201117709 六、發明說明： 【發明所屬之技術領域】 本發明係關於聯合收穫機。 【先前技術】 以往’已知於以行進用靜油壓式無段變速裝I驅動之 行進裝置之上側左右並列設有脫穀裝置與縠粒槽，於穀粒 槽之前側設有操縱部’於操縱部及脫縠装置之前側設有收 割裝置’並設有變更行進用靜油壓式無段變速裝褒之油壓 泵之斜板即泵斜板之傾斜角度之變速桿之聯合收穫機。 度盤之技術。 【專利文獻1】 此外，如專利文獻丨所示，已知於具有以行進用靜油 壓式無段變速裝置驅動之行進裝置之作業車輛設置設定將 變速桿操作至最高速位置時之最高車速之最高車速設定刻 日本特開2007-2305 18號公報 【發明内容】 而，在重複高速之農地間移動與低速 之收割作業之201117709 VI. Description of the Invention: [Technical Field to Which the Invention Is Ascribed] The present invention relates to a combine harvester. [Prior Art] Conventionally, it is known that a threshing device and a gutter groove are arranged side by side on the upper side of the traveling device driven by the traveling static hydraulic type stepless speed change device I, and a manipulating portion is provided on the front side of the grain groove. A combine harvester is provided with a harvesting device on the front side of the operating portion and the dislocating device and a shifting lever for changing the inclination angle of the pump swash plate of the hydraulic pump of the static oil pressure type stepless speed change device for traveling . The technology of the dial. [Patent Document 1] Further, as shown in the patent document ,, it is known that the maximum vehicle speed when the shift lever is operated to the highest speed position is set in the work vehicle setting setting of the traveling device driven by the traveling static oil type stepless speed change device. The maximum speed setting is disclosed in Japanese Patent Laid-Open Publication No. 2007-2305 No. 18 [Invention], and the high-speed agricultural land movement and the low-speed harvesting operation are repeated.
縱方向之操作便困難等問題。 設定最高車速，無法以 反之，若以收割作業時為基準 4 201117709 適於路上行進之高速行進，農地間移動需要時間而作業效 率降低。 本發明為解決上述之課題而採用以下之技術手段。 即，請求項1記載之發明係一種聯合收穫機，在被以 行進用靜油壓式無段變速裝置（12)驅動之行進裝置（3)之上 側j右並列設置脫殼裝置（2)與縠粒槽（5)，於該榖粒槽 之前側設置操縱部（6)，於該操縱部（6)及脫殼裝置（2)之前側 設置收割裝置(4 )，並設置用以變更前述行進用靜油壓式無 段變速裝置（12)之油壓泵⑽之斜板即泉斜板（15)之傾斜角 度之變速搖桿（13)，其特徵在於：使前述行進用靜油壓式無 段變速裝置（12)之油壓馬達（16)之斜板即馬達斜板⑽之傾 斜角度可於低速行進侧與高速行進側進行切換，並設置在 將該馬達斜板（17)之傾斜角度切換至低速行進側之狀態下 變更设定將前述變速搖桿（13)操作為最高速位置時之最高 車速之最高車速設定刻度盤（51)。 凊求項2記載之發明係如請求項丨之聯合收穫機，其 中，使以前述最高車速設定刻度盤（51)進行之最高車速之設 定僅在前述馬達斜板（丨7)之傾斜角度被切換至低速行進側 之狀態下為有效，在以該最高車速設定刻度盤（51)設定最高 車速後馬達斜板7)之傾斜角度從低速行進側被切換至高 速行進側時，使以前述最高車速設定刻度盤（5 1)進行之最高 車速之設定為無效。 根據請求項1記載之發明，由於藉由最高車速設定刻 度盤（51)之操作使前述行進用靜油壓式無段變速裝置（12)之 201117709 :由壓馬達（16)之斜板即馬達斜板（17)之傾斜角度切換至低速 丁進側之狀態下變更設定將前述變速搖桿⑴)操作為最高 速^置時之最尚車速，故可將車速之變速範圍限制於適於 農地條件或作物條件之範圍，可提高收割作業中之聯合收 穫機之操作性及收割作業之效率。 根據請求項2記載之發明，除可發揮上述請求項丨記 載之發明之效果外，由於在為農地間移動而將靜油壓式無 •k蜒速裝置（12)之油壓馬達（丨6)之斜板即馬達斜板（1 7)之傾 斜角度切換至高速行進側後，使上述之收割作業時之最高 車速之設定為無效，故可省略以手動解除此最高車速之設 定之操作，可更提高重複高速之農地間移動與低速之收割 作業之聯合收穫機之操作性及收割作業之效率。 【實施方式】 基於圖面說明本發明之實施之形態。 於圖1顯示聯合收穫機之機體構成。 此聯合收穫機係於機體架1之下側設有具備履帶3A之 行進裝置3,於機體架1之上部左側搭載有脫穀裝置2,於 該脫穀裝置2之右側搭載有具備排出螺旋7之縠粒槽5，於 此穀粒槽5之前側設有操縱部6，於此操縱部6與脫穀裝置 2之前側設有收割裝置4之構成。 前述收割裝置4係從前侧具備分草體8、拉起裝置8a、 收割刀9、搬送裝置9A之構成。 於前述脫穀裝置2之上部外側設將從收割敦置4側之 6 201117709 搬送裝置9A搬送來之穀桿供給至脫穀室之進給鏈ι〇,於此 進給鏈10之上側設對向於進給鏈10之挾扼杆（圖示省略）。 此外’於此進給鏈10之始端部内側設從搬送裝置9A 往進給鏈10轉交榖桿之輔助鏈11。 於圖2顯示聯合收穫機之傳動機構。 於搭載於操縱部6之下部之引擎22之輸出軸22 A固定 收割脫榖用輸出滑輪25B ’於此收割脫榖用輸出滑輪25b 與固定於中間軸29之一端之中間滑輪28捲繞具備收割脫 縠離合器44之傳動皮帶44A。此外’使固定於中間軸29 之另一端之中間齒輪30與固定於齒輪箱5〇内之中間傳動 軸3 1之中間齒輪30a咬合，使固定於中間傳動軸3丨之—端 之傘齒輪32與固定於脫穀傳動軸33之—端之傘齒輪32a 咬合。此外，使為從固定於脫縠傳動軸33之另一端之中間 滑輪33A透過皮帶傳動機構33B旋轉驅動分離胴34與處理 胴3 5之構成。 此外’使為使固定於中間輸出軸41之_端之中間齒輪 36A與固定於前述中間傳動軸31之另—端之中間齒輪％， 從固定於該中間輸出轴41之另一端部之輸出滑輪“A透過 皮帶傳動機構41B驅動以風鼓42為首之選別部㈣、捲繞 進給鏈10之後部之鏈輪43之構成。 此外，於前述齒輪箱50之操縱部6側之面安裝收割搬 t用靜油壓式無段變速裝置21，使固定於該收割搬送用靜 =壓式無段變速裝置21之輪入轴37之輪入齒輪37A咬合 1述中間齒輪36A。此外’使為從收割搬送用靜油壓式無 201117709 段變速裝置21之輸出轴38與以检槽連接之 過齒輪傳動機構38B、38C分歧驅動固〜 透 之收宝j铪屮妯 弋收割輸出滑輪45 二收d輸出軸39與固定捲繞輔助鏈1 軸40之士、从 之鏈輪4〇A之輸出 ==。於固定於前述收割輸出滑輪Μ與收割裝置4 47 A之外側端部之收割輸人滑輪Μ捲繞傳動皮帶 另一方面，於固定於前述引擎22之輸 卜 用輸出滑輪25A與固定於安裝於行進用之任務㈣之仃： 之行進用靜油壓式無段變速裝置12之輸 目=上部 輪26捲繞傳動皮帶12B。 2A之輸入滑 於圖3顯示任務箱18内之傳動機構。 於^務箱18之上部設以行進用靜油壓式無 U之油壓馬達16之輸出驅動 义裝置 入軸65之輸出齒於.八认 使固定於此輪 之輸出齒輪66咬合於固定於令間轴66八 輪_。此外，使固定於中間轴66a之 齒 於固定於側離人舳6 ]齒輪66C咬合 齒輪68之左右兩側設左右之側離合器69、69。 動 Μ::/吏前述被動齒輪68咬合於固定於傳動轴71之 側左—被動齒輪72 ’於此第二被動齒輪72之左右 =右對稱設左右之行星齒輪機“、7。 ：兩 構7〇係於圓筒形狀之行星齒 苗丨輪機 別軸承具備有效納… 周方向隔間隔分 、谞，双且仫相異之兩個 74，使令門杆居音,7 數之行星齒輪 便尹間灯星齒輪76與此行星齒輪74咬入 輪 旋轉地輛承於驅動軸71之輪 二吏 '自由 面輪75之小狴齒部與此尹 8 201117709 間行星齒輪76咬合，使前述行星齒輪74之大徑齒部咬合 於固定於前述傳動軸71之太陽齒輪71A之構成。此外，於 月J述行星齒輪木73與任務箱丨8之間設限制行星齒輪架 之旋轉之多板式之煞車77。 此外’使則述輸出齒輪75之大徑齒部咬合於可自由旋 轉地軸承於中間軸7 5之中間齒輪7 5 B之大徑齒部，使此中 間齒輪75B之小徑齒部咬合於固定於減速轴75c之一端之 大徑齒輪75D。此外’使為使固定於前述減速轴况之另 -端之小徑齒輪75E咬合於固定於車軸之—端部之車 軸齒輪76G。於固定於此鱼紅Λ σ 此皁軸76F之另一端部之驅動鏈輪 76H捲繞履帶3A之前部並驅動之構成。則係限制前述驅 動軸7 1動作之停車煞車器。 