JP5387825B2

JP5387825B2 - Combine

Info

Publication number: JP5387825B2
Application number: JP2009064298A
Authority: JP
Inventors: 靖藤田; 嘉隆上路; 孝彦上村
Original assignee: Iseki and Co Ltd
Current assignee: Iseki and Co Ltd
Priority date: 2009-03-17
Filing date: 2009-03-17
Publication date: 2014-01-15
Anticipated expiration: 2029-03-17
Also published as: JP2010213625A

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０６−１７９２８JP 06-17928 A

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。
本願は、走行用静油圧式無段変速装置とは別の刈取搬送用静油圧式無段変速装置により刈取部を駆動させる構成を採用し、刈取部の低速回転領域の作業を安定するように工夫したものである。 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.
The present application adopts a configuration in which the cutting unit is driven by a hydrostatic continuously variable transmission for cutting and conveying that is different from the hydrostatic continuously variable transmission for traveling so as to stabilize the work in the low-speed rotation region of the cutting unit. It is a devised one.

請求項１記載の発明では、走行用静油圧式無段変速装置１２により走行速度を無段階に変速可能な走行装置３の前方に刈取部４を設け、走行装置３の上方には脱穀装置２を設け、前記刈取部４は走行装置３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２１により変速駆動する構成とし、刈取搬送用静油圧式無段変速装置２１の出力軸である第１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７０を設け、刈取用遊星歯車機構７０は、キャリア７２に遊星歯車７３を回転自在に軸支すると共に環状歯車７７を一体に設け、環状歯車７７にエンジン２２から駆動される入力軸３７に取付けたギヤ７８を噛み合わせ、前記第１出力軸３８に取付けたサンギヤ７４を遊星歯車７３に噛み合わせ、該遊星歯車７３を前記刈取出力プーリー４５を備えた刈取出力軸４５Ａに固定の入力歯車７６に噛み合わせる構成とし、刈取部４によって刈り取られた穀稈を脱穀装置２の扱室に供給する穀稈供給搬送装置１０を備え、該穀稈供給搬送装置１０の搬送始端側に前側供給搬送装置１１を設け、エンジン２２の駆動力が中間軸２９を介してギヤケース５０に入力する構成とし、該ギヤケース５０内の伝動機構における中間軸２９と刈取搬送用静油圧式無段変速装置２１の入力軸である前記入力軸３７との間の部位から、扱胴３４を連動する脱穀伝動軸３３と、穀稈供給搬送装置１０を連動する中間出力軸４１を、定速で駆動する構成とし、前記第１出力軸３８から、刈取用遊星歯車機構７０を介して、刈取部４を連動する刈取出力軸４５Ａと、前側供給搬送装置１１を連動する第２出力軸４０を、車速に同調した速度で駆動する構成としたコンバインとしたものであり、走行用静油圧式無段変速装置１２によりエンジン２２の一定回転を無段階に変速して走行装置３に伝達して走行し、走行装置３の走行速度に同調して刈取部４へ伝達する回転も変速される。
また、刈取搬送用静油圧式無段変速装置２１は、走行用静油圧式無段変速装置１２とは独立して刈取部４を駆動できるので、刈取搬送用静油圧式無段変速装置２１が作動すると、刈取部４が駆動される。
この場合、刈取搬送用静油圧式無段変速装置２１の出力軸である第１出力軸３８から出力される回転数が低いとき、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、第１出力軸３８の回転数は一定せずに不安定となり、また、第１出力軸３８の伝達する回転トルクも低いことがあり、刈取部４の負荷が大きいと、穀稈を噛み込んだり、最悪のときには機体が走行しているにも拘わらず刈取部４が停止することがあるが、刈取搬送用静油圧式無段変速装置２１の回転を刈取用遊星歯車機構７０を介して刈取部４に伝達するので、刈取用遊星歯車機構７０は、第１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に回転出力し、刈取部４の低速回転での刈取作業を安定して行える。
請求項２記載の発明では、前記刈取出力プーリー４５から刈取部４に至る伝動系路中にワンウェイクラッチ８０を設け、前記第１出力軸３８を所定の速度で回転させている状態で刈取出力軸４５Ａの回転が停止し、該第１出力軸３８を所定の速度よりも高速で回転させると刈取出力軸４５Ａが正転し、該第１出力軸３８を所定の速度よりも低速で回転させると刈取出力軸４５Ａが逆転する構成としたコンバインとしたものであり、刈取用遊星歯車機構７０は逆回転から零回転を経て正回転まで刈取搬送用静油圧式無段変速装置２１の第１出力軸３８の回転を刈取出力プーリー４５に伝達可能であるが、ワンウェイクラッチ８０を設けているので、ワンウェイクラッチ８０によって刈取部４に逆回転が伝達されない。
請求項３記載の発明では、前記エンジン２２の出力軸と前記中間軸２９の間にクラッチ４４を設け、前記中間出力軸４１から脱穀装置２の唐箕４２を連動する構成としたコンバインとしたものである。
請求項４記載の発明では、前記エンジン２２の外側には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の外側にはラジエーター８９を設け、該ラジエーター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、ラジエーターカバー９０の幅方向に往復移動自在に設けたコンバインとしたものである。 According to the first aspect of the present invention, the cutting unit 4 is provided in front of the traveling device 3 capable of continuously changing the traveling speed by the hydrostatic continuously variable transmission 12 for traveling, and the threshing device 2 is disposed above the traveling device 3. The cutting unit 4 is driven to shift by a hydrostatic continuously variable transmission 21 for harvesting and conveying in synchronization with the traveling speed of the traveling device 3, and the output shaft of the hydrostatic continuously variable transmission 21 for harvesting and conveying is provided. A cutting planetary gear mechanism 70 is provided between the first output shaft 38 and the cutting output pulley 45. The cutting planetary gear mechanism 70 rotatably supports the planetary gear 73 on a carrier 72 and is annular. provided gear 77 integrally engaging the gear 78 mounted on the input shaft 37 driven by the ring gear 77 from the engine 22, engaging the sun gear 74 attached to the front Symbol first output shaft 38 to the planetary gear 73, the The planetary gear 73 is Output and configured to engage the pulley 45 the output shaft of 45A to the fixed input gear 76 reaper equipped with comprises a reaper culms supply transport device 10 supplies culms the threshing chamber threshing apparatus 2 which reaped by 4 preparative The front supply / conveyance device 11 is provided on the conveyance