JP5854101B2

JP5854101B2 - Combine

Info

Publication number: JP5854101B2
Application number: JP2014190283A
Authority: JP
Inventors: 藤田　靖; 靖藤田; 上路　嘉隆; 嘉隆上路; 上村　孝彦; 孝彦上村
Original assignee: Iseki and Co Ltd
Current assignee: Iseki and Co Ltd
Priority date: 2014-09-18
Filing date: 2014-09-18
Publication date: 2016-02-09
Anticipated expiration: 2029-03-17
Also published as: JP2015002747A

Description

本発明は、コンバインに係るものである。 The present invention relates to a combine.

従来、走行用静油圧式無段変速装置により走行速度を無段階に変速可能な走行装置の前方に刈取部を設け、走行装置の上方には脱穀装置を設け、前記刈取部は走行装置の走行速度に同調して刈取搬送用静油圧式無段変速装置により変速駆動する構成は、公知である（特許文献１参照）。 Conventionally, a cutting unit is provided in front of a traveling device capable of continuously changing the traveling speed by a hydrostatic continuously variable transmission for traveling, and a threshing device is provided above the traveling device. A configuration in which gear shifting driving is performed by a hydrostatic continuously variable transmission for cutting and conveying in synchronization with the speed is known (see Patent Document 1).

特開平０６−１７９２８号公報Japanese Patent Laid-Open No. 06-17928

前記公知例は、単に、刈取搬送用静油圧式無段変速装置の刈取ＨＳＴ出力軸からの変速回転を刈取部に出力するため、刈取搬送用静油圧式無段変速装置の刈取ＨＳＴ出力軸から出力される回転数が低いときには、油圧ポンプから油圧モータへの送油量が少ないため、刈取ＨＳＴ出力軸の回転数は一定せずに不安定となり、また、刈取ＨＳＴ出力軸の伝達する回転トルクも低くいことがあり、刈取部の負荷が大きいと、穀稈を噛み込んだり、最悪のときには刈取部が停止することがあるという課題がある。 The known example simply outputs the variable speed rotation from the harvesting HST output shaft of the hydrostatic continuously variable transmission for harvesting conveyance to the harvesting part, and therefore from the harvesting HST output shaft of the hydrostatic continuously variable transmission for harvesting conveyance. When the output rotational speed is low, the amount of oil supplied from the hydraulic pump to the hydraulic motor is small, so the rotational speed of the cutting HST output shaft is not constant and unstable, and the rotational torque transmitted by the cutting HST output shaft However, when the load on the cutting part is large, there is a problem that the cereal can be bitten or the cutting part may stop in the worst case.

本発明は、次の技術的手段を講じる。
即ち、請求項１記載の発明は、走行装置（３）を備えた機体フレーム（１）の上方位置に、脱穀穀稈供給用の供給搬送装置（１０）を備えた脱穀装置（２）を設け、前記機体フレーム（１）の前方に刈取部（４）を設け、前記脱穀装置（２）の横側にグレンタンク（５）を設け、該グレンタンク（５）の前側に操縦部（６）を設けたコンバインにおいて、前記操縦部（６）に備えた運転座席（８６）の下方にエンジンルーム（８７）を設け、該エンジンルーム（８７）内に備えたエンジン（２２）の外側にエンジン冷却用ファン（８８）を設け、該エンジン冷却用ファン（８８）の外側に設けたラジエーター（８９）の外側には防塵ネット（９２）を有するラジエーターカバー（９０）を設け、前記防塵ネット（９２）の内側には所定の幅を有した縦長の遮風プレート（９３）を、前記ラジエーターカバー（９０）の幅方向に往復移動自在に設け、前記エンジン（２２）によって駆動される静油圧式無段変速装置（２１）の出力軸（３８）と、刈取部（４）へ駆動力を出力する刈取出力軸（４５Ａ）の間に遊星歯車機構（７０）を設け、前記静油圧式無段変速装置（２１）の出力軸（３８）の回転と、該静油圧式無段変速装置（２１）の入力軸（３７）の回転を前記遊星歯車機構（７０）で合成して、前記刈取出力軸（４５Ａ）から刈取部（４）へ出力する構成とし、前記遊星歯車機構（７０）における円筒形状のキャリア（７２）に遊星歯車を回転自在に設け、該遊星歯車には前記出力軸（３８）からの回転を伝達するサンギヤ（７４）を噛み合わせ、前記遊星歯車には前記刈取出力軸（４５Ａ）と一体回転する入力歯車（７６）を噛み合わせ、前記キャリア（７２）に設けた環状歯車（７７）には静油圧式無段変速装置（２１）の入力軸（３７）に設けたギヤ（７８）を噛み合わせ、前記遊星歯車機構（７０）は、前記出力軸（３８）の回転を、逆回転から零回転を経て正回転させて前記刈取出力軸（４５Ａ）へ伝達する構成とし、該刈取出力軸（４５Ａ）と刈取出力軸（４５Ａ）に備えた刈取出力プーリー（４５）との間には、刈取部（４）への逆回転の伝達を防止するワンウェイクラッチ（８０）を備え、前記エンジン（２２）からの動力を前記脱穀装置（２）の扱胴（３４）と前記供給搬送装置（１０）とへ分岐伝動するギヤケース（５０）を設け、前記静油圧式無段変速装置（２１）を前記ギヤケース（５０）における操縦部（６）側の部位に設けたことを特徴とするコンバインとする。 The present invention takes the following technical means.
That is, the invention according to claim 1 is provided with a threshing device (2) provided with a supply and transport device (10) for supplying threshing culm at an upper position of the machine body frame (1) provided with the traveling device (3). A cutting part (4) is provided in front of the body frame (1), a grain tank (5) is provided on the lateral side of the threshing device (2), and a control part (6) is provided on the front side of the grain tank (5). The engine room (87) is provided below the driver seat (86) provided in the control section (6), and the engine is cooled outside the engine (22) provided in the engine room (87). And a radiator cover (90) having a dustproof net (92) outside the radiator (89) provided outside the engine cooling fan (88), and the dustproof net (92) A predetermined width inside The elongated air shielding plates (93), wherein provided reciprocally movable in the width direction of the radiator cover (90), the output shaft of the engine (22) hydrostatic continuously variable transmission driven by (21) ( 38) and a cutting output shaft (45A) that outputs a driving force to the cutting unit (4), a planetary gear mechanism (70) is provided, and the output shaft (38) of the hydrostatic continuously variable transmission (21). And the rotation of the input shaft (37) of the hydrostatic continuously variable transmission (21) by the planetary gear mechanism (70), from the cutting output shaft (45A) to the cutting unit (4). A planetary gear is rotatably provided on a cylindrical carrier (72) in the planetary gear mechanism (70), and a sun gear (74) for transmitting rotation from the output shaft (38) to the planetary gear. And the planetary gear has the cutting The input gear (76) rotating integrally with the force shaft (45A) is meshed, and the annular gear (77) provided on the carrier (72) is connected to the input shaft (37) of the hydrostatic continuously variable transmission (21). The planetary gear mechanism (70) meshes with the provided gear (78), and transmits the rotation of the output shaft (38) to the cutting output shaft (45A) by rotating from the reverse rotation to the positive rotation through zero rotation. A one-way clutch (80) that prevents transmission of reverse rotation to the cutting part (4) between the cutting output shaft (45A) and the cutting output pulley (45) provided on the cutting output shaft (45A). ), A gear case (50) for branching and transmitting the power from the engine (22) to the handling cylinder (34) of the threshing device (2) and the supply / conveyance device (10) is provided. The step transmission (21) is connected to the gear case (50). The combine is characterized in that it is provided at a site on the control unit (6) side .

請求項２記載の発明は、前記供給搬送装置（１０）の搬送始端部に前側供給搬送装置（１１）を設け、該前側供給搬送装置（１１）を、前記刈取出力軸（４５Ａ）から連動される搬送シンクロ用出力軸（４０）で駆動する構成とした請求項１に記載のコンバインとする。 According to a second aspect of the present invention , a front supply / conveyance device (11) is provided at a conveyance start end of the supply / conveyance device (10), and the front supply / conveyance device (11) is interlocked with the cutting output shaft (45A). The combine according to claim 1, wherein the combiner is driven by an output shaft (40) for conveying synchronization .

請求項３記載の発明は、前記遮風プレート（９３）を上側プレート（９９Ａ）と下側プレート（９９Ｂ）に分割し、前記上側プレート（９９Ａ）の下部に長孔（１００）を形成し、前記下側プレート（９９Ｂ）の上部には前記長孔（１００）内を移動する案内体（１０１）を設け、該上側プレート（９９Ａ）の下部と下側プレート（９９Ｂ）の上部を前記長孔（１００）と案内体（１０１）で伸縮自在且つ屈曲自在に連結した請求項２に記載のコンバインとする。 The invention of claim 3 divides the wind shield plate (93) into an upper plate (99A) and a lower plate (99B), and forms a long hole (100) in the lower part of the upper plate (99A), A guide body (101) that moves in the elongated hole (100) is provided at the upper part of the lower plate (99B), and the lower part of the upper plate (99A) and the upper part of the lower plate (99B) are disposed at the elongated hole. The combine according to claim 2, wherein the combine is connected to be freely extendable and bendable by (100) and the guide body (101) .

静油圧式無段変速装置（２１）の出力軸（３８）から出力される回転数が低いと、この静油圧式無段変速装置（２１）の油圧ポンプから油圧モータへの送油量が少なく、出力軸（３８）の回転数が不安定となり、また、出力軸（３８）から伝達される回転トルクが低く、刈取部（４）の負荷が大きい場合、刈取部（４）が停止することがあるが、請求項１に記載の発明によれば、遊星歯車機構（７０）によって、出力軸（３８）を所定回転数で回転させていても、刈取出力軸（４５Ａ）の回転を停止させておくことができるので、刈取部（４）の回転数が低い状態でも、静油圧式無段変速装置（２１）は安定したトルクを出力し、刈取部（４）による刈取作業を安定させることができる。 When the rotational speed output from the output shaft (38) of the hydrostatic continuously variable transmission (21) is low, the amount of oil fed from the hydraulic pump of the hydrostatic continuously variable transmission (21) to the hydraulic motor is small. When the rotational speed of the output shaft (38) becomes unstable, the rotational torque transmitted from the output shaft (38) is low, and the load on the cutting part (4) is large, the cutting part (4) stops. However, according to the first aspect of the present invention, even if the output shaft (38) is rotated at a predetermined rotational speed by the planetary gear mechanism (70), the cutting output shaft (45A) stops rotating. Since the hydrostatic continuously variable transmission (21) outputs a stable torque even when the rotational speed of the cutting part (4) is low, the cutting work by the cutting part (4) can be stabilized. Can do.

