam lever 62b protruding in the outer peripheral direction from the free pressing cam disk 62B, the convex claw 62a of the freely movable pressing cam disk 62B and the convex claw 62a of the shaft fixed pressing cam disk 62A are formed. The operating gear 57 and the traveling lever 46 are pressed and interlocked by the pressing action of the brake linings 58 and 58 by the pressing spring 61, and the operation gear 57 and the traveling lever 46 are pressed and interlocked. In this position, a contact of an automatic control switch 63 is turned on to drive the control motor 56, so that a combine harvesting transmission device having a traveling speed change control device is provided .
[Action and effect of the invention]
[0006]
Since the present invention is configured as described above, the power from the engine E is transmitted by the hydraulic continuously variable transmission 1 so as to be continuously variable-speed-changeable and transmitted into the traveling transmission case 3, and the traveling device 12 is driven. While being driven, the hydraulic pump 49a for driving the reaper is driven without being shifted by the continuously variable hydraulic transmission 1, and the hydraulic motor 49b is driven and rotated by the hydraulic pump 49a for driving the reaper. The rotation speed of the hydraulic motor 49b is changed by the operation of the trunnion lever 52, and the rotation of the hydraulic motor 49b drives the cutting blade device 34 and the raising device 35 of the reaping device 8 and drives the reaping device 8 The upper transfer device 42 and the lower transfer device 43 are driven. By operating the traveling lever 46, the hydraulic continuously variable transmission 1 is continuously variable, and the trunnion lever 52 of the hydraulic pump 49a for driving the reaper is operated to drive the hydraulic motor 49b. The rotation is shifted.
[0007]
Therefore, according to the present invention, the cutting blade device 34, the raising device 35, the upper transport device 42, and the lower transport device 43 of the mowing device 8 are provided with a hydraulic pressure for driving the mowing device provided separately from the continuously variable transmission 1 that changes the vehicle speed. In the configuration driven by the pump 49a and the hydraulic motor 49b, the harvesting rotation speed can be changed by following the vehicle speed shifted by the hydraulic continuously variable transmission 1 to improve the cutting performance of the grain culm. . In addition, while the configuration is such that the cutting rotation speed is changed to follow the vehicle speed, a configuration in which the cutting device 8 is driven at a constant rotation speed when traveling is stopped is also possible.
[0008]
Further, by rotating the cam lever 62b to abut the convex claws 62a, 62a of the pressing cam disk 62 with each other, the freely movable pressing cam disk 62B is pressed in the lateral direction and the pressing spring 61 is pressed. The pressure spring 61 presses the operation gear 57 and the brake linings 58, 58 which are sandwiched between the crimping plate 59 and the rotation support plate 46b of the traveling lever 46. At this time, the automatic control switch 63 is turned on by the rotation of the cam lever 62b, the control motor 56 is driven by the control of the controller 55, and the trunnion lever 51 of the hydraulic continuously variable transmission 1 is controlled to perform the automatic transmission. It will be in the control state. Moreover, even in the automatic transmission control state, the manual transmission operation can be prioritized by the operating force of the traveling lever 46 that overcomes the pressing force of the brake linings 58, 58, so that it is safe.
[0009]
When the automatic gear shift control state is switched to the manual gear shift state, the driving of the control motor 56 is stopped by returning the cam lever 62b to the original position, and the rotation of the freely movable pressing cam disc 62B is performed. As a result, the pressing force of the pressing spring 61 by the protruding claw portions 62a, 62a is released to be in a free state, and the traveling lever 46 having a reduced rotating load can be rotated by a light operating force to perform a manual shift.
BEST MODE FOR CARRYING OUT THE INVENTION
[0010]
Hereinafter, embodiments of the present invention will be described 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 arranged below the undercarriage 10 of the combine, and on the undercarriage 10, threshed grain culm supplied by a feed chain 13 is threshed. Then, a threshing device 15 including a Glen tank 14 for temporarily storing the grains sorted and recovered by the threshing is provided. A harvesting device 8 that weeds and raises the raised culm on the front side of the threshing device 15 and cuts the culm, transfers the cut culm to the rear side while transferring the cut culm to the rear side, and delivers the cut culm to the feed chain 13. Is suspended on the front end of the chassis 10 so that it can move up and down with respect to the soil surface. Also, an operating device 16 for controlling the operation of the combiner and an operating seat 17 for this operation are provided on one side of the reaper 8, and the engine E is disposed below the operating seat 17 to mount the vehicle body 18. Constitute.