藉由以上之構成，在連接左右之側離合器的之狀能下 直進行進，傾倒操作方向操縱桿6八後，首先，此傾倒操作 側之側離合器69被遮斷，操縱方向操縱桿6a之傾倒操作 角度越大’旋回内側之車軸76F之旋轉速度越低，在行星 齒輪架73停止之狀態τ，旋回外側與旋回内側之車轴⑽ 彼此反向旋轉而原地迴轉。 另外，使前述中間軸66Α之端部往任務箱^之 出’於此中間#由66Α之突出端部設形成為角軸或 ： 旋轉操作部⑽。藉此，在使為前述行進用靜油壓式無 速裝置12之油壓馬達16之輸出軸與前述輸入軸 ： 槽嵌合而連接之構成之狀況，於將行進用 曰/ 速裝置12安裝於任務箱丨8時，旋# 工“、奴變 奴轉操作旋轉操作部66可 9 201117709 使輸入軸65之栓槽之相位與行進用靜油Μ無段變速裝置 η側之油麼馬達16之輸出軸之栓槽之相位容易配合。其結 果’可使行進用靜油^無段變速蓑置12之安裝作業容易 進行。 ' 於圖4顯示行㈣靜㈣式無段變速裝置12及收割搬 送用靜油屢式無段變速裝置21之油壓回路。 前述行進用靜油壓式無段變速裝置12係以變更油壓泵 14之斜板即泵斜板15之傾斜角度，變更從此油壓泵"往 油麗馬達16之送油量，將此油壓馬達16之輸出軸之轉速 無段變速之構成。此外，設置變更此泵斜板15之傾斜角度 之複動汽紅95’設往此複動汽虹％供給作動油之間94， 設置無段調整此閥94之開度之電磁線圈93。此外，使為設 置與油壓泵14之輸入軸12Α同軸驅動之供給栗85，將此供 π泵85之吐出油補給至連通油壓泵14與油壓馬達μ之間 之閉回路12Τ之構成。 此外，設置兩階段切換此油壓馬達16之斜板即馬達斜 板17之傾斜角度之油壓缸19,設往此油壓缸供給作動油之 閥97’❺置使此閥97之切換作動之電 馬達斜…傾斜角度之切換，可將此油壓馬達二 出軸之轉速切換為低速行進側與高速行進側。 此外，於前述收割搬送用靜油壓式無段變速裝置2丨内 之閉回路係使為將從前述行進用靜油壓式無段變速裝置Η 之供給泵85輸送之作動油以分流闊92Α分流供給之構成。 如上述’由於在行進用靜油壓式無段變速裝置Η與收割搬 201117709 送用靜油壓式^ '速裝置21共用供給泵85,故可降低盤 造成：而廉價提供。另外，於前述分流間92A之送油方向 ^游：置過據B 92。此外’於使通過此收割搬送用靜油壓 ^ :奴變速裝置21之油壓泵89與油壓馬達9〇之間之閉回 路°又置使㈤壓側之油路與低壓側之油路短路之油路，於此 油路設置單向閱”。藉此，於從油壓…作動油： 方向變為逆向之狀況，{會將此作動油往油壓馬達90送 Γ,ΓΓ止油壓馬達9G之反轉。其結果，可防止收割裝置 驅動，可防止收割裝置4之破損。此外，不必於從 :割搬送、用靜油壓式無段變速裝置2"主收割裝置4之傳動 径中設置單向離合器，故可降低製造成本而廉價提供。 於圖5顯示方塊回路圖。 f署制器55與引擎控制器57與靜油壓式無段變速 二…工J益56之間連接為可通信以構成車内區域網路。於 :述主控制器55之輸入側連接檢出設於操縱部6之側部之 作角度之電位計i3A、撿出設於二 方向刼縱桿6A之左右操作角度之電位計6β、檢 、之車速感測H 58、將行進用靜油壓式無段變速 行之壓？達16之馬達斜板17切換為低速行進側與高、速 之口」：副變速開關17B、實行使左右之履帶彼此反轉旋回 ^轉時操作之迴轉開關61、變更設定將變迷搖桿Η 出=位置時之最高車速之最高車速設定刻度盤Η、檢 二靜:壓式無段變速裝置12之油…之泵斜板 貝斜角度之斜板角度感測器15S、檢出踩下操作停車 11 201117709 …、車器7 1B之停車煞車踏板（圖示省略）之踩下角度之停車 煞車感測器7 1 S。 月|J述最尚車速設定刻度盤5丨係如圖6所示設於配置 於操縱部6之前部左側之前上傾斜姿勢之面板5iA之下 P於此面板5 1 A集中配置有自動控制機能之啟用停止操 作用之夕數之開關（圖示省略）。 此外，於主控制器55之輸出侧連接遮斷操作左右之側 離。器69之側離合器電磁線圈69L、69R、使控制往左右之 煞車77之送油壓之比例減壓閥作動之左右之煞車電磁線圈 77L、77R、切換馬達斜板丨7之傾斜角度之閥97之電磁線 圈96隻更操作收割搬送用靜油壓式無段變速裝置21之油 之斜板角度之變速馬達2 1A。此外，將前述副變速 開關17B換為檢出收割離合器或脫穀離合器被連接操作之 開關亦可。藉此，在收割離合器或脫穀離合器被連接操作 時’行進用靜油屋式無段變速裝置12之油壓馬達16之馬 達斜板1 7之傾斜角度從高速行進側自動切換為低速行進 側，成為適於收割脫穀作業之低速行進狀態。 此外，於前述靜油壓式無段變速裝置控制器％之輸出 側連接使變U斜板15之傾斜角度之閥％切換作動之電 磁線圈93。另外，連結於前述引擎控制器57之感測器等機 器係圖式省略。 曰由以上之回路構成，以電位計13A檢出設於操縱部 之側部之變速# 13之前後操作角度，透過主控制器⑴ 靜油壓式無段變速裝置控制$ 56往電磁線圈93為輸出 12 201117709 此往電磁線圈93之輸出使閥94切換，複動汽紅％之作動 使录斜f 15之角度無段變更，從油壓栗U往油壓馬達16 之送油里增加’此油壓馬達16之輸出轉速增速。此外 達側之變速係基於副變速„ 17B之操作，藉由從主控制 盗55往電磁線圈96之輸出切換閥97,以藉由油壓缸”之 作動將馬達斜板17之傾斜角度切換為低速行進側與高速行 進側之兩位置進行。如上述，將行進用靜㈣式無段變速 裂置12之油壓馬達16兩階段變速可發揮副變速機能，省 略任務箱18内之機械式副變速機構。 如此，前述最高車速設定刻度盤51係在將行進用靜油 壓式無段變速裝置12之油壓馬達16之馬達斜板17之傾斜 角度切換為低速行進側之狀態下，無段變更設定變速桿Η 操作至最高速位置時之油壓泵14之果斜板15之最大傾斜 角度。 即，如於圖7顯示之圖所示，在取變速桿13之前進側 之操作位置為縱軸，取車速為橫軸，描繪顯示變速桿13之 前進側之操作位置與車速之比例關係之比例線時，藉由最 高車速設定刻度盤51之旋轉操作，在斜率相異之高速側之 比例線E與低速側之比例線F之間無段變更比例線之斜 率。具體地係於主控制器55預先設定有電位計13A之檢出 值與斜板角度感測器i 5S之檢出值之關係以使變速桿n之 單位操作量之泵斜板15之傾斜角度之變化量隨最高車速設 定刻度盤5 1之旋轉操作而變更。 藉此’例如，於比例線E將變速桿1 3操作至最高速位 13 201117709 置時之車速V1比於比例線F將變速桿13操作至最高速位 置時之車速V2高。 通常，在移動狀態係將油壓馬達16之馬達斜板17之 傾斜角度切換至高速行進側，於轉換為收割作業時，將此 馬達斜板17之傾斜角度切換至低速行進側。如上述為進 行收割作業而將馬達斜17之傾斜角度切換至低速行進 側，可將車速之變速範圍限制於適於以最高車速設定刻度 盤定之農地條件或作物條件之範圍，可提高收割作業 中之聯合收穫機之操作性及收割作業之效率。 此外，使以此最高車速設定刻度盤51進行之最高車速 之設定變更（調節）僅在油壓馬達1 主Ϊ堤1 ()之馬達斜板丨7之傾斜角 度被切換至低速行進側之狀態下為有效。此外，使為在以 最商車速設定刻度盤51設定最高車速後馬達斜板17之傾 斜角度從低速行進侧被切換至高速行進側m前次之 =亡速設定刻度盤51進行之最高車速之設定為無效， 解除最南車速之限制之構成。 即’以低速行進之收割作紫 作業、。束時，為農地間移動而 將靜油壓式無段變速裝w 社” Μ置12之油壓馬達16之斜板即馬達 斜板1 7之傾斜角度切換 制而π a ± 网速仃進側’解除最高車速之限 制而可尚速行進，故可省 声I y 名略以手動解除以最高車速設定刻 度盤51進行之最高車速 ^ , 。又疋之操作，可更提高重複高速 之晨地間移動與低速之 收割作業之效率。 °乍業之聯合收穫機之操作性及 如此，使為收割搬送用 用靜/由壓式無段變速裝置2 i同步 14 201117709 於車速變速作動之構成。 即，收割搬送用靜油壓式無段變速裝置21係對應於檢 出變速桿13之操作位置之電位計13A之檢出結果或車速感 測器58之檢出結果變速控制。 例如圖8所示，設定收割驅動速度以相對於行進速度 特疋之比率增速之標準作業線A、收割驅動速度以比此標準 作業線A陡斜率增速之倒伏作業線B。d係顯示將馬達斜 板”之傾斜角度切換至低速行進側之狀態下之最高速度， C係顯示將馬達斜板17之傾斜角度切換至高速行進側之狀 態下之最高速度。 如此’以來自引擎22之一定驅動旋轉驅動脫縠裝置2 與進給鏈U)而使脫榖作業安定，並使以收割搬送用靜油壓 式無&變速裝置21驅動之收割|置與輔助鍵u之驅動速 度同步於行進速度’使從收«置4往進給鍵1〇之榖桿之 轉交為圓滑且確實。 …此外，右在使行進用靜油壓式無段變速裝置12停止之 狀1、下.¾動收割搬送用靜油壓式無段變速裝置2 1，收割裝 ^ 4與進給鏈10在行進停止㈣下驅動。藉此，可往輔助 效率提:進°鏈1〇供給手收割縠桿’可使收割脫榖作業之 感測踩下操作停車煞車踏板後，對應於以停車煞j 段變：裝=出之踩下角度從主控制器55透過靜油壓心 圏93之L m往電磁線圈93為輸出，此往電磁务 之輸出使闕94切換，複動汽…作動使果斜板丨 15 201117709 之傾斜角度往低速側變更’從油壓聚14往油壓馬達16之 送油量減少’此油壓馬達16之輸出轉速減速。藉此，車速 對應於停車煞車踏板之踩下角度減速，到達停車狀態。停 車煞車踏板與停車料n 71B之間係透職械式之連繁機 構連接， 且設定有時序以使在停車煞車踏板之踩下途中上 述之油壓馬達16之輸出旋轉停止，其後停車煞車器7[b成 為完全作動狀態。藉此’於踩下停車煞車踏板而以停車時， 可使衝擊緩和而圓滑停車。 【圖式簡單說明】 圖1為聯合收穫機之側面圖。 圖2為聯合收穫機之傳動機構之說明圖。 圖3為任務箱内之傳動機構之說明圖。 圖4為行進用靜油壓式無段變速裝置及收割搬送用靜 /由壓式無段變速裝置之油壓回路。 圖5為方塊回路圖。 圖6為顯示最高車速設定刻度盤之配置之說明圖。 圖7為顯示車速與變速桿操作位置之關係之圖。 圖8為顯示車速與收割驅動速度之關係之圖。 