JP3727553B2

JP3727553B2 - Work machine operation structure

Info

Publication number: JP3727553B2
Application number: JP2001177066A
Authority: JP
Inventors: 吉弘上田; 之史山中
Original assignee: Kubota Corp
Current assignee: Kubota Corp
Priority date: 2001-06-12
Filing date: 2001-06-12
Publication date: 2005-12-14
Anticipated expiration: 2021-06-12
Also published as: KR100399705B1; KR20020094879A; CN1274197C; CN1390738A; JP2002362400A

Description

【０００１】
【発明の属する技術分野】
本発明は、変速操作具及び操向操作具を、左右一対の走行装置に個別に伝動する一対の無段変速装置に機械式連係機構を介して連係してある作業機の操作構造に関する。
【０００２】
【従来の技術】
従来、上記のような作業機の操作構造においては、例えば特開平８−３３１９７２号公報などで開示されているように、左右向きの軸心周りに回動する駆動軸に、その回動で左右向きの軸心周りに揺動し、かつ、駆動軸に対して相対摺動可能な一対の第１駆動揺動アームと、駆動軸に対して相対回動可能かつ相対摺動可能な一対の支持アームとを装備し、変速操作具と駆動軸とを、変速操作具の操作に連動して駆動軸が左右向きの軸心周りで回動するようにロッドを介して連結し、操向操作具と一対の第１駆動揺動アーム及び支持アームとを、操向操作具の操作に連動してその操作領域に対応する側の第１駆動揺動アーム及び支持アームが摺動するように、一対のワイヤ機構と縦向きの軸心周りに揺動する一対の第２駆動揺動アームとを介して連結し、一対の第１駆動揺動アーム及び支持アームと対応する無段変速装置とを、第１駆動揺動アーム及び支持アームの摺動、並びに、第１駆動揺動アームの揺動に連動して無段変速装置が変速操作されるように第１駆動揺動アーム及び支持アームと一体摺動し、かつ、第１駆動揺動アームの揺動に連動して前後向きの第１軸心周りに揺動する入力揺動スライドアームと、入力揺動スライドアームの摺動及び揺動に連動して前後向きの第２軸心周りに揺動する出力揺動アームと、出力揺動アームから無段変速装置にわたるワイヤ機構とを介して連結して、機械式連係機構を構成するとともに、変速操作具を中立位置に位置させた状態では、出力揺動アームが入力揺動スライドアームの摺動に伴って揺動しないように設定することで、変速操作具の操作では、一対の無段変速装置を同じ操作量で変速操作して左右の走行装置を等速駆動させる直進走行状態の現出を可能とし、又、その直進走行状態での操向操作具の操作によって、同じ操作量で変速操作されていた無段変速装置の操作量に差を与えて左右の走行装置を差動させる旋回走行状態の現出を可能にしていた。
【０００３】
【発明が解決しようとする課題】
しかしながら、上記の従来技術では、変速操作具の操作を、先ずロッド及び駆動軸を介して第１駆動揺動アームの左右向きの軸心周りの揺動に変換し、次に連係ロッドを介して入力揺動スライドアームの前後向きの第１軸心周りの揺動に変換し、更にカムフォロワーを介して出力揺動アームの前後向きの第２軸心周りの揺動に変換した後に、ワイヤ機構を介して無段変速装置に伝達し、又、操向操作具の操作を、先ずワイヤ機構を介して第２駆動揺動アームの縦向きの軸心周りの揺動に変換し、次に受動アームを介して第１駆動揺動アーム及び支持アームの摺動に伴う入力揺動スライドアームの摺動に変換し、更にカムフォロワーを介して出力揺動アームの前後向きの第２軸心周りの揺動に変換した後に、ワイヤ機構を介して無段変速装置に伝達するようにしていることから、機械式連係機構の構成が複雑化して組み付け性及びメンテナンス性が悪くなる不都合や製造コストが嵩む不都合などを招くようになっていた。
【０００４】
本発明の目的は、機械式連係機構の構成の簡素化を図れるようにして、組み付け性やメンテナンス性の向上、並びに、製造コストの削減などを図れるようにすることにある。
【０００５】
【課題を解決するための手段】
〔構成〕
上記目的を達成するため、本発明のうちの請求項１記載の発明では、変速操作具及び操向操作具を、左右一対の走行装置に個別に伝動する一対の無段変速装置に機械式連係機構を介して連係してある作業機の操作構造において、第１軸心周りに回動する回動部材に、その回動で前記第１軸心周りに揺動し、かつ、前記第１軸心と異なる方向の第２軸心周りに独立揺動可能な状態に一対の揺動アームを連結し、前記変速操作具と前記回動部材とを、前記変速操作具の操作に連動して前記回動部材が前記第１軸心周りで回動するように連動連結し、前記操向操作具と前記一対の揺動アームとを、前記操向操作具の操作に連動してその操作領域に対応する側の揺動アームが前記第２軸心周りで揺動するように連動連結し、前記一対の揺動アームと対応する前記無段変速装置とを、それぞれ一直線上で押し引き操作される摺動部材で連動連結するとともに、該摺動部材に、前記変速操作具を零速位置に位置させた状態での前記操向操作具の操作に基づく前記揺動アームの揺動方向に沿う方向の係合溝を形成して、該係合溝に対応する前記揺動アームを係合連結し、前記一対の揺動アームと対応する前記無段変速装置とを、前記変速操作具を零速位置に位置させた状態での前記操向操作具の操作に基づく前記揺動アームの揺動以外の揺動に連動して前記無段変速装置が変速操作されるように連動連結して、前記機械式連係機構を構成した。
【０００６】
〔作用〕
上記請求項１記載の発明によると、変速操作具の操作は、回動部材を介して両揺動アームの第１軸心周りの揺動に変換された後に各無段変速装置に伝達されるようになる。一方、操向操作具の操作は、変速操作具を零速位置に位置させた状態では、操向操作具の操作領域に対応する側の揺動アームの第２軸心周りの揺動に変換されるだけで各無段変速装置には伝達されることがなく、又、変速操作具を零速位置以外の位置に位置させた状態では、操向操作具の操作領域に対応する側の揺動アームの第２軸心周りの揺動に変換された後に対応する無段変速装置に伝達されるようになる。