[0011]
The power from the engine E is transmitted to the directly connected variable pump 1a of a hydraulic continuously variable transmission 1 (hereinafter, referred to as an HST device) in which a hydraulic pump and a motor are directly connected. The output shaft 2 of the direct-coupled variable pump 1a is connected to the input shaft 4 of the transmission case 3, and the input shaft 4 of the transmission case 3 is connected to the input shaft 4 of the transmission case.
[0012]
The transmission case 3 supports a triple gear 19 as an auxiliary transmission G that rotates about the input shaft 4 to shift to high, middle, and low speeds so as to be slidable left and right. The gear 20, the medium-speed gear 21, and the low-speed gear 22 are each fixed to a counter shaft 23, and one end of each of the left and right sprocket shafts 24 at the final stage is transmitted from the counter shaft 23 via a speed change interlocking mechanism M having a plurality of gear trains. The other end of the sprocket shaft 24 projects outward from the transmission case 3, and the left and right traveling crawlers are fixed by the sprocket 26 fixed to the other end. 11 is driven.
[0013]
An end of the input shaft 4 protrudes from a side opposite to the side of the input portion of the transmission case 3, and a single hydraulic pump 6 for driving the reaper 8 at the end of the shaft, and a one-way for preventing reverse rotation of the hydraulic pump 6. The clutch 5 is integrally combined and connected. An input gear case 27 is provided at an input portion of the mowing device 8, and the mowing device 8 is driven by oil supply from the hydraulic pump 6 to one end of the input shaft 9 protruding outward from the input gear case 27. A single hydraulic motor 7 is connected, and the other end of the input shaft 9 and the upper end of a cutting power transmission shaft 28 extending downward are meshed and interlocked with a bevel gear 29, and a vertically long, internally mounted cutting power transmission shaft 28 is provided. The upper end of the reaper transmission case 30 is connected to the input gear case 27 and the lower end thereof is connected to the horizontally long lower transmission case 31, and the lower end of the reaper transmission shaft 28 and the lower transmission shaft 32 housed in the lower transmission case 31 are connected. The power is transmitted from the input shaft 9 to the lower transmission shaft 32 so that the cutting blade device 34 and the raising device 35 are driven by being meshed and linked by the bevel gear 33.
[0014]
On the other hand, one end of an 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 and interlocked by a pair of transmission gears 37. Is connected to the input gear case 27, the other end is connected to the transfer transmission case 39, and the other end of the upper transmission shaft 36 and the transfer transmission shaft mounted in the transfer transmission case 39. 40 and a bevel gear 41 mesh with each other to transmit power from the input shaft 9 to the transport transmission shaft 40 to drive the upper transport device 42 and the lower transport device 43 and the like.
[0015]
A hydraulic pipe is connected to the hydraulic motor 7 from the hydraulic pump 6 via a switching valve 44 that uses a switching lever as a mowing clutch 44a, and a relief valve 45 is connected and connected between the hydraulic pump 6 and the switching valve 44. By doing so, the 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 reaper 8 only by the piping of the hydraulic hose. As described above, the degree of freedom is increased and the transmission configuration is facilitated without being restricted by constraints for layout setting, such as securing a necessary appropriate belt line, center distance and space.
[0016]
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 waste due to useless hydraulic operation can be prevented. The power from the engine E is shifted by the variable hydraulic pump 1a and the variable hydraulic 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, The traveling crawler 11 is driven by the left and right sprocket shafts 24 via the sprocket 26 via the auxiliary transmission G and the transmission interlocking mechanism M provided in the transmission case 1 to cause the vehicle body 18 to travel at a variable speed. On the other hand, the hydraulic pump 6 is interlocked by the drive of 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, so that the input of the reaper 8 is performed. The harvesting rotation speed can be changed according to the vehicle speed shift via the shaft 9 to improve the cutting performance of the grain stalk.
[0017]
When the transmission system is locked due to clogging or the like of each part of the reaping device 8 during cutting under bad conditions such as a fallen grain culm, the oil pressure is released by the relief valve 45, and the belt is moved as in the conventional belt transmission. Unlike the unstable safety device due to slip, it is possible to provide an effective and accurate safety device for the reaper 8 and, when the vehicle body 18 moves backward by the operation of the traveling lever 46, the input shaft 4 reverses. Therefore, the reverse rotation of the hydraulic pump 6 can be prevented and protected by the operation of the one-way clutch 5 during the reverse rotation.