【主要元件符號說明】 2 脫穀裝置 3 行進裝置 4 收割裝置 16 201117709 5 穀粒槽 6 操縱部 12 行進用靜油壓式無段變速裝置 13 變速桿 14 油壓泵 15 泵斜板 16 油壓馬達 17 馬達斜板 51 最高車速設定刻度盤 17It is difficult to operate in the vertical direction. Setting the maximum speed cannot be reversed. If it is based on the harvesting operation 4 201117709 It is suitable for high-speed travel on the road. It takes time to move between farms and the work efficiency is reduced. In order to solve the above problems, the present invention adopts the following technical means. That is, the invention described in claim 1 is a combine harvester in which a husking device (2) is arranged side by side on the upper side j of the traveling device (3) driven by the traveling static hydraulic stepless speed change device (12). The granule groove (5) is provided with a manipulation portion (6) on the front side of the granule groove, and a harvesting device (4) is disposed on the front side of the manipulation portion (6) and the husking device (2), and is provided to change the foregoing The swash plate of the hydraulic pump (10) for traveling the static oil type stepless speed change device (12) is the shift angle rocker (13) of the slanting angle of the spring swash plate (15), characterized in that the static oil pressure for the traveling is made The inclined angle of the hydraulic swash plate (10) of the hydraulic motor (16) of the stepless speed change device (12) can be switched between the low speed traveling side and the high speed running side, and is disposed on the motor swash plate (17) In the state where the tilt angle is switched to the low speed traveling side, the setting is set to the maximum vehicle speed setting dial (51) at which the shifting rocker (13) is operated at the highest speed position. The invention described in claim 2 is the combination harvester of the present invention, wherein the setting of the maximum vehicle speed by the maximum vehicle speed setting dial (51) is set only at the inclination angle of the motor swash plate (丨7). It is effective to switch to the low-speed traveling side. When the tilt angle of the motor swash plate 7) is switched from the low-speed traveling side to the high-speed traveling side after the maximum vehicle speed is set by the maximum vehicle speed setting dial (51), the highest is achieved. The setting of the maximum speed for the speed setting dial (5 1) is invalid. According to the invention of claim 1, the 201117709709 of the traveling static-pressure type stepless speed change device (12) is operated by the operation of the maximum vehicle speed setting dial (51): the swash plate which is the pressure motor (16) When the tilt angle of the swash plate (17) is switched to the low speed Ding side, the setting of the shift lever (1) is the highest speed at the highest speed, so the speed range of the vehicle speed can be limited to the farmland. The range of conditions or crop conditions can improve the operability of the combine harvester during harvesting operations and the efficiency of harvesting operations. According to the invention described in the second aspect of the invention, in addition to the effect of the invention described in the above-mentioned claim, the hydraulic motor of the hydrostatic type non-k idle device (12) is moved between the agricultural land (丨6) When the slanting plate of the motor swash plate (17) is switched to the high-speed traveling side, the setting of the maximum vehicle speed during the above-mentioned harvesting operation is invalid, so that the operation of manually setting the maximum vehicle speed can be omitted. The operability of the combine harvester and the efficiency of the harvesting operation can be further improved by repeating the high-speed inter-farm movement and the low-speed harvesting operation. [Embodiment] An embodiment of the present invention will be described based on the drawings. Figure 1 shows the body configuration of the combine harvester. The combine harvester is provided with a traveling device 3 having a crawler belt 3A on the lower side of the body frame 1, and a threshing device 2 is mounted on the left side of the upper portion of the body frame 1, and a discharge screw 7 is mounted on the right side of the threshing device 2 The sump 5 is provided with a manipulating portion 6 on the front side of the grain trough 5, and the harvesting device 4 is disposed on the front side of the manipulating portion 6 and the threshing device 2. The harvesting device 4 is configured to include a grass body 8, a pulling device 8a, a harvesting blade 9, and a conveying device 9A from the front side. On the outer