【０００７】
つまり、変速操作具の操作を、両揺動アームの第１軸心周りの揺動に変換して各無段変速装置に伝達するだけの構成で、一対の無段変速装置を同じ操作量で変速操作して左右の走行装置を等速駆動させる直進走行状態を現出することができ、又、その直進走行状態での操向操作具の操作を、その操作領域に対応する側の揺動アームの第２軸心周りの揺動に変換して対応する無段変速装置に伝達するだけの構成で、同じ操作量で変速操作されていた各無段変速装置の操作量に差を与えて左右の走行装置を差動させる旋回走行状態を現出することができるようになる。しかも、変速操作具を零速位置に位置させた走行停止状態では、操向操作具を操作しても、その操作領域に対応する側の揺動アームが第２軸心周りに揺動するだけで無段変速装置は変速操作されないことから、走行停止状態を維持することができるようになる。
【０００８】
上記請求項１記載の発明によると、変速操作具を零速位置に位置させた走行停止状態では、操向操作具を操作しても、その操作領域に対応する側の揺動アームが摺動部材の係合溝に沿って揺動するだけとなって摺動部材は押し引き操作されないことから、各無段変速装置を変速操作することができないようになり、結果、操向操作具の操作にかかわらず走行停止状態を維持することができるようになる。又、変速操作具を零速位置以外の位置に位置させた直進走行状態では、操向操作具を操作すると、その操作領域に対応する側の揺動アームが係合溝の側壁を押圧する状態に揺動して摺動部材を押し引き操作することから、対応する無段変速装置を変速操作することができるようになり、結果、操向操作具の操作に応じた旋回走行状態を現出することができるようになる。
【０００９】
〔効果〕
従って、変速操作具及び操向操作具を一対の無段変速装置に連係する機械式連係機構の構成の簡素化を図りながら、変速操作具の操作による所望の直進走行状態の現出、及び、操向操作具の操作による所望の旋回走行状態の現出を可能にすることができ、もって、機械式連係機構の組み付け性やメンテナンス性の向上、並びに、製造コストの削減などを図れるようになった。又、変速操作具を零速位置に位置させた走行停止状態での操向操作具の誤操作によって機体が不測に旋回する不都合の発生を未然に回避できるようになった。
【００１０】
〔構成〕
本発明のうちの請求項２記載の発明では、上記請求項１記載の発明において、前記揺動アームにおける前記摺動部材との係合箇所に球状体を装備した。
【００１１】
〔作用〕
上記請求項２記載の発明によると、摺動部材の係合溝内での摺動部材に対する揺動アームの相対移動を円滑にすることができ、その分、揺動アームの揺動による摺動部材の押し引き操作をスムーズにすることができるようになる。
【００１２】
〔効果〕
従って、変速操作具による変速操作及び操向操作具による操向操作をより軽く行える操作性の面で有利なものにすることができた。
【００１３】
【発明の実施の形態】
〔第１実施形態〕
以下、本発明の第１実施形態について説明する。
【００１４】
図１には作業機の一例である自脱形コンバインの全体側面が示されており、このコンバインは、走行装置の一例である左右一対のクローラ式走行装置１の駆動で走行する走行機体２の前部に、植立穀稈を刈り取って後方に向けて搬送する刈取搬送装置３を昇降可能に連結し、走行機体２に、刈取搬送装置３からの刈取穀稈を受け取って脱穀・選別処理を施す脱穀装置４と、脱穀装置４からの穀粒を貯留する穀粒タンク５とを搭載するとともに、穀粒タンク５の前方箇所に搭乗運転部６を形成することによって構成されている。
【００１５】
図２〜４に示すように、このコンバインは、エンジン７からの動力を、ベルトテンション式の主クラッチ８を介してミッションケース９の入力軸１０に伝達し、この入力軸１０から無段変速装置１１の一例である走行用の一対の静油圧式無段変速装置１１と作業用の静油圧式無段変速装置１２とに分配伝達し、走行用の一方の静油圧式無段変速装置１１による変速後の動力を、左側のギヤ式変速装置１３を介して左側のクローラ式走行装置１に伝達し、走行用の他方の静油圧式無段変速装置１１による変速後の動力を、右側のギヤ式変速装置１３を介して右側のクローラ式走行装置１に伝達し、作業用の静油圧式無段変速装置１２による変速後の動力を、ベルトテンション式の刈取クラッチ１４を介して刈取搬送装置３に伝達するように構成されている。つまり、左右のクローラ式走行装置１は、対応する走行用の静油圧式無段変速装置１１を介して伝達されるエンジン７からの動力で個別に駆動されるようになっている。
【００１６】
左右のギヤ式変速装置１３の間には、それらの伝動軸１５同士を断続させることで、左右のクローラ式走行装置１を等速駆動する状態と左右のクローラ式走行装置１の作動を許容する状態とに切り換える多板式の油圧クラッチ１６が介装されている。
【００１７】
図４に示すように、ミッションケース９は、左右に分離可能な２分割構造で、左右のギヤ式変速装置１３や油圧クラッチ１６などを内装するとともに、その左側の側壁１７の一部が外方に向けて膨出することによって、走行用の各静油圧式無段変速装置１１と作業用の静油圧式無段変速装置１２とを収納する凹部１８を有するように形成されている。走行用の各静油圧式無段変速装置１１及び作業用の静油圧式無段変速装置１２は、ミッションケース９の凹部１８に、走行用としてのアキシャル形のピストンポンプ１９とピストンモータ２０とを２基ずつ収容し、作業用としてのアキシャル形のピストンポンプ２１とピストンモータ２２とを１基ずつ収容し、それらの対応するピストンポンプ１９，２１とピストンモータ２０，２２とを接続する油路が形成されたポートブロック２３を左側の側壁１７に連結して凹部１８を閉塞することによって構成されている。
【００１８】
つまり、ミッションケース９の側壁１７を各静油圧式無段変速装置１１，１２のケーシングに有効利用することから、部品点数や製造コストの削減を図れるようになり、又、側壁１７の凹部１８を利用して各静油圧式無段変速装置１１，１２を構成することで、各静油圧式無段変速装置１１，１２がミッションケース９の内方に大きく入り込むようになって、それらの配設に要する空間が小さくなることから、コンバイン全体としての小型化を図れるようになっている。
【００１９】