即ち、静油圧式無段変速装置（２１）の出力軸（３８）から出力される回転数を所定回転数以上に保持させて、静油圧式無段変速装置（２１）の油圧ポンプから油圧モータへの送油量を確保して、出力軸（３８）の回転数を安定させ、この出力軸（３８）の回転トルクを確保して刈取部（４）の負荷に対応させ、刈取部（４）の停止を防止することができる。 That is, the rotational speed output from the output shaft (38) of the hydrostatic continuously variable transmission (21) is maintained at a predetermined rotational speed or more, and the hydraulic motor from the hydraulic pump of the hydrostatic continuously variable transmission (21) is maintained. The amount of oil to be fed is secured, the rotation speed of the output shaft (38) is stabilized, the rotational torque of the output shaft (38) is secured to correspond to the load of the cutting portion (4), and the cutting portion (4 ) Can be prevented.

また、機体停止状態から所定の走行速度の間でも、静油圧式無段変速装置（２１）および遊星歯車機構（７０）によって刈取部（４）を十分な回転数で駆動することができ、機体走行開始直後から刈取部（４）を安定して駆動することができ、刈取作業を安定して行なえる。 Further , even during the predetermined travel speed from the state where the airframe is stopped, the cutting unit (4) can be driven at a sufficient rotational speed by the hydrostatic continuously variable transmission (21) and the planetary gear mechanism (70). The cutting unit (4) can be driven stably immediately after the start of traveling, and the cutting operation can be performed stably.

また、出力軸（３８）の回転が停止しているときには、遊星歯車機構（７０）は刈取出力プーリー（４５）側へ零回転に至る前の逆回転を出力することになるが、この刈取出力プーリー（４５）に設けたワンウェイクラッチ（８０）により刈取部（４）への逆回転の伝達を防止して、出力軸（３８）の回転数および回転トルクを安定させることができる。また、刈取出力プーリー（４５）の回転数を零回転とするニュートラル位置の設定が容易になる。
そして、刈取部（４）を駆動する静油圧式無段変速装置（２１）を、エンジン（２２）からの動力を脱穀装置（２）の扱胴（３４）と供給搬送装置（１０）とへ分岐伝動するギヤケース（５０）における操縦部（６）側の部位に設けることで、機体の重量バランスやギヤケース（５０）の取付バランスを良好なものとすることができる。
また、このような刈取作業において、遮風プレート（９３）の端縁付近に、防塵ネット（９２）における他の部位を通過する外気よりも吸引力の強い吸引風を積極的に通して、遮風プレート（９３）の端縁と一緒に防塵ネット（９２）の付着物を移動させて防塵ネット（９２）の目詰まりを除去することができる。 When the rotation of the output shaft (38) is stopped, the planetary gear mechanism (70) outputs the reverse rotation before reaching the zero rotation to the cutting output pulley (45) side. The one-way clutch (80) provided on the pulley (45) prevents the reverse rotation from being transmitted to the cutting part (4), and the rotational speed and rotational torque of the output shaft (38) can be stabilized. In addition, it is easy to set the neutral position where the rotational speed of the cutting output pulley (45) is zero.
Then, the hydrostatic continuously variable transmission (21) that drives the mowing unit (4) is driven by the power from the engine (22) to the handling barrel (34) of the threshing device (2) and the supply transfer device (10). By providing it in the part on the side of the control section (6) in the branching gear case (50), the weight balance of the fuselage and the mounting balance of the gear case (50) can be improved.
In such a cutting operation, a suction wind having a suction force stronger than the outside air passing through other parts of the dust-proof net (92) is actively passed near the edge of the wind-shielding plate (93). The clogging of the dust-proof net (92) can be removed by moving the deposits on the dust-proof net (92) together with the edge of the wind plate (93).

請求項２に記載の発明によれば、上記請求項１に記載の発明の効果に加えて、供給搬送装置（１０）の搬送始端側に設けた前側供給搬送装置（１１）を、刈取出力軸（４５Ａ）から連動される搬送シンクロ用出力軸（４０）で駆動することによって、刈取穀稈の搬送性能が向上する。 According to the invention described in claim 2, in addition to the effect of the invention described in claim 1, the front supply / conveyance device (11) provided on the conveyance start end side of the supply / conveyance device (10) is provided with a cutting output shaft. By driving with the output shaft (40) for conveyance synchronization linked from (45A), the conveyance performance of the harvested cereal meal is improved.

請求項３に記載の発明によれば、上記請求項２に記載の発明の効果に加えて、防塵ネット（９２）の端部の斜めの部分でも、上側プレート（９９Ａ）がこの斜めの部分に沿うように傾斜移動し、外気の吸引を遮断することができる。According to the invention described in claim 3, in addition to the effect of the invention described in claim 2, the upper plate (99A) is also attached to the oblique part at the oblique part of the end of the dustproof net (92). It can be tilted to follow along, and the suction of outside air can be blocked.

コンバインの側面図。The side view of a combine. 刈取部の回転数と車速との関係図。The relationship figure of the rotation speed of a cutting part and a vehicle speed. 伝動機構の概略図。Schematic of a transmission mechanism. 無段変速装置の油圧回路図。The hydraulic circuit diagram of a continuously variable transmission. ミッション機構の概略図。Schematic diagram of the mission mechanism. ミッションケースの断面図。Sectional drawing of a mission case. ミッションケースの断面図。Sectional drawing of a mission case. 刈取用静油圧式無段変速装置部分の展開状態の断面図。Sectional drawing of the unfolding state of the hydrostatic continuously variable transmission part for mowing. 同一部拡大図。The same part enlarged view. 刈取用静油圧式無段変速装置部分の他の実施例の展開状態の断面図。Sectional drawing of the expansion | deployment state of the other Example of the hydrostatic continuously variable transmission part for a mowing. コンバインの右側面図。The right view of a combine. エンジン付近の概略平面図。The schematic plan view of the engine vicinity. ラジエーターカバーの縦断面図。The longitudinal cross-sectional view of a radiator cover. ラジエーターカバーの左側面図。The left view of a radiator cover. 同背面図。The rear view. ラジエーターカバーの移動機構および駆動機構を表示した背面図。The rear view which displayed the movement mechanism and drive mechanism of a radiator cover. 遮風プレートのガイド機構の側面図。The side view of the guide mechanism of a windshield plate. 同一部拡大図。The same part enlarged view. 同一部背面図。The same part rear view. 遮風プレートの上側プレートと下側プレートとの接続部分の側面図。The side view of the connection part of the upper side plate and lower side plate of a windshield plate. 同一部背面図。The same part rear view. 操作パネルの平面図。The top view of an operation panel. 同断面図。FIG. 閉塞部材の斜視図。The perspective view of a closure member.

本発明の実施例を図面により説明すると、１は機体フレ−ム、２は機体フレ−ム１の上方位置に設けた脱穀装置、３は機体フレ−ム１の下方位置に設けた走行装置、４は機体フレ−ム１の前方に設けた刈取部、５は前記脱穀装置２の側部に設けた該脱穀装置２より取出された穀物を一時貯留するグレンタンク、６は操縦部、７はグレンタンク５内の穀物を揚穀する揚穀排出装置である。 An embodiment of the present invention will be described with reference to the drawings. Reference numeral 1 denotes an airframe frame, 2 denotes a threshing device provided at an upper position of the airframe frame 1, 3 denotes a traveling device provided at a lower position of the airframe frame 1, 4 is a cutting part provided in front of the fuselage frame 1, 5 is a glen tank for temporarily storing grains taken out from the threshing device 2 provided on the side of the threshing device 2, 6 is a control unit, and 7 is A cereal discharger for cerealing grains in the Glen tank 5.

前記刈取部４の一例を示すと、分草体８、引起装置（図示省略）、刈刃９および搬送装置を有して構成する。
１０は搬送装置により搬送され穀稈を脱穀装置２の脱穀室（図示省略）に穀稈を供給する穀稈供給搬送装置、１１は穀稈供給搬送装置１０の始端側に設けたシンクロ用前側供給搬送装置（前側供給搬送装置）である。 An example of the cutting unit 4 includes a weeding body 8, a pulling device (not shown), a cutting blade 9, and a conveying device.
Reference numeral 10 denotes a cereal supply / conveyance device that supplies the cereal to the threshing chamber (not shown) of the threshing device 2, and 11 is a front supply for synchro provided on the starting end side of the cereal supply / conveyance device 10. It is a conveying apparatus (front supply conveying apparatus).

前記穀稈供給搬送装置１０は、前記刈取部４で刈り取られた穀稈を脱穀装置２の脱穀室（図示省略）の穀稈供給口（図示省略）から供給し、脱穀されて脱穀室の穀稈排出口（図示省略）より排出するまで搬送するものであるが、刈取部４で刈り取った穀稈を穀稈供給搬送装置１０まで搬送する構成は任意である。 The cereal supply / conveyance device 10 supplies the cereals harvested by the reaping unit 4 from the threshing supply port (not shown) of the threshing chamber (not shown) of the threshing device 2, and is threshed and cerealed in the threshing room. Although it conveys until it discharges | emits from a straw discharge port (illustration omitted), the structure which conveys the grain straw harvested by the cutting part 4 to the grain straw supply conveyance apparatus 10 is arbitrary.