side of the upper portion of the threshing apparatus 2, a feed chain that feeds the grain stem conveyed from the 6 201117709 conveying device 9A on the side of the harvesting 4 to the threshing chamber is provided, and the feed chain 10 is provided on the upper side. The mast of the feed chain 10 (not shown). Further, on the inner side of the start end portion of the feed chain 10, an auxiliary chain 11 for transferring the mast from the conveying device 9A to the feed chain 10 is provided. Figure 2 shows the transmission of the combine harvester. The output shaft 22A of the engine 22 mounted on the lower portion of the operating portion 6 is fixed to the harvesting and unloading output pulley 25B'. The harvesting and releasing output pulley 25b and the intermediate pulley 28 fixed to one end of the intermediate shaft 29 are wound and harvested. The drive belt 44A of the disengagement clutch 44. Further, the intermediate gear 30 fixed to the other end of the intermediate shaft 29 is engaged with the intermediate gear 30a of the intermediate transmission shaft 31 fixed in the gear case 5, so that the bevel gear 32 fixed to the end of the intermediate transmission shaft 3丨Engaged with the bevel gear 32a fixed to the end of the threshing drive shaft 33. Further, the separation pulley 34 and the processing cartridge 35 are rotationally driven by the intermediate pulley 33A fixed to the other end of the disengagement transmission shaft 33 through the belt transmission mechanism 33B. Further, 'the intermediate gear 36A fixed to the other end of the intermediate output shaft 41 and the intermediate gear % fixed to the other end of the intermediate transmission shaft 31 are output pulleys fixed from the other end of the intermediate output shaft 41 "A is driven by the belt drive mechanism 41B to drive the selection portion (four) including the wind drum 42 and the sprocket 43 at the rear portion of the feed chain 10. Further, the sprocket 43 on the side of the manipulation portion 6 of the gear case 50 is attached. The static oil-pressure type stepless speed change device 21 is used to engage the wheel gear 37A of the wheel-in shaft 37 fixed to the static-pressure type stepless speed change device 21 of the harvesting and transporting operation, and the intermediate gear 36A is engaged. The static oil pressure type for harvesting and transporting is not 201117709. The output shaft 38 of the section shifting device 21 is driven by the gear transmission mechanism 38B, 38C connected to the check tank. The harvesting pulley is harvested and the output pulley 45 is harvested. The output shaft 39 and the output of the fixed winding auxiliary chain 1 shaft 40 and the output of the sprocket 4A are ==. The harvesting pulley is fixed to the outer end of the harvesting output pulley Μ and the harvesting device 4 47 A Μ winding drive belt, on the other hand, fixed in front The output pulley 25A of the engine 22 is fixed to the load (4) attached to the traveling task: the destination of the traveling static hydraulic stepless speed change device 12 = the upper wheel 26 is wound around the drive belt 12B. The drive mechanism in the task box 18 is shown in Fig. 3. The output of the hydraulic motor 16 for traveling static oil pressure type U is provided on the upper part of the service box 18, and the output of the input device 65 is input to the shaft. The output gear 66 fixed to the wheel is engaged with the eight-wheel _ fixed to the inter-shaft 66. Further, the teeth fixed to the intermediate shaft 66a are fixed to the left and right sides of the occlusion gear 68 of the gear 66C. The left and right side clutches 69, 69. The movable gear:: / 吏 the aforementioned driven gear 68 is engaged with the side fixed to the transmission shaft 71. The left-passive gear 72' is located at the left and right of the second driven gear 72. Machine ", 7. : Two structures 7〇 are attached to the cylindrical shape of the planetary tooth nursery. The other bearings have effective... The circumferential direction is separated by intervals, 谞, and the two are different from each other, so that the door is sounded, 7 The planetary gears and the planetary gears 76 are engaged with the planetary gears 76, and the small gears of the freewheels 75 of the wheel of the drive shaft 71 are engaged with the planetary gears 76 of the Yin 8 201117709. The large-diameter tooth portion of the planetary