図１に示すように、搭乗運転部６には、変速操作具２４の一例である前後方向に揺動操作可能な単一の主変速レバー２４、前後方向に揺動操作可能な単一の副変速レバー２５、及び、操向操作具２６の一例である左右方向に揺動操作可能な単一の操向レバー２６、などが装備されている。
【００２０】
図５〜１０に示すように、主変速レバー２４及び操向レバー２６は、走行用の各静油圧式無段変速装置１１に機械式連係機構２７を介して連係されている。機械式連係機構２７は、第１軸心Ｐ１周りに回動する回動部材２８に、その回動で第１軸心Ｐ１周りに揺動し、かつ、第１軸心Ｐ１と直角をなす第２軸心Ｐ２周りに独立揺動可能な状態に一対の揺動アーム２９を連結し、主変速レバー２４と回動部材２８とを、主変速レバー２４の操作に連動して回動部材２８が第１軸心Ｐ１周りで回動するように押し引き式の第１連係具３０を介して連結し、操向レバー２６と各揺動アーム２９とを、操向レバー２６の操作に連動してその操作領域に対応する側の揺動アーム２９が第２軸心Ｐ２周りで揺動するように、一対の押し引き式の第２連係具３１を介して連結し、各揺動アーム２９と対応する静油圧式無段変速装置１１のトラニオン軸３２とを、揺動アーム２９の揺動に連動してトラニオン軸３２がその軸心Ｐ３周りで回動操作されるように押し引き式の第３連係具３３を介して連結することによって構成されるとともに、主変速レバー２４を零速位置となる中立位置に位置させた状態では、第２軸心Ｐ２が第３連係具３３の操作方向に沿うように設定されている。
【００２１】
回動部材２８は、ミッションケース９に隣接する支持枠３４に第１軸心Ｐ１周りに回動自在に支持された回動軸３５、及び、その両端に第１軸心Ｐ１周りに一体回動するように連結されたブラケット３６、などによって構成され、各ブラケット３６に対応する揺動アーム２９が第２軸心Ｐ２周りに揺動可能に支持されている。
【００２２】
第１連係具３０は、主変速レバー２４の前進増速方向（後進減速方向）となる前方への揺動操作に伴って回動部材２８を第１軸心Ｐ１周りに正転させる前進増速用の第１レリーズワイヤ３７と、主変速レバー２４の後進増速方向（前進減速方向）となる後方への揺動操作に伴って回動部材２８を第１軸心Ｐ１周りに逆転させる後進増速用の第２レリーズワイヤ３８とから構成されている。
【００２３】
各第２連係具３１は、操向レバー２６の中立位置から離れる方向への操作に伴って対応する揺動アーム２９を揺動操作するレリーズワイヤ３９と、揺動アーム２９及びレリーズワイヤ３９を介して操向レバー２６を中立位置に向けて付勢するバネ４０とから構成されている。
【００２４】
各第３連係具３３は、支持枠３４のレール４１によって案内される一対のローラ４２を備えるとともに、対応する揺動アーム２９の操作端が係合する係合溝４３が形成された摺動部材４４と、摺動部材４４からトラニオン軸３２の操作アーム４５にわたって架設されたロッド４６とから構成されており、揺動アーム２９の揺動に連動して、レール４１に沿って一直線上に押し引き操作することが可能になっている。係合溝４３は、主変速レバー２４を中立位置に位置させた状態での操向レバー２６の操作に基づく揺動アーム２９の揺動方向に沿うように形成されている。
【００２５】
尚、摺動部材４４の係合溝４３に係合する各揺動アーム２９の操作端には、係合溝４３内での摺動部材４４に対する揺動アーム２９の操作端の相対移動を円滑にして、揺動アーム２９の揺動による摺動部材４４の押し引き操作をスムーズにする球状体４７が装備されている。
【００２６】
走行用の各静油圧式無段変速装置１１のトラニオン軸３２は、対応する第３連係具３３が揺動アーム２９によって静油圧式無段変速装置１１側に押し込み操作されると、その軸心Ｐ３周りの前進増速方向（後進減速方向）に正転操作され、逆に、対応する第３連係具３３が揺動アーム２９によって静油圧式無段変速装置１１から離れる側に引き込み操作されると、その軸心Ｐ３周りの後進増速方向（前進減速方向）に逆転操作されるようになっている。
【００２７】
図示は省略するが、操向レバー２６は、その操作位置に基づいて油圧クラッチ１６に対する作動油の流動状態を切り換える切換弁が機械式又は電気式の連係機構を介して連係されており、操向レバー２６を中立位置に位置させた状態では、油圧クラッチ１６に作動油が供給されて左右のギヤ式変速装置１３の伝動軸１５同士を接続する油圧クラッチ１６の旋回不能状態が現出され、又、操向レバー２６を中立位置に位置させていない状態では、油圧クラッチ１６から作動油が排出されて左右のギヤ式変速装置１３の伝動軸１５同士を遮断する油圧クラッチ１６の旋回可能状態が現出されるようになっている。
【００２８】
以上の構成から、図８及び図９に示すように、主変速レバー２４を前後方向に揺動操作すると、その操作に連動して回動部材２８が第１軸心Ｐ１周りに回転するとともに両揺動アーム２９が第１軸心Ｐ１周りに一体揺動し、その揺動によって両第３連係具３３が同じ方向に同じ操作量で押し引き操作されて、両静油圧式無段変速装置１１のトラニオン軸３２が、主変速レバー２４の操作位置に応じた同じ操作位置に位置するようになる。これによって、主変速レバー２４を中立位置よりも前方側の前進操作領域で揺動操作すると、主変速レバー２４の操作位置に応じた駆動速度で左右のクローラ式走行装置１を等速正転駆動する前方直進状態を現出することができ、逆に、主変速レバー２４を中立位置よりも後方側の後進操作領域で揺動操作すると、主変速レバー２４の操作位置に応じた駆動速度で左右のクローラ式走行装置１を等速逆転駆動する後方直進状態を現出することができ、主変速レバー２４を中立位置に揺動操作すると、左右のクローラ式走行装置１を停止させる走行停止状態を現出することができるようになっている。
【００２９】
つまり、主変速レバー２４の操作によって、前後進の切り換えと無段階の変速操作とを行うことができ、もって、所望の速度での前方直進状態や後方直進状態を容易に現出できるようになっている。
【００３０】
上述した前方直進状態又は後方直進状態において、図１０に示すように、操向レバー２６を左右方向に揺動操作すると、その操作方向に対応する揺動アーム２９が第２軸心Ｐ２周りに揺動し、その揺動アーム２９に連係された第３連係具３３が押し引き操作されて、対応する静油圧式無段変速装置１１のトラニオン軸３２が、主変速レバー２４の操作位置に対応する操作位置から、操向レバー２６の中立位置からの操作量に応じた操作分だけ減速方向に操作されるようになる。これによって、操向レバー２６を中立位置よりも左側の操作領域に揺動操作すると、その操作方向に対応する左側のクローラ式走行装置１の駆動速度を操向レバー２６の中立位置からの操作量に応じた速度分だけ減速させて左右のクローラ式走行装置１を差動させる左旋回状態を現出することができ、逆に、操向レバー２６を中立位置よりも右側の操作領域に揺動操作すると、その操作方向に対応する右側のクローラ式走行装置１の駆動速度を操向レバー２６の中立位置からの操作量に応じた速度分だけ減速させて左右のクローラ式走行装置１を差動させる右旋回状態を現出することができるようになっている。