前記穀稈供給搬送装置１０は、挾扼杆（図示省略）と搬送供給チエン（フィードチェン、図示省略）により構成する。挾扼杆は脱穀装置２の上部カバーに上下自在に取付けられ、搬送供給チエンに弾着して穀稈を挟持搬送する。搬送供給チエンは無端チエンにより構成し、任意構成の案内レール（図示省略）により案内されて移動するように構成する。 The grain candy supply / conveyance device 10 is constituted by a cocoon (not shown) and a conveyance / supply chain (feed chain, not shown). The pestle is attached to the upper cover of the threshing device 2 so as to be freely movable up and down, and is attached to the transport and supply chain to sandwich and convey the cereal. The conveyance supply chain is constituted by an endless chain, and is configured to move while being guided by an optional guide rail (not shown).

しかして、走行装置３は走行用静油圧式無段変速装置１２により走行速度変更可能に構成し、刈取部４へ伝達する回転も走行装置３の走行速度に同調して変速するようにする。
即ち、走行用静油圧式無段変速装置１２は、主変速レバー１３の傾倒操作量に応じて増減速し、例えば、図２のように、走行速度に対して所定割合で伝動回転を増速する標準作業ラインＡと、該標準作業ラインＡよりも短時間で増速するようにした倒伏作業ラインＢにより変速するように構成する。 Thus, the traveling device 3 is configured such that the traveling speed can be changed by the traveling hydrostatic continuously variable transmission 12, and the rotation transmitted to the cutting unit 4 is also shifted in synchronization with the traveling speed of the traveling device 3.
That is, the traveling hydrostatic continuously variable transmission 12 increases / decreases in accordance with the amount of tilting operation of the main shift lever 13, and for example, as shown in FIG. The standard work line A and the overturn work line B that is accelerated in a shorter time than the standard work line A are configured to shift.

刈取搬送専用の刈取搬送用静油圧式無段変速装置（静油圧式無段変速装置）２１による走行速度への同調は、脱穀装置２と穀稈供給搬送装置１０とをエンジン２２からの一定駆動回転で駆動して脱穀作業を安定させつつ、穀稈供給搬送装置１０への引継を円滑・確実にする。 The tuning of the threshing device 2 and the cereal supply / conveyance device 10 from the engine 22 is performed in synchronization with the running speed by the hydrostatic continuously variable transmission (hydrostatic continuously variable transmission) 21 for chopping and conveying. While being driven by rotation to stabilize the threshing operation, the transfer to the cereal supply and transport device 10 is made smooth and reliable.

エンジン２２から走行用静油圧式無段変速装置１２および刈取搬送用静油圧式無段変速装置２１への回転伝達機構の構成は任意であるが、図３により一例を示すと、２５Ａは走行用出力プーリー、２５Ｂは刈取脱穀用出力プーリー，２６は走行用静油圧式無段変速装置１２の入力プーリー、２８は刈取脱穀用出力プーリー２５Ｂの回転が伝達される中間プーリー，２９は中間軸、３０は中間歯車、３１は中間伝動軸、３２は一対の脱穀用傘歯車、３３は脱穀伝動軸、３３Ａは脱穀用中間プーリー、３４は扱胴、３５は処理胴、３６は刈取用中間歯車、３７は刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ入力軸（入力軸）、３８は刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸（出力軸）、３９は刈取用中間出力軸、４０は搬送シンクロ用出力軸、４１は穀稈供給搬送中間出力軸、４１Ａは供給搬送用プーリー、４２は唐箕、４３は穀稈供給搬送装置１０の駆動歯車、４４は刈取脱穀クラッチ、４５は刈取用中間出力軸３９に設けた刈取中間出力プーリー（刈取出力プーリー），４６は刈取中間入力プーリー、４７は刈取出力プーリー４５と刈取中間入力プーリー４６に掛け回したベルト、５０は刈取用中間歯車３６および刈取用中間出力軸３９等を設けたギヤケースであり、ギヤケース５０の操縦部６側に刈取搬送用静油圧式無段変速装置２１を設ける。そのため、機体重量バランスやギヤケース５０の取付バランスを良好にする。 Although the configuration of the rotation transmission mechanism from the engine 22 to the hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for harvesting and conveying is arbitrary, FIG. 3 shows an example of 25A for traveling. An output pulley, 25B is an output pulley for cutting and threshing, 26 is an input pulley of the hydrostatic continuously variable transmission 12 for traveling, 28 is an intermediate pulley to which rotation of the output pulley 25B for cutting and threshing is transmitted, 29 is an intermediate shaft, 30 Is an intermediate gear, 31 is an intermediate transmission shaft, 32 is a pair of threshing bevel gears, 33 is a threshing transmission shaft, 33A is an intermediate pulley for threshing, 34 is a handling cylinder, 35 is a processing cylinder, 36 is an intermediate gear for cutting, 37 Is a cutting HST input shaft (input shaft) of the hydrostatic continuously variable transmission 21 for cutting and conveying, 38 is a cutting HST output shaft (output shaft) of the hydrostatic continuously variable transmission 21 for cutting and conveying, and 39 is an intermediate for cutting Output shaft, 40 is carrying Synchro output shaft, 41 is an intermediate output shaft for grain supply and conveyance, 41A is a pulley for supply and conveyance, 42 is tang, 43 is a drive gear of the grain supply and conveyance device 10, 44 is a harvesting and threshing clutch, 45 is an intermediate output for harvesting Cutting intermediate output pulley (cutting output pulley) provided on the shaft 39, 46 is a cutting intermediate input pulley, 47 is a belt wound around the cutting output pulley 45 and the cutting intermediate input pulley 46, 50 is a cutting intermediate gear 36 and a cutting The gear case is provided with an intermediate output shaft 39 and the like, and the hydrostatic continuously variable transmission 21 for cutting and conveying is provided on the side of the steering unit 6 of the gear case 50. Therefore, the airframe weight balance and the attachment balance of the gear case 50 are improved.

しかして、前記走行用静油圧式無段変速装置１２は、油圧ポンプ１４のポンプ斜板１５の傾斜を変更して油圧モータ１６への送油量を無段階に変更して回転を伝達し（図４）、油圧モータ１６にも傾斜角度を二段階に切替可能なモータ斜板１７を設け、機体の走行速度の上限の高速走行Ｃと通常走行Ｄとに切替可能に構成する（図２）。 Thus, the traveling hydrostatic continuously variable transmission 12 changes the inclination of the pump swash plate 15 of the hydraulic pump 14 to change the oil feed amount to the hydraulic motor 16 steplessly and transmits the rotation ( 4), the hydraulic motor 16 is also provided with a motor swash plate 17 whose inclination angle can be switched in two stages, and can be switched between high-speed traveling C and normal traveling D, which is the upper limit of the traveling speed of the aircraft (FIG. 2). .

したがって、本願の走行用静油圧式無段変速装置１２が油圧モータ１６により二段階に走行速度を切替可能にすることで副変速機能を奏するように構成しているので、ミッションケース１８内の機械的な副変速機構を省略している。 Therefore, the traveling hydrostatic continuously variable transmission 12 of the present application is configured to perform the sub-transmission function by enabling the traveling speed to be switched in two stages by the hydraulic motor 16. A typical auxiliary transmission mechanism is omitted.

１９はモータ斜板１７を切替える切替手段（油圧シリンダ）である（図４）。
圃場の状態等の条件を考慮しつつ主変速レバー１３により走行速度を設定するが、穀稈が密集する等の刈取作業中の作業条件が変化したとき、従来であれば副変速機構により減速操作するが、本願では、走行用静油圧式無段変速装置１２の油圧モータ１６のモータ斜板１７を低速側に切り替えて減速するので、円滑に走行でき、ミッションケース１８内の機械的な副変速機構を省略でき、部品点数削減でき、コストダウンおよび軽量化が図れる。 Reference numeral 19 denotes switching means (hydraulic cylinder) for switching the motor swash plate 17 (FIG. 4).
The traveling speed is set by the main speed change lever 13 in consideration of conditions such as the state of the field, but when the work conditions during the harvesting work such as crowding of cereals change, conventionally, the speed reduction operation is performed by the auxiliary speed change mechanism. However, in the present application, since the motor swash plate 17 of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is switched to the low speed side and decelerated, it can travel smoothly, and the mechanical sub-shift in the transmission case 18 The mechanism can be omitted, the number of parts can be reduced, and the cost and weight can be reduced.

また、機械的な副変速機構では副変速用歯車の噛み合い切替えのときにショックが生じることがあるが、本願では油圧モータ１６のモータ斜板１７の高速・低速の切り替えになって、副変速用歯車の噛み合いの切替ショックが発生せず、ノークラッチ化できて、操作性を向上させられる。 In addition, in the mechanical sub-transmission mechanism, a shock may occur when the meshing of the sub-transmission gear is switched, but in this application, the motor swash plate 17 of the hydraulic motor 16 is switched between high speed and low speed, so The gear meshing switching shock does not occur, the clutch can be made free, and the operability can be improved.

このミッションケース１８内の機械的な副変速機構を省略して走行用静油圧式無段変速装置１２の回転を車軸５１に伝達するミッションＭの構成は任意であるが、図５で一例を示すと、ミッションケース１８の上部に走行用静油圧式無段変速装置１２の油圧モータ１６のモータ出力軸５２を設け、モータ出力軸５２に出力歯車５３を設ける。出力歯車５３には入力軸５４の入力歯車５５を噛み合わせる。入力軸５４には別途回転数を調節するための中間歯車５４Ａを設け、中間歯車５４Ａはサイドクラッチ軸５６に固定の受動歯車５７を常時噛合せる。そのため、入力軸５４および入力歯車５５（中間歯車５４Ａ）とサイドクラッチ軸５６および単一の受動歯車５７との間には、副変速軸および副変速軸の軸方向に摺動して噛み合いを変更する複数の副変速用歯車等により構成する機械的な副変速機構を省略している。 The structure of the transmission M that transmits the rotation of the traveling hydrostatic continuously variable transmission 12 to the axle 51 by omitting the mechanical auxiliary transmission mechanism in the transmission case 18 is arbitrary, but an example is shown in FIG. The motor output shaft 52 of the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is provided on the upper part of the transmission case 18, and the output gear 53 is provided on the motor output shaft 52. The output gear 53 meshes with the input gear 55 of the input shaft 54. The input shaft 54 is provided with an intermediate gear 54 A for adjusting the rotational speed separately, and the intermediate gear 54 A always meshes the fixed passive gear 57 with the side clutch shaft 56. Therefore, between the input shaft 54 and the input gear 55 (intermediate gear 54A), the side clutch shaft 56 and the single passive gear 57, sliding is changed in the axial direction of the auxiliary transmission shaft and the auxiliary transmission shaft to change the meshing. A mechanical sub-transmission mechanism constituted by a plurality of sub-transmission gears is omitted.