gear 74 is engaged with the sun gear 71A fixed to the transmission shaft 71. Further, between the planetary gear 73 and the task box 丨8, a multi-plate type brake 77 for restricting the rotation of the carrier is provided. Further, the large-diameter tooth portion of the output gear 75 is engaged with the large-diameter tooth portion of the intermediate gear 75 5B which is rotatably supported by the intermediate shaft 75, so that the small-diameter tooth portion of the intermediate gear 75B is engaged and fixed. A large diameter gear 75D at one end of the reduction shaft 75c. Further, the small-diameter gear 75E fixed to the other end of the above-described decelerating shaft condition is engaged with the axle gear 76G fixed to the end portion of the axle. The drive sprocket 76H fixed to the other end of the fish shaft 76F is wound around the front portion of the crawler belt 3A and driven. This is a parking brake that restricts the operation of the aforementioned drive shaft 71. With the above configuration, the right side of the clutch is connected to the right side, and after the operation direction lever 6 is tilted, first, the side clutch 69 of the dumping operation side is blocked, and the steering direction lever 6a is tilted. The larger the operating angle is, the lower the rotational speed of the inner axle 76F is, and in the state τ where the planetary carrier 73 is stopped, the outer axle and the inner axle (10) that rotates inside are rotated in the opposite direction to rotate in the same direction. Further, the end portion of the intermediate shaft 66 is placed in the task box, and the intermediate portion of the intermediate shaft 66 is formed as an angular shaft or a rotary operation portion (10). In this way, the output shaft of the hydraulic motor 16 for the traveling static hydraulic type speedless device 12 is connected to the input shaft: groove, and the traveling speed/speed device 12 is mounted. At the time of the task box 丨8, the rotary operation unit 66 can be used to make the phase of the pin groove of the input shaft 65 and the oil for traveling without the partial shifting device η. The phase of the pin groove of the output shaft is easily matched. As a result, the installation work of the traveling static oil and the stepless speed change device 12 can be easily performed. ' Figure 4 shows the row (four) static (four) type stepless speed change device 12 and harvesting The hydraulic circuit of the static oil-independent stepless transmission 21 is transported. The traveling static-pressure type stepless transmission 12 changes the inclination angle of the pump swash plate 15 which is the swash plate of the hydraulic pump 14, and changes the oil from the oil. The pressure pump " the oil supply amount to the oil motor 16, the speed of the output shaft of the hydraulic motor 16 is formed without a step change. In addition, a reset steam red 95' which changes the inclination angle of the pump swash plate 15 is set. Set to this reverberation steam rainbow% supply between the operating oil 94, set no segment adjustment The electromagnetic coil 93 of the valve 94 is opened. Further, the supply pump 85 is provided to be coaxially driven with the input shaft 12 of the hydraulic pump 14, and the discharge oil for the π pump 85 is supplied to the communication hydraulic pump 14 and the oil. The closed circuit 12 is formed between the pressure motor μ. Further, a hydraulic cylinder 19 that switches the slanting plate of the hydraulic motor 16 or the inclination angle of the motor swash plate 17 in two stages is provided, and the hydraulic cylinder is supplied to the hydraulic oil cylinder. The valve 97' is configured to switch the inclination angle of the electric motor by switching the valve 97. The rotation speed of the two shafts of the hydraulic motor can be switched to the low speed traveling side and the high speed traveling side. The closed circuit in the static oil pressure type stepless speed change device 2 is configured such that the hydraulic oil sent from the supply pump 85 for the traveling static hydraulic stepless speed change device Α is supplied in a shunt width of 92 Α. 