start end side of the cereal supply / conveyance device 10, and the driving force of the engine 22 is input to the gear case 50 via the intermediate shaft 29. A threshing transmission shaft 33 that interlocks the handling cylinder 34 and the cereal supply and transport device 10 are interlocked from a portion between the shaft 29 and the input shaft 37 that is the input shaft of the hydrostatic continuously variable transmission 21 for harvesting and conveying. The intermediate output shaft 41 is configured to be driven at a constant speed, and from the first output shaft 38 via the planetary gear mechanism 70 for cutting, the cutting output shaft 45A that interlocks with the cutting unit 4 and the front supply / conveyance device 11. The A second output shaft 40 for movement, which has a structure with the combined driving at a speed synchronized to the vehicle speed, the traveling hydrostatic continuously variable transmission 12 to shift the constant rotation of the engine 22 steplessly The rotation that is transmitted to the traveling device 3 and travels to the cutting device 4 in synchronization with the traveling speed of the traveling device 3 is also shifted.
Further, the hydrostatic continuously variable transmission 21 for harvesting and conveying can drive the harvesting unit 4 independently of the hydrostatic continuously variable transmission 12 for traveling. When actuated, the cutting unit 4 is driven.
In this case, when the rotational speed output from the first output shaft 38 that is the output shaft of the chopping and conveying hydrostatic continuously variable transmission 21 is low, the hydraulic pump (not shown) for chopping and conveying hydrostatic continuously variable transmission. Since the amount of oil supplied to the hydraulic motor (not shown) of the device 21 is small, the rotational speed of the first output shaft 38 is not constant and unstable, and the rotational torque transmitted by the first output shaft 38 is also low. If the load of the cutting unit 4 is large, the cereals may be bitten, or in the worst case, the cutting unit 4 may stop even though the machine is running. Since the rotation of the step transmission 21 is transmitted to the cutting unit 4 via the cutting planetary gear mechanism 70, the cutting planetary gear mechanism 70 is configured such that when the rotation speed of the first output shaft 38 becomes equal to or higher than a predetermined rotation speed, Rotation output to the cutting output pulley 45, and the cutting unit 4 rotates at a low speed Stable and can be performed by the cutting work.
In a second aspect of the present invention, a one-way clutch 80 is provided in a transmission system path from the harvesting output pulley 45 to the harvesting unit 4 and the first output shaft 38 is rotated at a predetermined speed. When the rotation of 45A is stopped and the first output shaft 38 is rotated at a speed higher than a predetermined speed, the cutting output shaft 45A is rotated forward, and when the first output shaft 38 is rotated at a speed lower than the predetermined speed. The harvesting output shaft 45A is a combine that is configured to reversely rotate. The harvesting planetary gear mechanism 70 is a first output shaft of the hydrostatic continuously variable transmission 21 for harvesting conveyance from reverse rotation to zero rotation and forward rotation. Although the rotation of 38 can be transmitted to the cutting output pulley 45, since the one-way clutch 80 is provided, the reverse rotation is not transmitted to the cutting unit 4 by the one-way clutch 80.
In the invention according to claim 3, the clutch 44 is provided between the output shaft of the engine 22 and the intermediate shaft 29, and the combine is configured to interlock the Karatsu 42 of the threshing device 2 from the intermediate output shaft 41. is there.
According to a fourth aspect of the present invention, an engine cooling fan 88 is provided outside the engine 22, a radiator 89 is provided outside the engine cooling fan 88, and a dustproof net 92 is provided outside the radiator 89. A radiator cover 90 is provided, and a vertically long wind shielding plate 93 having a predetermined width is provided inside the dust-proof net 92 so as to be reciprocally movable in the width direction of the radiator cover 90.