サイドクラッチ軸５６の左右側には左右のサイドクラッチ（左右サイドクラッチ）５８を設ける。サイドクラッチ軸５６の受動歯車５７には遊星歯車機構６０の駆動軸６１に固定の駆動歯車６７を噛み合わせる。遊星歯車機構６０は公知の構成でよく、簡単に説明すると、左右一対の浅い円筒形状のキャリア６２に遊星歯車６３を夫々設け、遊星歯車６３には駆動軸６１に固定のサンギヤ６４Ａを噛み合わせる。遊星歯車６３に一体状に設けた遊星歯車６３Ａには中間遊星歯車６５を噛み合わせる。中間遊星歯車６５は、駆動軸６１に遊嵌状態に設けた出力用歯車６４を噛み合わせる。キャリア６２にはキャリア６２の回転に制動を付与する多板式のブレーキ６６を設ける。 Left and right side clutches (left and right side clutches) 58 are provided on the left and right sides of the side clutch shaft 56. A drive gear 67 fixed to a drive shaft 61 of the planetary gear mechanism 60 is engaged with the passive gear 57 of the side clutch shaft 56. The planetary gear mechanism 60 may have a known configuration. Briefly, the planetary gear 63 is provided on a pair of left and right shallow cylindrical carriers 62, and the planetary gear 63 is engaged with a sun gear 64 A fixed to the drive shaft 61. An intermediate planetary gear 65 is meshed with a planetary gear 63A provided integrally with the planetary gear 63. The intermediate planetary gear 65 meshes with an output gear 64 provided in a loosely fitted state on the drive shaft 61. The carrier 62 is provided with a multi-plate brake 66 that applies braking to the rotation of the carrier 62.

６６Ａは駐車ブレーキ、６８はサイドクラッチ５８からの回転を出力するサイドクラッチ歯車、６８Ａはサイドクラッチ歯車６８に噛み合うキャリア６２に設けた歯車である。
左右のサイドクラッチ５８を入りの状態ではサイドクラッチ歯車６８とキャリア６２の歯車６８Ａとの噛み合いで回転が遊星歯車機構６０に伝達されて直進し、パワステを傾倒させると、旋回内側となるサイドクラッチ５８を切りにすると共に、旋回内側となるキャリア６２に駆動軸６１からの回転を伝達しつつこの回転にブレーキ６６により制動を掛けて緩旋回を開始し、更に、ブレーキ６６により旋回内側となるキャリア６２に制動を掛けて旋回内側の車軸５１の回転が零になるとブレーキターンとなり、更に、キャリア６２に制動を掛けると旋回外側と旋回内側の車軸５１の回転が逆転してスピンターンとなる。 66A is a parking brake, 68 is a side clutch gear that outputs rotation from the side clutch 58, and 68A is a gear provided on the carrier 62 that meshes with the side clutch gear 68.
In a state where the left and right side clutches 58 are engaged, rotation is transmitted to the planetary gear mechanism 60 by the meshing of the side clutch gear 68 and the gear 68A of the carrier 62, and when the power steering is tilted, the side clutch 58 is turned inside. In addition, the rotation from the drive shaft 61 is transmitted to the carrier 62 on the inner side of the turning, and the rotation is braked by the brake 66 to start the gentle turning. Further, the carrier 62 on the inner side of the turning is started by the brake 66. When the vehicle is braked and the rotation of the axle 51 on the inside of the turn becomes zero, a brake turn occurs, and when the carrier 62 is braked, the rotation of the axle 51 on the outside and inside of the turn is reversed to form a spin turn.

しかして、前記刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８と、刈取出力プーリー４５との間には刈取用遊星歯車機構（遊星歯車機構）７０を設け、刈取用遊星歯車機構７０は、刈取ＨＳＴ出力軸３８の回転数が所定回転数以上になったとき、刈取出力プーリー４５に回転出力するように構成する。 Therefore, a cutting planetary gear mechanism (planetary gear mechanism) 70 is provided between the cutting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for cutting and conveying and the cutting output pulley 45, and the planetary gear for cutting is provided. The mechanism 70 is configured to rotate and output to the harvesting output pulley 45 when the rotational speed of the harvesting HST output shaft 38 becomes equal to or higher than a predetermined rotational speed.

刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８から出力される回転数が低いと、油圧ポンプ（図示省略）から刈取搬送用静油圧式無段変速装置２１の油圧モータ（図示省略）への送油量が少なく、刈取ＨＳＴ出力軸３８の回転数は不安定となり、また、刈取ＨＳＴ出力軸３８の伝達する回転トルクも低く、刈取部４の負荷が大きいと、刈取部４が停止することがある。 When the rotational speed output from the harvesting HST output shaft 38 of the harvesting and conveying hydrostatic continuously variable transmission 21 is low, a hydraulic motor (not shown) of the harvesting and conveying hydrostatic continuously variable transmission 21 from the hydraulic pump (not shown). When the cutting HST output shaft 38 is unstable, the rotational torque transmitted by the cutting HST output shaft 38 is low, and the load of the cutting unit 4 is large, the cutting unit 4 May stop.

即ち、刈取ＨＳＴ出力軸３８と刈取出力プーリー４５を直接接続すると、刈取ＨＳＴ出力軸３８と刈取出力プーリー４５との回転数は同じになるので、上記不具合が、発生するが、本願は刈取用遊星歯車機構７０により刈取出力プーリー４５の回転が逆転から零回転を経て正回転を伝達するように構成し、例え、刈取出力プーリー４５が零回転のときであっても、刈取用遊星歯車機構７０により刈取ＨＳＴ出力軸３８は所定回転数を確保するようにしている。 That is, when the cutting HST output shaft 38 and the cutting output pulley 45 are directly connected, the rotational speeds of the cutting HST output shaft 38 and the cutting output pulley 45 are the same, and thus the above-mentioned problem occurs. The gear mechanism 70 is configured so that the rotation of the cutting output pulley 45 is transmitted from the reverse rotation to the zero rotation through the zero rotation. For example, even when the cutting output pulley 45 is at the zero rotation, the cutting planetary gear mechanism 70 The mowing HST output shaft 38 ensures a predetermined rotational speed.

そのため、刈取部４の回転数の低い領域でも、刈取搬送用静油圧式無段変速装置２１は充分安定したトルクを有する回転を出力し、刈取部４の作業を安定させられる。
前記刈取出力プーリー４５は、前記刈取ＨＳＴ出力軸３８とは別軸の刈取中間出力軸（刈取出力軸）４５Ａに取付け、刈取中間出力軸４５Ａと刈取ＨＳＴ出力軸３８は同軸状に配置する。 Therefore, even in the region where the number of rotations of the cutting unit 4 is low, the cutting and conveying hydrostatic continuously variable transmission 21 outputs a rotation having a sufficiently stable torque, and the operation of the cutting unit 4 can be stabilized.
The cutting output pulley 45 is attached to a cutting intermediate output shaft (cutting output shaft) 45A that is separate from the cutting HST output shaft 38, and the cutting intermediate output shaft 45A and the cutting HST output shaft 38 are arranged coaxially.

そのため、ギヤケース５０をコンパクトに構成できる。
刈取用遊星歯車機構７０の構成は任意であるが、一例を示すと、浅い円筒形状のキャリア７２に遊星歯車７３を回転自在に設け、遊星歯車７３には刈取ＨＳＴ出力軸３８からの回転を伝達するサンギヤ７４を噛み合わせる。サンギヤ７４は刈取ＨＳＴ出力軸３８と一体回転するボス７４Ａに設ける。 Therefore, the gear case 50 can be configured compactly.
The configuration of the mowing planetary gear mechanism 70 is arbitrary, but as an example, a planetary gear 73 is rotatably provided on a shallow cylindrical carrier 72, and rotation from the mowing HST output shaft 38 is transmitted to the planetary gear 73. The sun gear 74 is engaged. The sun gear 74 is provided on a boss 74 A that rotates integrally with the cutting HST output shaft 38.

遊星歯車７３には別途出力遊星歯車７５を回転自在に遊嵌する。出力遊星歯車７５には刈取中間出力軸４５Ａと一体回転する入力歯車７６を噛み合わせる。
キャリア７２には環状歯車７７を設け、環状歯車７７には刈取ＨＳＴ入力軸３７に設けた一定回転するギヤ７８を噛み合わせて構成する。 An output planetary gear 75 is freely loosely fitted to the planetary gear 73 separately. The output planetary gear 75 meshes with an input gear 76 that rotates integrally with the cutting intermediate output shaft 45A.
The carrier 72 is provided with an annular gear 77, and the annular gear 77 is configured by meshing with a gear 78 that rotates at a constant rotation provided on the cutting HST input shaft 37.

即ち、刈取ＨＳＴ入力軸３７からの一定回転をキャリア７２に伝達し、刈取ＨＳＴ出力軸３８からの変速回転を遊星歯車７３に入力する構成となり、刈取用遊星歯車機構７０は入力歯車７６から刈取中間出力軸４５Ａに、逆転から零回転を経て正回転を伝達し、それゆえ、刈取出力プーリー４５が零回転のときであっても、刈取用遊星歯車機構７０により刈取ＨＳＴ出力軸３８は所定回転数で回転している。 That is, a constant rotation from the cutting HST input shaft 37 is transmitted to the carrier 72, and a variable speed rotation from the cutting HST output shaft 38 is input to the planetary gear 73, and the cutting planetary gear mechanism 70 receives the intermediate cutting from the input gear 76. The forward rotation is transmitted to the output shaft 45A through zero rotation from the reverse rotation. Therefore, even when the cutting output pulley 45 is at zero rotation, the cutting planetary gear mechanism 70 causes the cutting HST output shaft 38 to rotate at a predetermined rotational speed. It is rotating at.