【００３１】
つまり、左右の各旋回状態では、旋回内側のクローラ式走行装置１を減速させることから、旋回外側のクローラ式走行装置１を増速させる場合に比較して、機体の旋回を円滑に行えるようになっている。
【００３２】
機械式連係機構２７は、操向レバー２６の揺動操作によって、対応する静油圧式無段変速装置１１のトラニオン軸３２を、主変速レバー２４の操作位置に対応する操作位置から、中立位置を超えた反対側の操作領域まで操作できるように構成されており、これによって、左右の旋回状態では、操向レバー２６の操作によって、左右のクローラ式走行装置１を同じ方向に駆動しながら速度差を与える通常旋回状態、一方のクローラ式走行装置１を駆動停止させるピボット旋回状態、及び、左右のクローラ式走行装置１を逆方向に駆動するスピン旋回状態のそれぞれを容易に現出できるようになっている。
【００３３】
更に、図５、図６及び図８に示すように、主変速レバー２４を中立位置に操作した走行停止状態では、操向レバー２６を揺動操作しても、その操作領域に対応する側の揺動アーム２９が摺動部材４４の係合溝４３に沿って揺動するだけとなって摺動部材４４は押し引き操作されないことから、各静油圧式無段変速装置１１のトラニオン軸３２を操作できないようになっており、結果、操向レバー２６の揺動操作にかかわらず走行停止状態を維持することができ、主変速レバー２４を中立位置に位置させた走行停止状態での操向レバー２６の誤操作によって機体が不測に旋回する不都合の発生を未然に回避できるようになっている。
【００３４】
尚、図示は省略するが、主変速レバー２４は、機械式又は電気式の連係機構を介して作業用の静油圧式無段変速装置１２のトラニオン軸に、主変速レバー２４が前進操作領域に操作されている状態では、作業用の静油圧式無段変速装置１２のトラニオン軸が主変速レバー２４の操作位置に対応する中立位置から正転（刈取搬送装置３が脱穀装置４に向けて穀稈を搬送する方向）側の操作位置に位置し、主変速レバー２４が後進操作領域に操作されている状態では、作業用の静油圧式無段変速装置１２のトラニオン軸が主変速レバー２４の操作位置にかかわらず中立位置に位置する状態となるように連係されており、これによって、前進作業走行時には、走行用の各静油圧式無段変速装置１１により変速される走行速度に同調して、刈取搬送装置３による穀稈の刈り取り搬送速度を変速することができ、もって、走行速度にかかわらず収穫する作物を好適な状態で刈り取り搬送することができるようになっている。
【００３５】
又、副変速レバー２５は、機械式又は電気式の連係機構を介してギヤ式変速機構１３に、副変速レバー２５の操作によって、走行用の各静油圧式無段変速装置１１による変速後の動力を高低２段に変速できるように連係されている。
【００３６】
〔別実施形態〕
以下、本発明の別実施形態を列記する。
〔１〕作業機としては、人参収穫機や大根収穫機などであってもよい。
〔２〕無段変速装置１１としてはベルト式無段変速装置などであってもよい。
〔３〕変速操作具２４としては変速ペダルなどであってもよい。
〔４〕操向操作具２６としてはステアリングホイールなどであってもよい。
〔５〕第１連係具３０及び第２連係具３１を、プッシュプルワイヤ又はロッドで構成するようにしてもよく、又、第３連係具３３を、プッシュプルワイヤ又はロッドあるいはレリーズワイヤとバネとから構成するようにしてもよく、第３連係具５７を、プッシュプルワイヤあるいはレリーズワイヤとバネとから構成するようにしてもよい。
〔６〕機械式連係機構２７としては、操向操作具２６の操作によって、左右の走行装置１を同じ方向に駆動しながら速度差を与える通常旋回状態のみを現出できるように構成されたものであってもよく、又、その通常旋回状態と、一方の走行装置１を駆動停止させるピボット旋回状態とを現出できるように構成されたものであってもよい。
〔７〕機械式連係機構２７を、左右の走行装置１を同じ方向に駆動しながら速度差を与える通常旋回状態のみの現出が可能な状態と、通常旋回状態に加えてピボット旋回状態の現出が可能な状態との２状態の切り換えが可能となるように構成してもよく、又、それらの２状態と、それらの２状態に加えて左右のクローラ式走行装置１を逆方向に駆動するスピン旋回状態の現出が可能な状態との３状態の切り換えが可能となるように構成してもよい。
【図面の簡単な説明】
【図１】自脱形コンバインの全体側面図
【図２】伝動構造を示す概略縦断背面図
【図３】伝動構造を示す概略縦断側面図
【図４】ミッションケースの縦断背面図
【図５】機械式連係機構の構成を示す縦断側面図
【図６】機械式連係機構の構成を示す平面図
【図７】機械式連係機構の構成を示す要部の縦断面図
【図８】走行停止時の機械式連係機構の状態を示す作用説明図
【図９】直進走行時の機械式連係機構の状態を示す作用説明図
【図１０】旋回走行時の機械式連係機構の状態を示す作用説明図
【符号の説明】
１走行装置
１１無段変速装置
２４変速操作具
２６操向操作具
２７機械式連係機構
２８回動部材
２９揺動アーム
４３係合溝
４４摺動部材
４７球状体
Ｐ１第１軸心
Ｐ２第２軸心[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an operating structure for a working machine in which a speed change operation tool and a steering operation tool are linked via a mechanical linkage mechanism to a pair of continuously variable transmissions that individually transmit a pair of left and right traveling devices.