請求項１記載の発明では、刈取用遊星歯車機構７０が、刈取出力プーリー４５に回転出力する際に、刈取搬送用静油圧式無段変速装置２１の出力軸である第１出力軸３８の回転数を充分な回転数に上昇させてから刈取部４へ伝達するので、刈取部４の低速回転での刈取作業が安定し、刈取作業を円滑に行うことができる。
請求項２記載の発明では、上記請求項１記載の発明の効果に加え、ワンウェイクラッチ８０が刈取部４への逆回転の伝達を防止するので、刈取搬送用静油圧式無段変速装置２１の低速駆動時に刈取出力軸４５Ａが逆転する状態が発生しても、刈取部４の破損を防止することができる。
また、刈取搬送用静油圧式無段変速装置２１を変速制御する場合には、この制御を簡素化することができる。
請求項３記載の発明では、上記請求項２記載の発明の効果に加え、穀稈供給搬送装置１０を連動する中間出力軸４１から脱穀装置２の唐箕４２を連動することができる。
請求項４記載の発明では、上記請求項３記載の発明の効果に加え、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。また、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。 According to the first aspect of the present invention, when the cutting planetary gear mechanism 70 rotates and outputs to the cutting output pulley 45, the rotation of the first output shaft 38 that is the output shaft of the cutting and conveying hydrostatic continuously variable transmission 21 is achieved. Since the number is increased to a sufficient number of revolutions and then transmitted to the mowing unit 4, the mowing operation at the low speed rotation of the mowing unit 4 is stabilized and the mowing operation can be performed smoothly.
In the second aspect of the invention, in addition to the effect of the first aspect of the invention, the one-way clutch 80 prevents the reverse rotation from being transmitted to the cutting unit 4. Even if the state where the cutting output shaft 45 </ b> A reverses during low-speed driving occurs, the cutting unit 4 can be prevented from being damaged.
In addition, this control can be simplified when shifting control is performed on the harvesting and conveying hydrostatic continuously variable transmission 21.
In the invention described in claim 3, in addition to the effect of the invention described in claim 2 above, it is possible to interlock the Karatsu 42 of the threshing apparatus 2 from the intermediate output shaft 41 interlocking with the grain supply / conveyance apparatus 10.
In the invention according to claim 4, in addition to the effect of the invention according to claim 3, the wind shielding plate 93 temporarily adheres to the dust-proof net 92 by blocking the suction air of the engine cooling fan 88. The adhesive force of a part of is reduced and dropped. Further, a suction air having a stronger suction force 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, and the dust-proof net 92 is put together with the edge of the wind-shielding plate 93. The clogging of the dust-proof net 92 can be removed by moving the deposit.