'Because the static oil pressure type stepless speed change device for traveling and the harvesting and transporting 201117709 supply static oil pressure type 'speed device 21 share the supply pump 85, the disk can be reduced: it is inexpensively provided. In addition, in the aforementioned split flow 92A's oil delivery direction ^ Tour: set according to B 92 In addition, the closed circuit between the hydraulic pump 89 and the hydraulic motor 9〇 through the static oil pressure of the harvesting and transporting device is set to (5) the oil passage on the pressure side and the oil passage on the low pressure side. Short circuit oil circuit, set one-way reading on this oil circuit." Therefore, in the case of hydraulic oil from the oil pressure: the direction is reversed, {the hydraulic oil is sent to the hydraulic motor 90, and the hydraulic motor 9G is reversed. As a result, the harvesting device can be prevented from being driven, and the harvesting device 4 can be prevented from being damaged. Further, since it is not necessary to provide a one-way clutch from the transmission path of the cut-and-transport and the static-pressure type stepless speed change device 2" main harvesting device 4, it is possible to reduce the manufacturing cost and provide it at a low cost. A block circuit diagram is shown in FIG. The interface between the controller 55 and the engine controller 57 and the static oil-type stepless speed change is communicable to form an in-vehicle area network. On the input side of the main controller 55, the potentiometer i3A for detecting the angle provided on the side of the operating portion 6 and the potentiometer 6β for detecting the left and right operating angles of the two-stage lever 6A are detected. The speed of the vehicle is measured by H 58. Will the static oil pressure type of the stepless speed change be used? The motor swash plate 17 of up to 16 is switched to the low-speed traveling side and the high-speed and high-speed port": the sub-transmission switch 17B, the slewing switch 61 that operates when the left and right crawler belts are reversed and rotated back, and the change setting will become the joystick Η Out = the highest speed of the vehicle speed setting dial Η, check two static: pressure type stepless speed change device 12 oil pump slanting plate oblique angle slanting plate angle sensor 15S, check out Operation parking 11 201117709 ..., parking device 7 1B parking brake pedal (not shown) stepping angle parking brake sensor 7 1 S. The most recent vehicle speed setting dial 5 is provided under the panel 5iA disposed in the upper tilting position before the left side of the front portion of the operating portion 6, as shown in Fig. 6. The panel 5 1 A is centrally equipped with an automatic control function. The switch for enabling the lapse of the operation (not shown). Further, on the output side of the main controller 55, the left and right sides of the escaping operation are connected. The side clutch electromagnetic coils 69L, 69R of the device 69, the left and right brake electromagnetic coils 77L, 77R for controlling the proportional pressure reducing valve for the oil supply pressure to the left and right brakes 77, and the valve 97 for switching the tilt angle of the motor swash plate 丨7 The electromagnetic coil 96 is operated only by the shift motor 2 1A of the swash plate angle of the oil for the static oil pressure type stepless speed change device 21 for the transfer. Further, the sub-shift switch 17B may be replaced with a switch for detecting that the harvest clutch or the threshing clutch is connected. Thereby, when the harvesting clutch or the threshing clutch is connected, the inclination angle of the motor swash plate 17 of the hydraulic motor 16 of the traveling static oil type stepless transmission 12 is automatically switched from the high speed traveling side to the low speed traveling side. It becomes a low-speed traveling state suitable for harvesting and threshing operations. Further, an electromagnetic coil 93 for switching the valve % of the inclination angle of the U-slanting plate 15 is switched to the output side of the static hydraulic stepless transmission controller %. Further, a machine such as a sensor connected to the engine controller 57 is omitted.