[0002]
[Prior art]
Conventionally, in the operation structure of the working machine as described above, for example, as disclosed in Japanese Patent Application Laid-Open No. 8-331972, a drive shaft that rotates around a left-right axis is rotated to the left and right. A pair of first drive oscillating arms that oscillate around an orientation axis and can slide relative to the drive shaft, and a pair of supports that can rotate relative to the drive shaft and can slide relative to each other An arm, and the shift operation tool and the drive shaft are connected via a rod so that the drive shaft rotates about a left-right axis in conjunction with the operation of the shift operation tool. And the pair of first drive swing arm and support arm so that the first drive swing arm and support arm on the side corresponding to the operation area slide in conjunction with the operation of the steering operation tool. Through a pair of second drive swing arms swinging around a longitudinal axis A pair of first drive swing arms and a support arm and a corresponding continuously variable transmission are linked to the sliding of the first drive swing arm and the support arm and the swing of the first drive swing arm. Thus, the first drive center is slid integrally with the first drive swing arm and the support arm so that the continuously variable transmission is operated to shift, and the first axis is oriented forward and backward in conjunction with the swing of the first drive swing arm. An input swing slide arm swinging around, an output swing arm swinging around the second axis in the front-rear direction in conjunction with sliding and swinging of the input swing slide arm, and an output swing arm A mechanical linkage mechanism is configured by connecting via a wire mechanism extending across the continuously variable transmission, and the output swing arm slides on the input swing slide arm when the speed change operation tool is positioned at the neutral position. By setting so that it does not swing along with In the operation of the tool, it is possible to display a straight traveling state in which a pair of continuously variable transmissions are shifted with the same operation amount and the left and right traveling devices are driven at a constant speed, and the steering operation in the straight traveling state is enabled. Depending on the operation of the tool, the turning amount of the continuously variable transmission device that has been changed by the same amount of operation is given a difference so that the right and left traveling devices can be differentiated, thereby enabling the appearance of a turning traveling state.
[0003]
[Problems to be solved by the invention]
However, in the above prior art, the operation of the speed change operation tool is first converted into the swing around the axis of the first drive swing arm through the rod and the drive shaft, and then through the linkage rod. After the input swing slide arm is converted to swing about the first axial center in the front-rear direction, and further converted to swing about the second axial center in the front-rear direction of the output swing arm via the cam follower, the wire mechanism To the continuously variable transmission, and the operation of the steering operation tool is first converted into a swing around the longitudinal axis of the second drive swing arm via the wire mechanism, and then passively It is converted into the sliding of the input swing slide arm accompanying the slide of the first drive swing arm and the support arm via the arm, and further around the second axial center of the output swing arm via the cam follower. After converting to swing, it is connected to a continuously variable transmission via a wire mechanism. Since that way reached, it was supposed to lead to such construction increase is complicated to assemblability and disadvantages and manufacturing cost maintenance becomes poor disadvantageous mechanical linkage mechanism.
[0004]
An object of the present invention is to simplify the structure of a mechanical linkage mechanism so as to improve assemblability and maintainability and reduce manufacturing costs.
[0005]
[Means for Solving the Problems]
〔Constitution〕
In order to achieve the above object, according to the first aspect of the present invention, the shift operation tool and the steering operation tool are mechanically linked to a pair of continuously variable transmissions individually transmitting to a pair of left and right traveling devices. In the operating structure of the working machine linked through a mechanism, the rotating member that rotates around the first axis swings around the first axis by the rotation, and the first shaft A pair of swing arms are coupled in a state that allows independent swing about the second axis in a direction different from the center, and the shift operation tool and the rotating member are linked to the operation of the shift operation tool. A rotating member is interlocked and connected so as to rotate around the first axis, and the steering operation tool and the pair of swing arms are moved to the operation area in conjunction with the operation of the steering operation tool. swing arm of the corresponding side is interlocked so as to swing about the second axis, said pair of swing arms paired The continuously variable transmission is connected to each other by a sliding member that is pushed and pulled on a straight line, and the operation is performed with the transmission operating tool positioned at the zero speed position on the sliding member. The pair of swing arms is formed by forming an engagement groove in a direction along the swing direction of the swing arm based on the operation of the direction operation tool, and engaging and connecting the swing arm corresponding to the engagement groove. correspondence between the continuously variable transmission which, in conjunction with the swing of the other swinging of the swing arm based on the steering operation member of the operation in a state where the positioning the shift operation member to zero speed position and The mechanical linkage mechanism is configured by interlocking connection so that the continuously variable transmission is operated to change speed.
[0006]
[Action]
According to the first aspect of the present invention, the operation of the speed change operating tool is transmitted to each continuously variable transmission after being converted into the swing around the first axis of both swing arms via the rotating member. It becomes like this. On the other hand, the operation of the steering operation tool is converted into a swing around the second axis of the swing arm on the side corresponding to the operation region of the steering control tool in a state where the speed change operation tool is positioned at the zero speed position. Is not transmitted to each continuously variable transmission, and in a state where the speed change operation tool is located at a position other than the zero speed position, the swing on the side corresponding to the operation area of the steering operation tool is not performed. After being converted into swinging around the second axis of the moving arm, it is transmitted to the corresponding continuously variable transmission.
[0007]
That is, the operation of the speed change operation tool is simply converted into the swing around the first axis of both swing arms and transmitted to each continuously variable transmission, and the pair of continuously variable transmissions can be operated with the same operation amount. A straight traveling state in which the right and left traveling devices are driven at a constant speed by shifting operation can be displayed, and the operation of the steering operation tool in the straight traveling state can be swung on the side corresponding to the operation region. The structure is such that it is converted into a swing around the second axis of the arm and transmitted to the corresponding continuously variable transmission, and a difference is given to the operation amount of each continuously variable transmission that has been operated with the same operation amount. It is possible to present a turning traveling state in which the left and right traveling devices are differentiated. In addition, in the travel stop state where the speed change operation tool is positioned at the zero speed position, even if the steering operation tool is operated, the swing arm on the side corresponding to the operation region only swings around the second axis. Thus, since the continuously variable transmission is not operated to shift, the traveling stop state can be maintained.
[0008]
According to the first aspect of the present invention, in the travel stop state in which the speed change operation tool is positioned at the zero speed position, even if the steering operation tool is operated, the swing arm on the side corresponding to the operation area slides. Since the sliding member is not pushed / pulled only by swinging along the engaging groove of the member, each continuously variable transmission can no longer be speed-changed. It becomes possible to maintain the traveling stop state regardless of whether or not. In a straight traveling state in which the speed change operation tool is positioned at a position other than the zero speed position, when the steering operation tool is operated, the swing arm on the side corresponding to the operation region presses the side wall of the engagement groove. As the result, the corresponding continuously variable transmission can be shifted, and as a result, the turning traveling state corresponding to the operation of the steering operation tool is revealed. Will be able to.