換言すると、刈取ＨＳＴ出力軸３８を所定回転数で回転させていても、刈取用遊星歯車機構７０により刈取出力プーリー４５の回転を停止させておくことができる。
そのため、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８から出力される回転数を所定回転以上に保持させて、刈取搬送用静油圧式無段変速装置２１の油圧ポンプ（図示省略）から刈取搬送用静油圧式無段変速装置２１の油圧モータ（図示省略）への送油量を確保して、刈取ＨＳＴ出力軸３８の回転数を安定させ、刈取ＨＳＴ出力軸３８の回転トルクを確保し、刈取部４の負荷に対応させて、刈取部４の停止することを防止する。 In other words, even if the cutting HST output shaft 38 is rotated at a predetermined rotation speed, the cutting output pulley 45 can be stopped by the cutting planetary gear mechanism 70.
For this reason, the rotational speed output from the cutting HST output shaft 38 of the chopping and conveying hydrostatic continuously variable transmission 21 is maintained at a predetermined value or more, and the hydraulic pump of the chopping and conveying hydrostatic continuously variable transmission 21 (illustrated). (Omitted) is secured to the hydraulic motor (not shown) of the hydrostatic continuously variable transmission 21 for cutting and conveying, the rotational speed of the cutting HST output shaft 38 is stabilized, and the cutting HST output shaft 38 rotates. Torque is secured, and the cutting unit 4 is prevented from stopping in response to the load of the cutting unit 4.

また、刈取用遊星歯車機構７０は刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ入力軸３７および刈取ＨＳＴ出力軸３８を利用して設けられるので、合理的でコンパクトに構成できる。 Further, since the harvesting planetary gear mechanism 70 is provided using the harvesting HST input shaft 37 and the harvesting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for harvesting conveyance, it can be configured rationally and compactly.

この場合、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８から出力される回転を検出して、刈取出力プーリー４５への出力回転を判定するように構成する。
そのため、高精度の回転数検出ができ、刈取部４の作業速度の制御精度を向上させる。 In this case, the rotation output from the harvesting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for harvesting conveyance is detected, and the output rotation to the harvesting output pulley 45 is determined.
Therefore, the rotational speed can be detected with high accuracy, and the control accuracy of the work speed of the cutting unit 4 is improved.

刈取ＨＳＴ出力軸３８の端部に回転体７９Ａを設け、回転体７９Ａの回転を検出する回転検出手段７９Ｂを設けている。
前記刈取出力プーリー４５には、ワンウェイクラッチ８０を設ける。刈取出力プーリー４５には刈取用遊星歯車機構７０により逆回転から零回転を経て正回転まで伝達されるが、ワンウェイクラッチ８０により刈取部４に逆回転の回転が伝達されるのを防止する。 A rotary body 79A is provided at the end of the cutting HST output shaft 38, and rotation detection means 79B for detecting the rotation of the rotary body 79A is provided.
The cutting output pulley 45 is provided with a one-way clutch 80. The cutting output pulley 45 is transmitted from the reverse rotation to zero rotation by the cutting planetary gear mechanism 70, but prevents the reverse rotation from being transmitted to the cutting portion 4 by the one-way clutch 80.

即ち、刈取ＨＳＴ出力軸３８を所定回転数で回転させていても、刈取用遊星歯車機構７０により刈取出力プーリー４５の回転を停止させるためには、刈取ＨＳＴ出力軸３８の回転が停止しているときには、刈取用遊星歯車機構７０は刈取出力プーリー４５へ零回転に至る前の逆回転を出力することになるので、ワンウェイクラッチ８０により刈取部４への逆回転の伝達を防止して、刈取ＨＳＴ出力軸３８の回転数および回転トルクを安定させている。 That is, in order to stop the rotation of the cutting output pulley 45 by the cutting planetary gear mechanism 70 even if the cutting HST output shaft 38 is rotated at a predetermined rotational speed, the rotation of the cutting HST output shaft 38 is stopped. Sometimes, the cutting planetary gear mechanism 70 outputs the reverse rotation before reaching zero rotation to the cutting output pulley 45, so that the one-way clutch 80 prevents the reverse rotation from being transmitted to the cutting unit 4, and the cutting HST The rotational speed and rotational torque of the output shaft 38 are stabilized.

それゆえ、刈取ＨＳＴ出力軸３８から刈取用遊星歯車機構７０を経て刈取出力プーリー４５の下手側の刈取部４への駆動が確実になる。
また、刈取ＨＳＴ出力軸３８の回転と刈取用遊星歯車機構７０の回転により刈取出力プーリー４５の回転数が変化するが、ワンウェイクラッチ８０を設けているので逆回転が伝達されることはないので、刈取出力プーリー４５の回転数を零回転にするためには減速操作すれば良く、刈取出力プーリー４５の回転数を零回転とするニュートラル位置の設定が容易（不要）になる。 Therefore, driving from the cutting HST output shaft 38 to the cutting portion 4 on the lower side of the cutting output pulley 45 through the cutting planetary gear mechanism 70 is ensured.
Further, the rotational speed of the harvesting output pulley 45 changes due to the rotation of the harvesting HST output shaft 38 and the planetary gear mechanism 70 for harvesting, but since the one-way clutch 80 is provided, reverse rotation is not transmitted. In order to make the rotational speed of the reaping output pulley 45 zero, it is only necessary to perform a decelerating operation, and it becomes easy (unnecessary) to set the neutral position where the rotational speed of the reaping output pulley 45 is zero.

しかして、刈取部４およびシンクロ用前側供給搬送装置１１への伝達回転は、刈取搬送用静油圧式無段変速装置２１により変速し、刈取搬送用静油圧式無段変速装置２１が刈取部４を走行速度の増減速に合わせて同調させて変速する。 Therefore, the transmission rotation to the cutting part 4 and the front-side supply / conveyance device 11 for synchronization is shifted by the hydrostatic continuously variable transmission 21 for harvesting and conveying. Is synchronized with the increase / decrease of the running speed.

即ち、刈取中間出力軸４５Ａに別途シンクロ用歯車８２を設け、シンクロ用歯車８２に中間軸８３の歯車（第１歯車）８４を噛み合わせる。中間軸８３には別途歯車（第２歯車）８４Ａを設け、歯車８４Ａの回転を搬送シンクロ用出力軸４０の歯車８５に伝達し、刈取用遊星歯車機構７０により刈取部４に伝達する回転と同じ回転をシンクロ用前側供給搬送装置１１に伝達する。 That is, a separate synchro gear 82 is provided on the cutting intermediate output shaft 45 A, and the gear (first gear) 84 of the intermediate shaft 83 is engaged with the synchro gear 82. The intermediate shaft 83 is provided with a separate gear (second gear) 84 A, and the rotation of the gear 84 A is transmitted to the gear 85 of the conveying synchro output shaft 40 and is the same as the rotation transmitted to the cutting unit 4 by the cutting planetary gear mechanism 70. The rotation is transmitted to the front supply / conveyor 11 for synchronization.

したがって、刈取部４の回転と同期した回転をシンクロ用前側供給搬送装置１１に伝達するので、搬送性能が向上する。
また、ギヤケース５０内に中間軸８３と歯車８４および歯車８４Ａを納めることができ、構成を簡素にできる。 Therefore, since the rotation synchronized with the rotation of the cutting unit 4 is transmitted to the front supply / conveyor device 11 for synchronization, the conveyance performance is improved.
Further, the intermediate shaft 83, the gear 84, and the gear 84A can be accommodated in the gear case 50, and the configuration can be simplified.

また、刈取搬送用静油圧式無段変速装置２１は、単独で走行用静油圧式無段変速装置１２とは無関係に刈取部４および／またはシンクロ用前側供給搬送装置１１を駆動できるので、機体停止状態から所定走行速度の間でも、刈取搬送用静油圧式無段変速装置２１および刈取用遊星歯車機構７０により刈取部４およびシンクロ用前側供給搬送装置１１を十分な回転数で駆動させることができ、機体走行開始直後から安定して刈取部４および脱穀装置２を駆動させられ、刈取作業および脱穀作業を安定・確実に行える。 Further, the hydrostatic continuously variable transmission 21 for harvesting and conveying can drive the harvesting unit 4 and / or the front supply / conveyor 11 for synchronization independently of the hydrostatic continuously variable transmission 12 for traveling. Even during the predetermined traveling speed from the stop state, the mowing section 4 and the synchro front supply and transport apparatus 11 can be driven at a sufficient number of revolutions by the mowing and conveying hydrostatic continuously variable transmission 21 and the mowing planetary gear mechanism 70. The reaping part 4 and the threshing device 2 can be driven stably immediately after the start of the vehicle running, and the reaping work and the threshing work can be performed stably and reliably.

また、走行用静油圧式無段変速装置１２から走行装置３への回転を停止させたとき、単独の刈取搬送用静油圧式無段変速装置２１でシンクロ用前側供給搬送装置１１を駆動すると、機体走行停止状態でシンクロ用前側供給搬送装置１１を駆動し、シンクロ用前側供給搬送装置１１および穀稈供給搬送装置１０へ手刈り穀稈を供給でき、刈取作業および脱穀作業の作業性および操作性を向上させられる。 Further, when the rotation from the hydrostatic continuously variable transmission 12 for traveling to the traveling device 3 is stopped, the front supply / conveyor 11 for synchronization is driven by the single hydrostatic continuously variable transmission 21 for harvesting and conveying, The front-side supply / conveyance device 11 for synchronization is driven in a state where the machine body is stopped, and the hand-harvested cereal can be supplied to the front-side supply / conveyance device 11 for synchronization and the cereal supply / conveyance device 10. Can be improved.