[0018]
As shown in FIG. 3, the relief valve 45 is provided with an adjusting lever 45a capable of adjusting the relief set pressure strongly, and this adjusting lever 45a is linked to a torque changing lever 47 provided on one side of the operating device 16. By connecting with the mechanism 47a, the output torque of the hydraulic motor 7 is changed by the operation of the torque changing lever 47 according to crop conditions and cutting conditions. In some cases, such as when the relief set pressure is weakened to lower the torque, and when the harvested culm is in a normal upright state and there are few weeds, the relief set pressure is increased and the torque is increased to increase the upper limit value of the output torque. Since it can be changed, it is regulated by a constant output torque according to crop conditions and cutting conditions like the conventional belt transmission. When the conditions are such that the culm is likely to be clogged during mowing, the torque is reduced, so that the relief is effective with a slight clogging, the cutting device 8 is stopped, and the clogging is easily released. , Breakage and the like can also be prevented.
[0019]
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 harvesting device 8 is likely to be clogged with the cereal stem. Instead, the link mechanism 47a is connected to a sub-transmission lever 48 provided on one side of the operating device 16 to switch the sub-transmission gear 19, and the operation of switching the sub-transmission lever 48 to a lower speed side is performed. In conjunction therewith, 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 crop conditions and cutting conditions.
[0020]
In addition, unlike the above-described embodiment, the power transmission by hydraulic drive to the reaper 8 is performed, as shown in FIG. 4, by using a separation variable pump 49a of a hydraulic continuously variable transmission 49 (hereinafter referred to as an HST device) of a hydraulic separation type. Attached to the side of the HST device 1 opposite to the input side of the directly connected variable pump 1a, a separate variable pump 49a and a one-way clutch 50 for preventing reverse rotation of the separated variable pump 49a are provided at the shaft end of the directly connected variable pump 1a. And the trunnion control trunnion lever shaft 51 of the directly-coupled variable pump 1a and the trunnion control trunnion lever 52 of the separation variable pump 49a are integrally connected so as to be synchronously interlocked. The trunnion levers 51 and 52 and the traveling lever 46 are connected by a link mechanism 46a.
[0021]
One end of the input shaft 9 provided in the input gear case 27 of the mowing device 8 is connected to a separation motor 49b driven by oil supply from the variable separation pump 49a, and the cutting transmission shaft 28 is connected from the input shaft 9 as described above. The transmission to the lower transmission shaft 32 drives the cutting blade device 34 and the raising device 35 and the like, while the transmission from the input shaft 9 to the conveyance transmission shaft 40 via the upper transmission shaft 36 causes the upper conveyance device 42 and the lower A hydraulic pipe for driving the transfer device 43 and the like to feed oil from the variable separation pump 49a to the separation motor 49b is configured by connecting and connecting a relief valve 53 and a switching valve 54 in the middle thereof. By operating the traveling 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 directly connected variable pump 1a of the HST device 1, so that the mowing rotation speed is changed in accordance with the vehicle speed change. Following performance can improve the mowing performance of the culm, and the degree of freedom is increased without being restricted by the constraints on the transmission configuration as compared with the conventional belt transmission or the like, thereby facilitating the transmission configuration. When the transmission system is locked due to clogging of various parts of the reaping device 8 during mowing under bad conditions such as a fallen grain culm, an effective and safe safety device of the reaping device 8 is provided by releasing the oil pressure by the relief valve 53. In addition, by directly connecting the directly connected variable pump 1a and the separated variable pump 49a on the same axis, the hydraulic transmission configuration such as piping can be simplified.
[0022]
Further, as shown in FIG. 5, the trunnion lever 52 of the direct-coupled variable pump 1a and the trunnion lever 52 of the separation variable pump 49a are integrally synchronized and interlocked by tilting the trunnion lever 52 by θ with respect to the trunnion lever 51. By coupling, even if the driving of the traveling device 12 is stopped with the trunnion lever 51 positioned in the neutral state, the mowing device 8 is driven at a low rotational speed because the trunnion lever 52 is inclined by θ, so that the vehicle speed is reduced. The reaping device 8 is driven at a constant rotational speed even when the vehicle speed is stopped, although the reaping device 8 is driven at a constant rotational speed even when the vehicle speed is stopped. It is possible to improve and improve the mowing performance that has caused a problem.