[0009]
〔effect〕
Therefore, while simplifying the configuration of the mechanical linkage mechanism that links the transmission operation tool and the steering operation tool to the pair of continuously variable transmissions, the desired straight-ahead running state appears by the operation of the transmission operation tool, and It is possible to display a desired turning state by operating the steering operation tool, so that the assembly and maintenance of the mechanical linkage mechanism can be improved, and the manufacturing cost can be reduced. It was. In addition, it has become possible to avoid the occurrence of inconvenience that the airframe turns unexpectedly due to an erroneous operation of the steering operation tool when the shift operation tool is positioned at the zero speed position.
[0010]
〔Constitution〕
In the invention of claim 2, wherein one of the present invention, in the invention described in claim 1, wherein, equipped with a spherical body engagement portion between the slide member in said oscillating arm.
[0011]
[Action]
According to the second aspect of the present invention, the relative movement of the swinging arm with respect to the sliding member within the engaging groove of the sliding member can be made smooth, and the sliding by the swinging of the swinging arm is made correspondingly. The push-pull operation of the member can be made smooth.
[0012]
〔effect〕
Accordingly, it is possible to make the shift operation with the shift operation tool and the steering operation with the steering operation tool more advantageous in terms of operability.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
[First Embodiment]
The first embodiment of the present invention will be described below.
[0014]
FIG. 1 shows an entire side surface of a self-decomposing combine that is an example of a work machine, and this combine is a traveling machine body 2 that is driven by a pair of left and right crawler type traveling devices 1 that is an example of a traveling device. The front part is connected with a cutting and conveying device 3 that cuts and conveys the planted cereal toward the rear so that it can be moved up and down. The threshing device 4 to be applied and the grain tank 5 for storing the grain from the threshing device 4 are mounted, and the boarding operation unit 6 is formed at a location in front of the grain tank 5.
[0015]
As shown in FIGS. 2 to 4, the combine transmits the power from the engine 7 to the input shaft 10 of the transmission case 9 via the belt tension type main clutch 8, and the continuously variable transmission from the input shaft 10. 11 is distributed and transmitted to a pair of hydrostatic continuously variable transmissions 11 for travel and a hydrostatic continuously variable transmission 12 for work, which is an example of the travel 11, and by one hydrostatic continuously variable transmission 11 for traveling. The power after the shift is transmitted to the crawler type traveling device 1 on the left side through the left gear type transmission 13, and the power after the shift by the other hydrostatic continuously variable transmission 11 for traveling is transmitted to the right gear. Is transmitted to the crawler type traveling device 1 on the right side via the transmission 13 and the power after the shift by the working hydrostatic continuously variable transmission 12 is transferred via the belt tension type cutting clutch 14 to the cutting and conveying device 3. Configured to communicate to It has been. That is, the left and right crawler type traveling devices 1 are individually driven by the power from the engine 7 transmitted through the corresponding hydrostatic continuously variable transmission 11 for traveling.
[0016]
The transmission shafts 15 are intermittently connected between the left and right gear transmissions 13 to allow the left and right crawler traveling devices 1 to be driven at a constant speed and the left and right crawler traveling devices 1 to operate. A multi-plate hydraulic clutch 16 for switching to a state is interposed.
[0017]
As shown in FIG. 4, the transmission case 9 has a two-part structure that can be separated into left and right, and includes a left and right gear-type transmission 13 and a hydraulic clutch 16, and a part of the left side wall 17 is outward. Is formed so as to have a recess 18 that accommodates each hydrostatic continuously variable transmission 11 for traveling and the hydrostatic continuously variable transmission 12 for work. Each of the hydrostatic continuously variable transmission 11 for traveling and the hydrostatic continuously variable transmission 12 for work includes an axial piston pump 19 and a piston motor 20 for traveling in the recess 18 of the mission case 9. An oil passage that accommodates two each, accommodates one axial piston pump 21 and one piston motor 22 for work, and connects the corresponding piston pumps 19 and 21 and piston motors 20 and 22 is provided. The formed port block 23 is connected to the left side wall 17 to close the recess 18.
[0018]
In other words, since the side wall 17 of the transmission case 9 is effectively used for the casing of each hydrostatic continuously variable transmission 11, 12, the number of parts and the manufacturing cost can be reduced, and the concave portion 18 of the side wall 17 can be reduced. By using the hydrostatic continuously variable transmissions 11 and 12 to make use of the hydrostatic continuously variable transmissions 11 and 12, the hydrostatic continuously variable transmissions 11 and 12 greatly enter the inside of the mission case 9. Therefore, the size of the combine as a whole can be reduced.
[0019]
As shown in FIG. 1, the boarding operation unit 6 includes a single main transmission lever 24 that is swingable in the front-rear direction, which is an example of the shift operation tool 24, and a single sub-shifter that is swingable in the front-rear direction. A shift lever 25 and a single steering lever 26 that is an example of the steering operation tool 26 that can swing in the left-right direction are provided.
[0020]
As shown in FIGS. 5 to 10, the main transmission lever 24 and the steering lever 26 are linked to each traveling hydrostatic continuously variable transmission 11 via a mechanical linkage mechanism 27. The mechanical linkage mechanism 27 is moved to the rotating member 28 that rotates about the first axis P1 and swings about the first axis P1 by the rotation, and is perpendicular to the first axis P1. A pair of oscillating arms 29 are coupled so as to be able to oscillate independently about the biaxial center P2, and the main transmission lever 24 and the rotary member 28 are linked to each other by operating the main transmission lever 24. The first lever 30 is connected via a push-pull type first linkage 30 so as to rotate around the first axis P <b> 1, and the steering lever 26 and each swing arm 29 are interlocked with the operation of the steering lever 26. The swing arm 29 on the side corresponding to the operation region is connected via a pair of push-pull type second linkages 31 so that the swing arm 29 swings around the second axis P <b> 2. The trunnion shaft 32 of the hydrostatic continuously variable transmission 11 is connected to the trunnion shaft 32 in conjunction with the swing of the swing arm 29. The main transmission lever 24 is positioned at the neutral position that is the zero-speed position while being connected via a push-pull type third linkage 33 so as to be rotated around the axis P3. In the state, the second axis P <b> 2 is set so as to follow the operation direction of the third linkage 33.