曰 It is composed of the above circuit, and the potentiometer 13A detects the operating angle before and after the shift #13 provided on the side of the operating portion, and controls the $56 to the electromagnetic coil 93 through the main controller (1) hydrostatic stepless transmission. Output 12 201117709 The output of the electromagnetic coil 93 causes the valve 94 to switch, and the action of the double-shifting steam red causes the angle of the recording angle f 15 to be changed without a section, and the oil pressure from the oil pressure pump U to the hydraulic motor 16 is increased. The output speed of the hydraulic motor 16 is increased. Further, the shifting on the side is based on the operation of the sub-shift 17B, and the tilting angle of the motor swash plate 17 is switched by the action of the hydraulic cylinder by switching the valve 97 from the main control thief 55 to the output of the electromagnetic coil 96. The low speed traveling side and the high speed traveling side are performed at two positions. As described above, the two-stage shifting of the hydraulic motor 16 for the stationary (four) type stepless speed change splitting 12 can function as a sub-transmission function, and the mechanical sub-transmission mechanism in the task box 18 can be omitted. In the state in which the tilting angle of the motor swash plate 17 of the hydraulic motor 16 of the traveling static hydraulic stepless transmission 12 is switched to the low speed traveling side, the maximum speed setting dial 51 is set to be changed without a step change. Rod 最大 The maximum tilt angle of the swash plate 15 of the hydraulic pump 14 when operating to the highest speed position. That is, as shown in the diagram shown in FIG. 7, the operation position on the front side before taking the shift lever 13 is the vertical axis, and the vehicle speed is taken as the horizontal axis, and the relationship between the operation position of the forward side of the shift lever 13 and the vehicle speed is plotted. In the case of the proportional line, the slope of the proportional line is not changed between the proportional line E on the high-speed side of the slope and the proportional line F on the low-speed side by the rotation operation of the maximum vehicle speed setting dial 51. Specifically, the main controller 55 presets the relationship between the detected value of the potentiometer 13A and the detected value of the swash plate angle sensor i 5S so that the tilt angle of the pump swash plate 15 of the unit operation amount of the shift lever n is set. The amount of change is changed in accordance with the rotation operation of the maximum vehicle speed setting dial 51. Thus, for example, the vehicle speed V1 when the shift lever 13 is operated to the highest speed position 13 201117709 on the proportional line E is higher than the vehicle speed V2 when the shift lever 13 is operated to the highest speed position. Normally, in the moving state, the inclination angle of the motor swash plate 17 of the hydraulic motor 16 is switched to the high speed traveling side, and when switching to the harvesting operation, the inclination angle of the motor swash plate 17 is switched to the low speed traveling side. As described above, in order to perform the harvesting operation, the tilt angle of the motor ramp 17 is switched to the low speed traveling side, and the shift range of the vehicle speed can be limited to the range of agricultural conditions or crop conditions suitable for setting the maximum speed setting, thereby improving the harvesting operation. The operability of the combine harvester and the efficiency of the harvesting operation. Further, the setting (adjustment) of the maximum vehicle speed by the maximum vehicle speed setting dial 51 is changed only to the state where the inclination angle of the motor swash plate 7 of the main dam 1 of the hydraulic motor 1 is switched to the low-speed traveling side. The next is valid. Further, in order to set the maximum vehicle speed at the most commercial vehicle speed setting dial 51, the inclination angle of the motor swash plate 17 is switched from the low speed traveling side to the high speed traveling side m, and the highest speed of the dead speed setting dial 51 is performed. Set to invalid, the structure of the limit of the southernmost speed is released. That is, the harvest at low speed is used for purple work. When the beam is moved, the static oil pressure type stepless speed change device is moved for the movement between the agricultural land. The tilting angle of the motor swash plate of the hydraulic motor 16 of the set 12 is switched by the inclination angle of the motor slanting plate 17 and the speed is π a ± The side 'releases the limit of the maximum speed and can