[0023]
In addition, a manually controlled travel in which the travel lever 46 is manually operated to drive the HST device 1 and an automatic controlled 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. Conventionally, in the automatic control, the HST device 1 drives a series of operation gears 57 by the power of the control motor 56 during automatic control, and frictionally presses the rotation support plate 46a of the traveling lever 46 and the operation gear 57. The operation of the trunnion lever 51 is controlled via the brake lining 58 to be operated. However, during automatic control, priority is given to manual control from the viewpoint of danger prevention. There was a disadvantage that the operation of 46 became very heavy.
[0024]
For this reason, as shown in FIGS. 6 and 7, a series of operation gears 57 interlocked by the control motor 56 are connected to a brake lining 58 between the rotation support plate 46b of the traveling lever 46 and the crimping plate 59, respectively. A pressing spring 61 is provided to support the support shaft 60 by sandwiching the pressing shaft 59 and press the crimping plate 59 against the rotating support shaft plate 46b. One side of the pressing spring 61 is pressed so that the projecting claws 62a abut against each other. The shaft is fixed by a pair of pressing cam disks 62A and 62B that are freely movable on one side, and the pressing operation is performed by rotating a cam lever 62b that protrudes in the outer circumferential direction from the one freely movable pressing cam disk 62B. The position where the operating gear 57 and the traveling lever 46 are pressed and linked by the pressing action of the pressing spring 61 and the brake lining 58 by abutting the convex claws 62 a of the cam disk 62 with 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.
[0025]
When the vehicle speed is switched to the automatic control traveling, the cam lever 62b is rotated to abut the convex claws 62a of the pressing cam disk 62 with each other, so that the pressing cam disk 62B is pressed in the lateral direction and the pressing spring 61 is pressed. Then, the operation gear 57 and the brake lining 58 sandwiched between the pressing plate 59 pressed by the pressing spring 61 and the traveling lever 46 are simultaneously pressed together, and at this time, the automatic control switch 63 is turned 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 the automatic control traveling. In these configurations, even during the automatic control traveling, the manual control traveling can be prioritized by the operation force of the traveling lever 46 that overcomes the pressing force of the brake lining 58, so that it is safe.
[0026]
When switching from the automatic control traveling to the manual control traveling, the driving 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 portion 62a is rotated by the rotation of the pressing cam disc 62B. The traveling lever 46, in which the pressing force of the lever 61 is released to be in the free state and the rotational load is reduced, can be rotated by a small operating force to perform the manually controlled traveling. The operation of the pressing cam disk 62 may be automatically controlled by an electromagnetic clutch or the like.
[0027]
Switching between the automatic control operation for controlling the trunnion lever 51 of the HST device 1 and the manual control operation using the traveling lever 46 is different from the above-described embodiment, as shown in FIG. The fixed pressing cam disk 64A and the axially rotating pressing cam disk 65B are positioned relative to each other, and the convex claw portion 65a provided on the pressing cam disk 65A and the concave claw portion 65b provided on the pressing cam disk 65B are respectively positioned. At the same time, an operation rotary plate 69 whose both sides are sandwiched between brake linings 68 is positioned between the pressing cam plate 65B and a fixed plate 67 received at a shaft end of the drive shaft 64a with a washer 66, A gear portion of the operation rotary plate 69 is meshed with a gear portion of a rotary support plate 70 for controlling the trunnion lever 51 of the HST device 1 by operating the traveling lever 46, and the pressing cam disk is formed. 5B is provided with a shifter groove 65c in its width direction, a shifter 71 fitted in the shifter groove 65c is rotatably fixed to a shifter motor 72, and a limit switch 73 for turning ON / OFF a contact by the rotation of the shifter 71. Are arranged so as to be engaged with the rotation of the shifter 71.
[0028]
As shown in FIG. 10, when the automatic control switch 74 is turned on, the control motor 64 is driven, and at the same time, the relay 75 for driving the shifter motor 72 is operated, and the driving of the shifter motor 72 is turned on and off by the limit switch 73. A circuit is provided, and the control motor 64 is driven by the automatic control switch 74 of the electric circuit, and at the same time the shifter motor 72 is driven, and the press cam plate 65B is pressed by the shifter 71 toward the operation rotary plate 69 by the gap t. The pressing cam disk 65B is prevented from rotating by the frictional force of the brake lining 68, and the rotation is prevented by the convex claw 65a of the pressing cam disk 65A from acting on the concave claw portion 65b of the pressing cam disk 65B in the lateral direction. By the force, the pressing cam disc 65B is further operated via the brake lining 68. The moving platen 69 is strongly pressed to rotate the operation turning plate 69 by the drive shaft 64a of the control motor 64, and the operation turning plate 69 turns the turning support plate 70 so that the operation lever 46 and the traveling lever 46 are moved together. The trunnion lever 51 of the device 1 is rotationally braked so as to perform automatic control traveling.