[0021]
The rotating member 28 is integrally rotated around the first axis P1 at both ends thereof, with a rotating shaft 35 supported by the support frame 34 adjacent to the mission case 9 so as to be rotatable around the first axis P1. The swing arm 29 corresponding to each bracket 36 is supported so as to be swingable around the second axis P2.
[0022]
The first linkage 30 is a forward acceleration that causes the rotating member 28 to rotate forward around the first axis P1 in accordance with the forward swinging operation of the main transmission lever 24 in the forward acceleration direction (reverse deceleration direction). The first release wire 37 and the reverse shift increase that reversely rotates the rotating member 28 around the first axis P1 in accordance with the backward swinging operation in the reverse speed increasing direction (forward decelerating direction) of the main transmission lever 24. The second release wire 38 for speed is used.
[0023]
Each of the second linking tools 31 is provided via a release wire 39 that swings the corresponding swing arm 29 in accordance with an operation in a direction away from the neutral position of the steering lever 26, and the swing arm 29 and the release wire 39. And a spring 40 that urges the steering lever 26 toward the neutral position.
[0024]
Each third linkage 33 includes a pair of rollers 42 guided by the rails 41 of the support frame 34, and a sliding member in which an engagement groove 43 is formed to engage the operation end of the corresponding swing arm 29. 44 and a rod 46 extending from the sliding member 44 to the operation arm 45 of the trunnion shaft 32, and pushed and pulled in a straight line along the rail 41 in conjunction with the swing of the swing arm 29. It is possible to operate. The engagement groove 43 is formed along the swinging direction of the swinging arm 29 based on the operation of the steering lever 26 with the main transmission lever 24 positioned at the neutral position.
[0025]
The operating end of each swing arm 29 engaged with the engaging groove 43 of the sliding member 44 smoothly moves relative to the operating end of the swing arm 29 with respect to the sliding member 44 within the engaging groove 43. Thus, a spherical body 47 is provided which makes smooth the pushing and pulling operation of the sliding member 44 by swinging the swing arm 29.
[0026]
The trunnion shaft 32 of each hydrostatic continuously variable transmission 11 for traveling is pivoted when the corresponding third linkage 33 is pushed by the swing arm 29 toward the hydrostatic continuously variable transmission 11 side. A forward rotation is performed in the forward acceleration direction (reverse deceleration direction) around P3, and conversely, the corresponding third linkage 33 is retracted to the side away from the hydrostatic continuously variable transmission 11 by the swing arm 29. And the reverse operation is performed in the reverse acceleration direction (forward deceleration direction) around the axis P3.
[0027]
Although not shown, the steering lever 26 is linked with a switching valve for switching the flow state of the hydraulic oil with respect to the hydraulic clutch 16 based on the operation position via a mechanical or electrical linkage mechanism. When the lever 26 is in the neutral position, hydraulic oil is supplied to the hydraulic clutch 16 and the hydraulic clutch 16 that connects the transmission shafts 15 of the left and right gear transmissions 13 appears to be unable to turn. In a state where the steering lever 26 is not positioned at the neutral position, the hydraulic clutch 16 that is capable of turning the hydraulic clutch 16 that cuts off the transmission shafts 15 of the left and right gear transmissions 13 by discharging the hydraulic oil from the hydraulic clutch 16 appears. It has come out.
[0028]
With the above configuration, as shown in FIGS. 8 and 9, when the main speed change lever 24 is swung in the front-rear direction, the rotating member 28 rotates around the first axis P1 in conjunction with the operation. The swing arm 29 swings integrally around the first axis P1, and both the third linkages 33 are pushed and pulled in the same direction with the same operation amount by the swing, so that the both hydrostatic continuously variable transmission 11 is operated. The trunnion shaft 32 is located at the same operation position corresponding to the operation position of the main speed change lever 24. As a result, when the main speed change lever 24 is swung in the forward operation region ahead of the neutral position, the left and right crawler type traveling devices 1 are driven at constant speed in the forward direction at a drive speed corresponding to the operation position of the main speed change lever 24. In contrast, when the main speed change lever 24 is swung in the reverse operation region on the rear side of the neutral position, the left and right sides are driven at the drive speed corresponding to the operation position of the main speed change lever 24. The crawler type traveling device 1 can be driven in a straight-reverse direction in which the crawler type traveling device 1 is driven in reverse rotation at a constant speed, and when the main transmission lever 24 is swung to the neutral position, It is possible to appear.
[0029]
In other words, the operation of the main speed change lever 24 allows the forward / reverse switching and the stepless speed change operation to be performed, so that the forward straight traveling state and the backward straight traveling state at a desired speed can be easily displayed. ing.
[0030]
As shown in FIG. 10, when the steering lever 26 is swung in the left-right direction in the straight forward or backward straight state described above, the swing arm 29 corresponding to the operation direction swings around the second axis P2. The third linkage 33 linked to the swing arm 29 is pushed and pulled, and the corresponding trunnion shaft 32 of the hydrostatic continuously variable transmission 11 corresponds to the operation position of the main transmission lever 24. From the operation position, an operation corresponding to the operation amount from the neutral position of the steering lever 26 is operated in the deceleration direction. Accordingly, when the steering lever 26 is swung to the left operation region from the neutral position, the driving speed of the left crawler type traveling device 1 corresponding to the operation direction is changed from the neutral position of the steering lever 26 to the operation amount. Accordingly, a left-turning state in which the left and right crawler type traveling devices 1 are differentiated by decelerating by a speed corresponding to the speed can be displayed. Conversely, the steering lever 26 is swung to the operation region on the right side of the neutral position. When operated, the drive speed of the right crawler type traveling device 1 corresponding to the operation direction is decelerated by the speed corresponding to the operation amount from the neutral position of the steering lever 26, and the left and right crawler type traveling devices 1 are differentiated. The right turn state can be displayed.
[0031]
That is, in each of the left and right turning states, the crawler type traveling device 1 on the inner side of the turning is decelerated, so that the aircraft can be smoothly turned as compared with the case where the crawler type traveling device 1 on the outer side of the turning is accelerated. It has become.
[0032]
The mechanical linkage mechanism 27 moves the trunnion shaft 32 of the corresponding hydrostatic continuously variable transmission 11 from the operation position corresponding to the operation position of the main transmission lever 24 by the swinging operation of the steering lever 26. It is configured to be able to operate up to the operation area on the opposite side, and in this way, in the left and right turning state, the left and right crawler type traveling devices 1 are driven in the same direction by the operation of the steering lever 26. It is possible to easily present the normal turning state that gives the drive, the pivot turning state in which one of the crawler type traveling devices 1 is driven and stopped, and the spin turning state in which the left and right crawler type traveling devices 1 are driven in opposite directions. ing.