travel at a speed. Therefore, the sound can be saved by manually canceling the maximum speed of the maximum speed setting dial 51. The operation of the speed can further improve the repetition of the high speed morning. The efficiency of the inter-ground movement and the low-speed harvesting operation. The operability of the combined harvester of the industry and the like, so that the static/pressure-type stepless speed change device for the harvesting and transporting 2 i is synchronized 14 201117709 In other words, the static oil hydraulic type stepless speed change device 21 for harvesting and transporting corresponds to the detection result of the potentiometer 13A that detects the operation position of the shift lever 13 or the detection result shift control of the vehicle speed sensor 58. For example, FIG. As shown, the standard operating line A for which the harvesting drive speed is increased at a rate relative to the traveling speed characteristic, and the harvesting drive speed are increased by a steeper slope than the standard line A. The d-line shows that the motor is tilted. Slab Switch-over to the highest speed side of the low-speed traveling, C-based displays the inclination angle of the motor swash plate 17 is switched to the high speed traveling at the maximum speed side of the state. In this way, the untwisting operation is stabilized by the rotation of the untwisting device 2 and the feed chain U from a certain drive of the engine 22, and the harvesting operation is performed by the static oil-pressure type without the shifting device 21 The drive speed of the auxiliary key u is synchronized with the travel speed 'to make the transfer from the take-up button 4 to the feed button 1 圆 smooth and sure. In addition, the right side is used to stop the traveling static hydraulic stepless speed change device 12, and the lower 3⁄4 moving harvesting static oil pressure type stepless speed change device 2 1, the harvesting device 4 and the feed chain 10 are The travel stops (four) and drives down. In this way, the auxiliary efficiency can be raised: the feed chain 1 〇 supply hand harvesting mast can make the sense of the harvesting dislocation operation step on the parking brake pedal, corresponding to the parking 煞j segment: loading = out The stepping angle is output from the main controller 55 through the L m of the static oil pressure core 93 to the electromagnetic coil 93, and the output of the electromagnetic current causes the 阙94 to switch, and the double-acting steam...actuates the slanting plate 丨15 201117709 The angle is changed to the low speed side, 'the oil supply amount from the hydraulic pressure 14 to the hydraulic motor 16 is decreased'. The output speed of the hydraulic motor 16 is decelerated. Thereby, the vehicle speed is decelerated corresponding to the depression angle of the parking brake pedal, and reaches the parking state. The parking brake pedal and the parking material n 71B are connected by a mechanical mechanism, and a timing is set so that the output of the hydraulic motor 16 described above is stopped during the depression of the parking brake pedal, and then the parking brake is stopped. The 7[b becomes fully active. By this, when the parking brake pedal is depressed and the vehicle is parked, the impact can be relaxed and the vehicle can be smoothly stopped. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side view of a combine harvester. Figure 2 is an explanatory view of the transmission mechanism of the combine harvester. Figure 3 is an explanatory view of the transmission mechanism in the task box. Fig. 4 is a hydraulic circuit of a traveling static-pressure type stepless transmission and a static/pressure-type stepless transmission. Figure 5 is a block circuit diagram. Fig. 6 is an explanatory view showing the configuration of the maximum vehicle speed setting dial. Fig. 7 is a view showing the relationship between the vehicle speed and the operating position of the shift lever. Fig. 8 is a graph showing the relationship between the vehicle speed and the harvesting drive speed. [Description of main component symbols] 2 Threshing device 3 Traveling device 4 Harvesting device 16 201117709 5 Grain trough 6 Manipulating part 12 Static oil-pressure type stepless speed change device 13 Shift lever 14 Hydraulic pump 15 Pump swash plate 16 Oil pressure Motor 17 motor swash plate 51 maximum speed setting dial 17