しかして、操縦部７の運転座席８６の下方（後側）付近には周囲を包囲されたエンジンルーム８７を形成し、エンジンルーム８７内にエンジン２２を設け、エンジン２２の外側（右側）にはエンジン冷却用ファン８８を設け、エンジン冷却用ファン８８の外側にはラジエーター８９を設け、ラジエーター８９の外側にはラジエーターカバー９０を設ける。ラジエーターカバー９０は枠体９１を有する。枠体９１には防塵ネット９２を設ける（図１１）。 Thus, an engine room 87 is formed in the vicinity of the lower part (rear side) of the driver seat 86 of the control unit 7, and the engine room 87 is provided in the engine room 87, and the engine 22 is provided outside (on the right side) of the engine 22. An engine cooling fan 88 is provided, a radiator 89 is provided outside the engine cooling fan 88, and a radiator cover 90 is provided outside the radiator 89. The radiator cover 90 has a frame body 91. A dustproof net 92 is provided on the frame 91 (FIG. 11).

防塵ネット９２の内側には所定の幅（前後幅）を有して縦長の遮風プレート９３をラジエーターカバー９０の幅方向（機体進行方向・前後方向）に往復移動自在に設ける。遮風プレート９３は、ラジエーターカバー９０の幅方向に移動する行程において、エンジン冷却用ファン８８の吸引作用で防塵ネット９２に付着している付着物のうちの一部を遮風プレート９３により一時的にエンジン冷却用ファン８８の吸引風を遮断することで付着力を失わせて（低下させて）落下させると共に、その余の付着物は他の防塵ネット９２の部分を通過する吸引風よりも流速が高く（速く）強い吸引力の吸引風が通る遮風プレート９３の端縁付近の防塵ネット９２部分に付着させたまま遮風プレート９３と一緒に移動（連れ動ごか）させて防塵ネット９２の目詰まりを除去する。 A vertically long wind shielding plate 93 having a predetermined width (front-rear width) is provided inside the dust-proof net 92 so as to be reciprocally movable in the width direction of the radiator cover 90 (the machine body traveling direction and the front-rear direction). In the process of moving in the width direction of the radiator cover 90, the wind shield plate 93 temporarily removes some of the deposits attached to the dust net 92 by the suction action of the engine cooling fan 88 by the wind shield plate 93. In addition, the suction force of the engine cooling fan 88 is blocked so that the adhesive force is lost (decreased) and dropped, and the remaining adhering matter has a flow velocity higher than that of the suction air passing through the other dustproof net 92. The dustproof net 92 is moved together with the windshield plate 93 while being attached to the dustproof net 92 portion near the edge of the windshield plate 93 through which the suction air of high (fast) and strong suction force passes. Remove clogging.

即ち、遮風プレート９３は一時的にエンジン冷却用ファン８８の吸引風を遮断して防塵ネット９２に付着している付着物のうちの一部の付着力を低下させて落下させるが、遮風プレート９３の移動方向上手側の端縁付近に他の防塵ネット９２を通過する外気より吸引力の強い吸引風を積極的に通して、遮風プレート９３の端縁と一緒に防塵ネット９２の付着物を移動させて防塵ネット９２の目詰まりを除去する。 In other words, the wind shield plate 93 temporarily blocks the suction air of the engine cooling fan 88 and reduces the adhesion force of some of the deposits adhering to the dust proof net 92 and drops it. A suction air having a stronger suction force than the outside air passing through the other dustproof net 92 is actively passed near the edge on the upper side in the moving direction of the plate 93, and the dustproof net 92 is attached together with the edge of the windshield plate 93. The kimono is moved to remove clogging of the dustproof net 92.

遮風プレート９３と枠体９１との間に遮風プレート９３の移動を案内するガイド機構９４を設ける（図１４）。
枠体９１の下横枠には案内レール９５を設け、案内レール９５に枠体９１の下部を摺動案内するように嵌合させる。 A guide mechanism 94 for guiding the movement of the wind shield plate 93 is provided between the wind shield plate 93 and the frame body 91 (FIG. 14).
A guide rail 95 is provided in the lower horizontal frame of the frame body 91 and is fitted to the guide rail 95 so as to slide and guide the lower portion of the frame body 91.

枠体９１の上横枠には案内レール９５を設け、案内レール９５には遮風プレート９３の案内体９６を嵌合（係合）させる。案内体９６はベアリング（図示省略）を有する軸受９７を介して軸９８により遮風プレート９３に回転自在に取付ける。 A guide rail 95 is provided on the upper horizontal frame of the frame body 91, and the guide body 96 of the wind shielding plate 93 is fitted (engaged) with the guide rail 95. The guide body 96 is rotatably attached to the wind shielding plate 93 by a shaft 98 via a bearing 97 having a bearing (not shown).

そのため、遮風プレート９３の移動を円滑にする。
遮風プレート９３は上側プレート９９Ａと下側プレート９９Ｂとの二つに分割し、上側プレート９９Ａに長孔１００を形成し、下側プレート９９Ｂには長孔１００内を移動する案内体１０１を設け、遮風プレート９３は長孔１００の部分で伸縮自在であって屈曲自在に上側プレート９９Ａと下側プレート９９Ｂを連結する。 Therefore, the movement of the wind shielding plate 93 is made smooth.
The wind shielding plate 93 is divided into an upper plate 99A and a lower plate 99B, a long hole 100 is formed in the upper plate 99A, and a guide body 101 that moves in the long hole 100 is provided in the lower plate 99B. The wind shielding plate 93 is telescopic at the portion of the long hole 100 and bends the upper plate 99A and the lower plate 99B.

したがって、枠体９１の斜め枠部分の斜めになっている防塵ネット９２の端末の部分も、短い上側案内レール９５の終点位置に上側プレート９９Ａが達すると、上側プレート９９Ａが斜め部分に沿うように傾斜移動して吸引外気を遮断する（図１７）。 Therefore, when the upper plate 99A reaches the end position of the short upper guide rail 95, the end portion of the dustproof net 92 that is inclined at the oblique frame portion of the frame 91 is also arranged so that the upper plate 99A follows the oblique portion. The suctioned outside air is shut off by tilting (FIG. 17).

この場合、案内体１０１は図示は省略するが、ベアリング（図示省略）を有する軸受を介して軸により遮風プレート９３に回転自在に取付ける。
また、上側の案内体９６にはバネ１０２を設け、遮風プレート９３の上側プレート９９Ａと下側プレート９９Ｂとが、常時直線状態に短縮するように付勢する。 In this case, although not shown, the guide body 101 is rotatably attached to the wind shielding plate 93 by a shaft via a bearing having a bearing (not shown).
Further, the upper guide body 96 is provided with a spring 102, and the upper plate 99A and the lower plate 99B of the wind shielding plate 93 are always urged so as to be shortened in a straight line state.

したがって、枠体９１の斜め部分から離れる移動行程では、遮風プレート９３は直線状態になって移動する。
しかして、遮風プレート９３の移動構成は任意であるが、例えば、枠体９１の中間上横枠に伝動軸（リードカム軸）１０３を回転自在に軸装し、伝動軸１０３に伝動軸１０３の回転により軸心方向に移動する移動部材１０４を取付け、移動部材１０４は遮風プレート９３に取付ける（図１４）。 Therefore, in the movement process which leaves | separates from the diagonal part of the frame 91, the wind shielding plate 93 moves in a linear state.
However, the moving structure of the wind shielding plate 93 is arbitrary. For example, the transmission shaft (lead cam shaft) 103 is rotatably mounted on the middle horizontal frame of the frame 91, and the transmission shaft 103 is connected to the transmission shaft 103. A moving member 104 that moves in the axial direction by rotation is attached, and the moving member 104 is attached to the wind shield plate 93 (FIG. 14).

しかして、遮風プレート９３の移動行程の終端の何れか一方側または両側の枠体９１には、遮風プレート９３の端縁が移動させた付着物を吸引する塵埃吸引口１０５を設ける。
したがって、塵埃吸引口１０５は、遮風プレート９３の移動方向上手側の端縁付近の防塵ネット９２に付着して遮風プレート９３に連れ動かされた付着物を、通常の防塵ネット９２を通過する外気よりも流速の高い塵埃吸引口１０５を通る強い吸引風により吸引除去する。 Accordingly, a dust suction port 105 is provided on the frame body 91 on either one side or both sides of the end of the movement process of the wind shielding plate 93 to suck the attached matter moved by the edge of the wind shielding plate 93.
Accordingly, the dust suction port 105 passes through the normal dustproof net 92 through the adhering matter attached to the dustproof net 92 near the edge on the upper side in the moving direction of the windshield plate 93 and moved by the windshield plate 93. Suction removal is performed by a strong suction air passing through the dust suction port 105 having a higher flow velocity than the outside air.

防塵ネット９２の付着物が遮風プレート９３に連れ動かされて塵埃吸引口１０５により強制的に除去されるので、常時、ラジエーターカバー９０の防塵ネット９２を綺麗にして、エンジンルームエンジンルーム８７内の冷却効果を安定して維持する。 The adhering matter on the dustproof net 92 is moved by the wind shield plate 93 and forcibly removed by the dust suction port 105. Therefore, the dustproof net 92 of the radiator cover 90 is always cleaned, and the inside of the engine room engine room 87 is kept clean. Maintain a stable cooling effect.

操縦部６の操作パネル１１０に設けた種々のレバー１１１の操作溝１１２に閉塞部材１１３を設ける。閉塞部材１１３はプレート１１４に操作溝１１２より幅狭の溝１１５を形成すると共に、溝１１５を閉塞するように、左右側から一対のブラシ１１６を対峙させて設けている。 A closing member 113 is provided in operation grooves 112 of various levers 111 provided on the operation panel 110 of the control unit 6. The closing member 113 is formed with a groove 115 narrower than the operation groove 112 in the plate 114 and a pair of brushes 116 facing each other from the left and right sides so as to close the groove 115.