[0033]
Further, as shown in FIGS. 5, 6, and 8, in the traveling stop state in which the main transmission lever 24 is operated to the neutral position, even if the steering lever 26 is swung, the side corresponding to the operation region is Since the swing arm 29 only swings along the engagement groove 43 of the slide member 44 and the slide member 44 is not pushed and pulled, the trunnion shaft 32 of each hydrostatic continuously variable transmission 11 is moved. As a result, the traveling stop state can be maintained regardless of the swinging operation of the steering lever 26, and the steering lever in the traveling stop state in which the main transmission lever 24 is positioned at the neutral position. Therefore, it is possible to avoid the occurrence of inconvenience that the aircraft turns unexpectedly due to 26 erroneous operations.
[0034]
Although not shown, the main transmission lever 24 is connected to the trunnion shaft of the working hydrostatic continuously variable transmission 12 via a mechanical or electrical linkage mechanism, and the main transmission lever 24 is moved to the forward operation region. In the operated state, the trunnion shaft of the working hydrostatic continuously variable transmission 12 is rotated forward from the neutral position corresponding to the operation position of the main shift lever 24 (the cutting and conveying device 3 is directed toward the threshing device 4). When the main transmission lever 24 is operated in the reverse operation region, the trunnion shaft of the working hydrostatic continuously variable transmission 12 is connected to the main transmission lever 24. It is linked so as to be in a neutral position regardless of the operation position, and in this way, during forward work traveling, it synchronizes with the traveling speed changed by each hydrostatic continuously variable transmission 11 for traveling. , Mowing transport equipment 3 by can shift the mowing conveying speed of the culms, has been, and is capable of mowing conveyed in a state suitable crops to harvest regardless of travel speed.
[0035]
The auxiliary transmission lever 25 is connected to the gear-type transmission mechanism 13 via a mechanical or electric linkage mechanism, and the sub-transmission lever 25 is operated to operate the sub-transmission lever 25 after shifting by each hydrostatic continuously variable transmission 11 for traveling. It is linked so that the power can be shifted in two steps.
[0036]
[Another embodiment]
Hereinafter, other embodiments of the present invention will be listed.
[1] The working machine may be a carrot harvester or a radish harvester.
[2] The continuously variable transmission 11 may be a belt type continuously variable transmission or the like.
[3] The shift operation tool 24 may be a shift pedal or the like.
[4] The steering operation tool 26 may be a steering wheel or the like.
[5] The first linkage 30 and the second linkage 31 may be formed of push-pull wires or rods, and the third linkage 33 may be formed of push-pull wires or rods or release wires and springs. Alternatively , the third linkage 57 may be formed of a push-pull wire or a release wire and a spring.
[6] The mechanical linkage mechanism 27 is configured such that only the normal turning state in which a speed difference is given while driving the left and right traveling devices 1 in the same direction can be displayed by operating the steering operation tool 26. Alternatively, the normal turning state and the pivot turning state in which one of the traveling devices 1 is stopped can be displayed.
[7] The mechanical linkage mechanism 27 is capable of appearing only in a normal turning state that gives a speed difference while driving the left and right traveling devices 1 in the same direction, and in a pivoting state in addition to the normal turning state. It may be configured to be able to switch between two states with the state where it can be removed, and in addition to these two states, the left and right crawler type traveling devices 1 are driven in opposite directions. You may comprise so that switching of three states with the state in which the spin turning state which can be performed can be performed is attained.
[Brief description of the drawings]
[Fig. 1] Overall side view of self-decomposing combine [Fig. 2] Schematic longitudinal rear view showing the transmission structure [Fig. 3] Schematic longitudinal side view showing the transmission structure [Fig. 4] Vertical rear view of the transmission case [Fig. 5] FIG. 6 is a plan view showing the structure of the mechanical linkage mechanism. FIG. 7 is a longitudinal sectional view of the main part showing the structure of the mechanical linkage mechanism. FIG. FIG. 9 is an operation explanatory view showing the state of the mechanical linkage mechanism during straight traveling. FIG. 10 is an operation explanatory view showing the state of the mechanical linkage mechanism during turning. [Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Traveling device 11 Continuously variable transmission 24 Shifting operation tool 26 Steering operation tool 27 Mechanical linkage mechanism 28 Rotating member 29 Swing arm 43 Engaging groove 44 Sliding member 47 Spherical body P1 1st axis P2 2nd axis heart

Claims

The shift operation tool (24) and the steering operation tool (26) are linked via a mechanical linkage mechanism (27) to a pair of continuously variable transmissions (11) that are individually transmitted to the pair of left and right traveling devices (1). The operation structure of a working machine
The rotating member (28) rotating around the first axis (P1) swings around the first axis (P1) by the rotation, and is different from the first axis (P1). A pair of swing arms (29) are coupled so as to be independently swingable around a second axis (P2) in the direction, and the shift operation tool (24) and the rotating member (28) are connected to the shift gear. In conjunction with the operation of the operation tool (24), the rotation member (28) is interlocked and connected so as to rotate around the first axis (P1), and the steering operation tool (26) and the pair of The swing arm (29) on the side corresponding to the operation area is swung around the second axis (P2) in conjunction with the operation of the steering operation tool (26). the continuously variable transmission (11) and a pulling operation of pressing on each straight line interlocking connected to the corresponding said pair of swing arms (29) The sliding operation tool (26) is operated in a state in which the shifting operation tool (24) is positioned at the zero speed position on the sliding member (44). An engaging groove (43) in a direction along the swinging direction of the swinging arm (29) is formed, and the swinging arm (29) corresponding to the engaging groove (43) is engaged and connected. The pair of swing arms (29) and the corresponding continuously variable transmission (11) are connected to the steering operation tool (26) in a state in which the speed change operation tool (24) is positioned at the zero speed position. The mechanical linkage mechanism (27) is interlocked and connected so that the continuously variable transmission (11) is operated in response to a swing other than the swing of the swing arm (29) based on the operation of The operation structure of the work machine that is configured.

The operating structure of the working machine according to claim 1, wherein a spherical body (47) is provided at a position where the swing arm (29) is engaged with the sliding member (44).