[0029]
When switching from the automatic control traveling to the manual control traveling, by turning off the automatic control switch 74, the control motor 64 and the shifter motor 72 were turned off, and the operation rotary plate 69 was locked to the drive shaft 64a of the control motor 64. Since the pressing force of the pressing cam disk 65B is released and the pressing cam disk 65B is in a free state, the rotation load of the rotation support disk that meshes with the operation rotation disk 69 is reduced. The operation becomes lighter, and the manually controlled traveling can be smoothly performed.
[Brief description of the drawings]
FIG. 1 is a side view showing the entire combine.
FIG. 2 is a block diagram showing a hydraulic transmission configuration from a traveling hydraulic continuously variable transmission to a reaper.
FIG. 3 is a block diagram showing a relief valve control mechanism having a hydraulic power transmission configuration in FIG. 2;
FIG. 4 is a block diagram showing a synchronous interlocking control state of both the traveling and harvesting hydraulic continuously variable transmissions.
FIG. 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 the traveling hydraulic continuously variable transmission.
FIG. 7 is a front view showing a control mechanism of the traveling hydraulic continuously variable transmission.
FIG. 8 is a block diagram showing a control circuit of the traveling hydraulic continuously variable transmission.
FIG. 9 is a side view showing a control mechanism of the hydraulic stepless transmission for traveling.
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 Running mission case 8 Harvester
18 body
34 cutting blade device
35 raising device
42 Upper transfer device
43 Lower transport device
46 running lever
46b rotating support plate
49a hydraulic pump
49b hydraulic motor
52 trunnion lever
55 controllers
56 control motor
57 operation gear
58 brake lining
59 crimping machine
61 pressing spring
62A pressing cam board
62B pressing cam disk
62a convex nail
62b cam lever
63 automatic control switch
E engine

Claims

A hydraulic continuously variable transmission 1 for transmitting the power from the engine E to the traveling transmission case 3 in a continuously variable speed changeable manner, and a mowing device driven by the hydraulic continuously variable transmission 1 without shifting. A hydraulic pump 49a for driving is provided, and a hydraulic motor 49b, which is driven and rotated by oil supply from the hydraulic pump 49a for driving the reaper and whose rotational speed is changed by the operation of the trunnion lever 52, is provided. The rotation of the motor 49b drives the cutting blade device 34 and the raising device 35 of the mowing device 8 and drives the upper transport device 42 and the lower transport device 43 of the mowing device 8, and the travel lever 46 is operated. When the hydraulic continuously variable transmission 1 is continuously variable, the trunnion lever 52 of the hydraulic pump 49a for driving the reaper is operated to operate the hydraulic motor 49b. A configuration that driving rotation is interlocked so as to shift the manual transmission state to shift the hydraulic stepless transmission 1 the travel lever -46 is manually operated, control is provided in the vehicle body 18 - traveling lever by La 55 The operation gear 57 linked with the control motor 56 is rotated by the rotation of the traveling lever 46 so as to be able to switch to the automatic speed change control state in which the hydraulic continuously variable transmission 1 is shifted by automatically operating the gear 46. A left and right brake linings 58, 58 are provided between the support plate 46b and the crimping plate 59, and a pressing spring 61 for pressing the crimping plate 59 toward the rotation support plate 46b is provided. A pair of pressing cam discs 62A and 62B, whose other sides are freely movable to fix the shaft, are configured to abut against each other's convex claws 62a to press the pressing spring 61, so that the one side is freely movable. By rotating a cam lever 62b protruding in the outer peripheral direction from the rubber plate 62B, the convex claw portion 62a of the freely movable pressing cam disk 62B and the convex claw portion 62a of the shaft-fixed pressing cam disk 62A are mutually moved. The operating gear 57 and the traveling lever 46 are crimped and interlocked by the pressing action of the brake linings 58, 58 by the pressing spring 61, and the operation gear 57 and the traveling lever 46 are automatically crimped at the position where they are crimped and interlocked. A combine harvester transmission device comprising a traveling speed change control device, wherein a contact of a control switch 63 is turned on to drive the control motor 56 .