閉塞部材１１３は、操作パネル１１０の下面側に取付ける。
したがって、操作パネル１１０の下方に操作溝１１２からの異物の混入を防止する。
（実施例の作用）
機体を走行させると、刈取部４が圃場の穀稈を刈り取って搬送し、刈取部４により搬送された穀稈はシンクロ用前側供給搬送装置１１に引き継がれ、シンクロ用前側供給搬送装置１１は穀稈を穀稈供給搬送装置１０に受け渡し、穀稈供給搬送装置１０は穀稈を一定速度で搬送して脱穀装置２の脱穀室に供給して脱穀する。 The closing member 113 is attached to the lower surface side of the operation panel 110.
Therefore, foreign matter from the operation groove 112 is prevented from entering the operation panel 110 below.
(Operation of Example)
When the machine is run, the cutting unit 4 harvests and transports the cereals in the field, the cereals transported by the cutting unit 4 are taken over by the synchro front supply transport device 11, and the synchro front supply transport device 11 The cocoon is delivered to the cereal supply / conveyance device 10, and the cereal supply / conveyance device 10 conveys the cereal at a constant speed and supplies it to the threshing chamber of the threshing device 2 for threshing.

走行装置３は走行用静油圧式無段変速装置１２により主変速レバー１３を傾倒させると、走行用静油圧式無段変速装置１２がエンジン２２の一定回転を無段階に変速して伝達し、走行速度変更可能に構成し、刈取部４およびシンクロ用前側供給搬送装置１１へ伝達する回転も走行装置３の走行速度に同調して変速するようにしているので、刈取部４は走行速度に応じて最適な作業回転数が伝達される When the traveling device 3 tilts the main transmission lever 13 by the traveling hydrostatic continuously variable transmission 12, the traveling hydrostatic continuously variable transmission 12 transmits the constant rotation of the engine 22 steplessly and transmits it. Since the traveling speed can be changed, and the rotation transmitted to the cutting unit 4 and the front supply / conveyor 11 for synchronization is also synchronized with the traveling speed of the traveling device 3, the cutting unit 4 is adapted to the traveling speed. The optimum working speed is transmitted

即ち、主変速レバー１３を傾倒操作すると、走行用静油圧式無段変速装置１２によりエンジン２２の一定回転が無段階に変速されて走行装置３に伝達され、走行装置３の走行速度に同調して刈取部４およびシンクロ用前側供給搬送装置１１へ伝達する回転も変速される。 That is, when the main transmission lever 13 is tilted, the constant rotation of the engine 22 is continuously shifted by the traveling hydrostatic continuously variable transmission 12 and transmitted to the traveling device 3, and is synchronized with the traveling speed of the traveling device 3. The rotation transmitted to the cutting part 4 and the front supply / conveyor 11 for synchronization is also shifted.

また、刈取搬送用静油圧式無段変速装置２１は、単独で走行用静油圧式無段変速装置１２とは無関係に刈取部４を駆動できるので、操作レバー（図示省略）により刈取搬送用静油圧式無段変速装置２１を作動させると、刈取部４を駆動させる。 Further, the hydrostatic continuously variable transmission 21 for harvesting and conveying can drive the harvesting unit 4 independently of the traveling hydrostatic continuously variable transmission 12 for traveling, and therefore, the stationary lever for harvesting and conveying is operated by an operation lever (not shown). When the hydraulic continuously variable transmission 21 is operated, the cutting unit 4 is driven.

この場合、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８から出力される回転数が低いときには、油圧ポンプ（図示省略）から刈取搬送用静油圧式無段変速装置２１の油圧モータ（図示省略）への送油量が少ないため、刈取ＨＳＴ出力軸３８の回転数は一定せずに不安定となり、また、刈取ＨＳＴ出力軸３８の伝達する回転トルクも低くいことがあり、刈取部４の負荷が大きいと、穀稈を噛み込んだり、最悪のときには刈取部４が停止することがある。 In this case, when the rotational speed output from the cutting HST output shaft 38 of the chopping and conveying hydrostatic continuously variable transmission 21 is low, the hydraulic pressure of the chopping and conveying hydrostatic continuously variable transmission 21 from a hydraulic pump (not shown). Since the amount of oil supplied to the motor (not shown) is small, the rotational speed of the cutting HST output shaft 38 is not constant and unstable, and the rotational torque transmitted by the cutting HST output shaft 38 may be low. If the load of the reaping part 4 is large, the cereals may be bitten or the reaping part 4 may stop in the worst case.

本願では、前記刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８と、刈取中間出力プーリー刈取出力プーリー４５との間には刈取用遊星歯車機構７０を設け、刈取用遊星歯車機構７０は、刈取ＨＳＴ出力軸３８の回転数が所定回転数以上になったとき、刈取出力プーリー４５に回転出力するように構成してるので、刈取ＨＳＴ出力軸３８が安定して充分な回転トルクを有する駆動回転を刈取出力プーリー４５に出力することができる。 In the present application, the HST output shaft 38 Cutting of the transport hydrostatic continuously variable transmission 21 the reaper, the mowing take-up planetary gear mechanism 70 is provided between the intermediate output pulley reaper output pulley 45 reaper provided, the planet gear for Reaper The mechanism 70 is configured to rotate and output to the cutting output pulley 45 when the rotational speed of the cutting HST output shaft 38 becomes equal to or higher than a predetermined rotational speed, so that the cutting HST output shaft 38 is stable and has sufficient rotational torque. Can be output to the cutting output pulley 45.

特に、刈取部４を低速回転で刈取作業するとき、刈取部４を安定させて負荷に耐える作業が可能となり、作業性を向上させる。
即ち、刈取用遊星歯車機構７０は、刈取ＨＳＴ出力軸３８からの回転を、刈取出力プーリー４５が逆回転から零回転を経て正回転するように伝達するから、例え、刈取出力プーリー４５が零回転のときであっても、刈取用遊星歯車機構７０により刈取ＨＳＴ出力軸３８は所定回転トルクを有して回転している。 In particular, when the cutting unit 4 is cut at a low speed, the cutting unit 4 can be stabilized to withstand a load, and workability is improved.
In other words, the cutting planetary gear mechanism 70 transmits the rotation from the cutting HST output shaft 38 so that the cutting output pulley 45 rotates from the reverse rotation to the positive rotation through zero rotation. For example, the cutting output pulley 45 rotates at zero rotation. Even at this time, the cutting HST output shaft 38 is rotated with a predetermined rotational torque by the cutting planetary gear mechanism 70.

そのため、刈取部４の回転数の低い領域でも、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８は充分安定した回転トルクを有する回転を出力し、刈取部４の作業を安定させられる。 Therefore, even in the region where the number of rotations of the cutting unit 4 is low, the cutting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for cutting conveyance outputs a sufficiently stable rotation torque, and the operation of the cutting unit 4 is stabilized. Be made.

刈取出力プーリー４５は、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ出力軸３８とは別途形成した刈取中間出力軸４５Ａに取付け、刈取中間出力軸４５Ａと刈取ＨＳＴ出力軸３８は同軸状に配置しているので、ギヤケース５０をコンパクトに構成できる。 The harvesting output pulley 45 is attached to a harvesting intermediate output shaft 45A formed separately from the harvesting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for harvesting conveyance, and the harvesting intermediate output shaft 45A and the harvesting HST output shaft 38 are coaxial. The gear case 50 can be made compact.

刈取用遊星歯車機構７０は、浅い円筒形状のキャリア７２に遊星歯車７３と環状歯車７７を設け、環状歯車７７に一定回転するギヤ７８により刈取ＨＳＴ入力軸３７からの一定回転を入力し、キャリア７２に刈取ＨＳＴ出力軸３８からの変速回転を遊星歯車７５とサンギヤ７４により入力する構成であるから、刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ入力軸３７および刈取ＨＳＴ出力軸３８を利用して刈取用遊星歯車機構７０を構成して設置できるので、合理的でコンパクトに構成できる。 The cutting planetary gear mechanism 70 is provided with a planetary gear 73 and an annular gear 77 in a shallow cylindrical carrier 72, and a constant rotation from the cutting HST input shaft 37 is input to the annular gear 77 by a gear 78 that rotates at a constant speed. Since the shift rotation from the cutting HST output shaft 38 is input by the planetary gear 75 and the sun gear 74, the cutting HST input shaft 37 and the cutting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for cutting conveyance are used. Since the mowing planetary gear mechanism 70 can be configured and installed, it can be configured rationally and compactly.

しかして、刈取出力プーリー４５は、刈取用遊星歯車機構７０により逆回転から零回転を経て正回転まで伝達するが、刈取部４に逆回転の回転が伝達されないように、刈取出力プーリー４５にワンウェイクラッチ８０を設けているので、刈取部４への駆動が確実になる。 Thus, the cutting output pulley 45 is transmitted from the reverse rotation to the positive rotation through the zero rotation by the cutting planetary gear mechanism 70, but the one-way transmission to the cutting output pulley 45 is prevented so that the reverse rotation is not transmitted to the cutting unit 4. Since the clutch 80 is provided, driving to the cutting unit 4 is ensured.

特に、刈取出力プーリー４５の回転領域を逆回転するように、刈取ＨＳＴ出力軸３８および刈取用遊星歯車機構７０を設定しても、ワンウェイクラッチ８０により刈取部４の逆転は回避できるので、刈取ＨＳＴ出力軸３８の回転数の設定および刈取用遊星歯車機構７０の各歯車のギヤ比の設定が容易にでき、厳密な刈取出力プーリー４５の回転数を零回転にさせるニュートラル位置の設定が不要になる。 In particular, even if the cutting HST output shaft 38 and the cutting planetary gear mechanism 70 are set so as to reversely rotate the rotation region of the cutting output pulley 45, the one-way clutch 80 can avoid the reverse rotation of the cutting unit 4, so the cutting HST It is possible to easily set the rotation speed of the output shaft 38 and the gear ratio of each gear of the cutting planetary gear mechanism 70, and it is not necessary to set the neutral position to make the rotation speed of the cutting output pulley 45 exactly zero. .

しかして、刈取中間出力軸４５Ａに別途シンクロ用歯車８２を設け、シンクロ用歯車８２に中間軸８３の歯車８４を噛み合わせ、歯車８４の回転を搬送シンクロ用出力軸４０の歯車８５に伝達するので、刈取用遊星歯車機構７０により刈取部４に伝達する回転と同じ回転をシンクロ用前側供給搬送装置１１に伝達する。 Therefore, a separate synchro gear 82 is provided on the cutting intermediate output shaft 45A, the gear 84 of the intermediate shaft 83 is meshed with the synchro gear 82, and the rotation of the gear 84 is transmitted to the gear 85 of the transport synchro output shaft 40. Then, the same rotation as that transmitted to the cutting unit 4 by the cutting planetary gear mechanism 70 is transmitted to the synchro front supply / conveyance device 11.

したがって、刈取部４の回転と同期した回転をシンクロ用前側供給搬送装置１１に伝達するので、搬送性能が向上する。
また、ギヤケース５０内に中間軸８３と歯車８４が納めることができ、構成を簡素にできる。 Therefore, since the rotation synchronized with the rotation of the cutting unit 4 is transmitted to the front supply / conveyor device 11 for synchronization, the conveyance performance is improved.
Further, the intermediate shaft 83 and the gear 84 can be housed in the gear case 50, and the configuration can be simplified.

しかして、エンジン２２から各部の回転伝動について簡単に説明すると、エンジン２２の回転が中間プーリー２８に伝達され、中間プーリー２８は中間軸２９と中間歯車３０を介してケースの中間伝動軸３１に回転を伝達し、中間伝動軸３１で扱胴３４側と穀稈供給搬送中間出力軸４１および刈取搬送用静油圧式無段変速装置２１とに伝動を分岐する。脱穀用傘歯車３２に伝達された回転は扱胴３４に伝達して駆動する。 Thus, the rotation transmission of each part from the engine 22 will be briefly described. The rotation of the engine 22 is transmitted to the intermediate pulley 28, and the intermediate pulley 28 rotates to the intermediate transmission shaft 31 of the case via the intermediate shaft 29 and the intermediate gear 30. The intermediate transmission shaft 31 branches the transmission to the handling cylinder 34 side, the grain supply / conveyance intermediate output shaft 41 and the chopping / conveying hydrostatic continuously variable transmission 21. The rotation transmitted to the threshing bevel gear 32 is transmitted to the barrel 34 and driven.

中間伝動軸３１の回転は穀稈供給搬送中間出力軸４１に伝達されて、穀稈供給搬送中間出力軸４１の回転は穀稈供給搬送装置１０の終端側から入力させて、穀稈供給搬送装置１０を駆動する。 The rotation of the intermediate transmission shaft 31 is transmitted to the grain supply / intermediate output shaft 41, and the rotation of the grain supply / transport intermediate output shaft 41 is input from the terminal side of the grain supply / transport apparatus 10, 10 is driven.

したがって、穀稈供給搬送中間出力軸４１は走行用静油圧式無段変速装置１２および刈取搬送用静油圧式無段変速装置２１とは無関係にエンジン２２からの一定に設定された回転を、穀稈供給搬送装置１０に伝達し、穀稈供給搬送装置１０と扱胴３４とは常時同じ関係で回転する。 Accordingly, the cereal supply / conveyance intermediate output shaft 41 generates a constant rotation from the engine 22 regardless of the hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for harvesting and conveying. It is transmitted to the koji supply / conveyance device 10, and the cereal supply / conveyance device 10 and the handling cylinder 34 always rotate in the same relationship.

穀稈供給搬送中間出力軸４１の下手側には刈取用中間歯車３６により回転が伝達される刈取搬送用静油圧式無段変速装置２１の刈取ＨＳＴ入力軸３７を設けているので、穀稈供給搬送中間出力軸４１の回転が刈取搬送用静油圧式無段変速装置２１のポンプに入力されて、刈取搬送用静油圧式無段変速装置２１のモータから変速された回転刈取ＨＳＴ出力軸３８により出力され、刈取ＨＳＴ出力軸３８の回転が刈取用遊星歯車機構７０により変速されて刈取用中間出力軸３９および搬送シンクロ用出力軸４０により刈取部４およびシンクロ用前側供給搬送装置１１を駆動回転させる。 On the lower side of the grain supply / conveyance intermediate output shaft 41, there is provided the harvesting HST input shaft 37 of the hydrostatic continuously variable transmission 21 for harvesting and conveying, whose rotation is transmitted by the intermediate gear 36 for harvesting. The rotation of the conveyance intermediate output shaft 41 is input to the pump of the hydrostatic continuously variable transmission 21 for harvesting and conveying, and is output by the rotary harvesting HST output shaft 38 that is shifted from the motor of the hydrostatic continuously variable transmission 21 for harvesting and conveying. The rotation of the cutting HST output shaft 38 is shifted by the cutting planetary gear mechanism 70, and the cutting intermediate output shaft 39 and the conveying synchro output shaft 40 drive and rotate the cutting unit 4 and the synchro front supply / conveyance device 11. .

なお、前記した各実施例は、理解を容易にするために、個別または混在させて図示、あるいは説明しており、ブロック図等を含めたこれらの実施例は相互に夫々種々組合せ可能であり、これらの表現によって、構成・作用等が限定されるものではなく、また、相乗効果を奏する場合も勿論存在する。 In addition, for ease of understanding, each of the above-described embodiments is illustrated or described individually or mixedly, and these embodiments including a block diagram can be variously combined with each other. These expressions are not intended to limit the configuration / action and the like, and there are, of course, cases where a synergistic effect is achieved.

１機体フレーム
２脱穀装置
３走行装置
４刈取部
５グレンタンク
６操縦部
１０供給搬送装置
１１前側供給搬送装置
２１刈取搬送用静油圧式無段変速装置（静油圧式無段変速装置）
２２エンジン
３４扱胴
３７刈取ＨＳＴ入力軸（入力軸）
３８刈取ＨＳＴ出力軸（出力軸）
４０搬送シンクロ用出力軸
４５刈取中間出力プーリー（刈取出力プーリー）
４５Ａ刈取中間出力軸（刈取出力軸）
５０ギヤケース
７０刈取用遊星歯車機構（遊星歯車機構）
７２キャリア
７４サンギヤ
７６入力歯車
７７環状歯車
７８ギヤ
８０ワンウェイクラッチ
８６運転座席
８７エンジンルーム
８８エンジン冷却用ファン
８９ラジエーター
９０ラジエーターカバー
９２防塵ネット
９３遮風プレート
９９Ａ上側プレート
９９Ｂ下側プレート
１００長孔
１０１案内体 1 body frame
2 Threshing device
3 traveling device 4 mowing part
5 Glen tank
6 Steering part 10 Supply conveyance device 11 Front supply conveyance device 21 Hydrostatic continuously variable transmission for harvesting conveyance (hydrostatic continuously variable transmission)
22 engine
34 Handling cylinder 37 Cutting HST input shaft (input shaft)
38 Harvesting HST output shaft (output shaft)
40 Conveyor sync output shaft 45 Cutting intermediate output pulley (cutting output pulley)
45A Mowing intermediate output shaft (Mowing output shaft)
50 gear case 70 Planetary gear mechanism for cutting (planetary gear mechanism)
72 Carrier 74 Sun gear 76 Input gear 77 Annular gear 78 Gear 80 One-way clutch
86 driver's seat
87 engine room
88 Engine cooling fan
89 radiator
90 radiator cover
92 dustproof net
93 wind shield plate
99A upper plate
99B lower plate
100 long holes
101 guide

Claims

A threshing device (2) provided with a supply conveying device (10) for supplying threshing cereals is provided at an upper position of a machine frame (1) provided with a traveling device (3), and in front of the machine frame (1). In a combine provided with a cutting part (4), provided with a grain tank (5) on the lateral side of the threshing device (2), and provided with a control part (6) on the front side of the grain tank (5), the control part ( The engine room (87) is provided below the driver seat (86) provided in 6), and the engine cooling fan (88) is provided outside the engine (22) provided in the engine room (87). A radiator cover (90) having a dust-proof net (92) is provided outside the radiator (89) provided outside the cooling fan (88), and a predetermined width is provided inside the dust-proof net (92). Vertical wind shield plate (9 ) And, provided reciprocally move in the width direction of the radiator cover (90), the output shaft of the engine (hydrostatic driven by 22) continuously variable transmission (21) and (38), reaper (4 ), A planetary gear mechanism (70) is provided between the cutting output shaft (45A) for outputting the driving force to the rotary shaft, the rotation of the output shaft (38) of the hydrostatic continuously variable transmission (21), and the hydrostatic type CVT input shaft (21) rotation of (37) was synthesized by the planetary gear mechanism (70), and configured to output reaper from the reaper output shaft (45A) to (4), said planetary gear A planetary gear is rotatably provided on a cylindrical carrier (72) in the mechanism (70), and a sun gear (74) that transmits rotation from the output shaft (38) is meshed with the planetary gear, and the planetary gear is engaged with the planetary gear. Rotates together with the cutting output shaft (45A) The input gear (76) is meshed, and the annular gear (77) provided on the carrier (72) is meshed with the gear (78) provided on the input shaft (37) of the hydrostatic continuously variable transmission (21). The planetary gear mechanism (70) is configured to transmit the rotation of the output shaft (38) to the reaping output shaft (45A) by rotating the rotation of the output shaft (38) from the reverse rotation to the reaping output shaft (45A) through zero rotation. ) And a cutting output pulley (45) provided on the cutting output shaft (45A), a one-way clutch (80) for preventing transmission of reverse rotation to the cutting unit (4) is provided, and the engine (22) A gear case (50) for branching and transmitting power from the threshing device (2) to the barrel (34) of the threshing device (2) and the supply conveying device (10), and the hydrostatic continuously variable transmission (21) to the gear case Parts on the control unit (6) side in (50) Combines characterized by being provided in .

A front supply / conveyance device (11) is provided at the conveyance start end of the supply / conveyance device (10), and the front supply / conveyance device (11) is connected to an output shaft (40) for synchronization synchronized with the cutting output shaft (45A). 2. The combine according to claim 1, wherein the combine is driven by

The wind shield plate (93) is divided into an upper plate (99A) and a lower plate (99B), a long hole (100) is formed in the lower part of the upper plate (99A), and the lower plate (99B) A guide body (101) that moves in the elongated hole (100) is provided at the upper portion, and the lower portion of the upper plate (99A) and the upper portion of the lower plate (99B) are disposed on the elongated hole (100) and the guide body (101). The combine according to claim 2, wherein the combine is connected to be stretchable and bendable .