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。
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である。
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。 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.
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 transport device.
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 cereal 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。
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。
刈取搬送専用の刈取搬送用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 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).
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.
Synchronization with the running speed by the chopping and conveying hydrostatic continuously variable transmission 21 dedicated to chopping and conveying is achieved by driving the threshing device 2 and the cereal supply and conveying device 10 with constant driving rotation from the engine 22 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（第２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 (second output shaft), 41 culms supply conveyance intermediate output shaft, 41A supply conveyor pulley, 42 is winnowing fan, 43 driving gear of culms supply transport device 10, 44 reaper threshing clutch, Reference numeral 45 denotes a cutting intermediate output pulley (cutting output pulley) provided on the cutting intermediate output shaft 39, 46 denotes a cutting intermediate input pulley, 47 denotes a belt wound around the cutting output pulley 45 and the cutting intermediate input pulley 46, and 50 denotes a cutting The gear case is provided with an intermediate gear 36, a cutting intermediate output shaft 39, and the like, and a cutting and conveying hydrostatic continuously variable transmission 21 is provided on the control unit 6 side 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）。
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。
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。 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). .
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.
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。
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。 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.
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 </ b> A for adjusting the rotational speed separately, and the intermediate gear 54 </ b> 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。
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。 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 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.

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。 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（第１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。
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。
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。 Therefore, a cutting planetary gear mechanism 70 is provided between the cutting HST output shaft (first output shaft) 38 of the cutting and conveying hydrostatic continuously variable transmission 21 and the cutting output pulley 45, and the cutting planetary gear mechanism 70 is provided. The gear 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.
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.
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。
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。
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。 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.
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 </ b> A that rotates integrally with the cutting HST output shaft 38.
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。
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。 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.
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。
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。
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。 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.
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.
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。
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。 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.
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。
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８４を噛み合わせる。中間軸８３には別途歯車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。
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, 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.
That is, a separate synchro gear 82 is provided on the cutting intermediate output shaft 45A, and the gear 84 of the intermediate shaft 83 is engaged with the synchro gear 82. The intermediate shaft 83 is separately provided with a gear 84A, and the rotation of the gear 84A is transmitted to the gear 85 of the output shaft 40 for synchronizing the synchronization, and the same rotation as the rotation transmitted to the cutting portion 4 by the cutting planetary gear mechanism 70 is performed on the front side for synchronization. This is transmitted to the supply conveyance device 11.
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。
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, 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.
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）。
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。 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).
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。
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。
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。
そのため、遮風プレート９３の移動を円滑にする。 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.
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.
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).
Therefore, the movement of the wind shielding plate 93 is made smooth.

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。
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）。
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。
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。 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.
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).
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.
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.

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）。
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。 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).
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。
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。
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。 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.
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.
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.

（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。
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。
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。 (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.
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.
That is, when the main transmission lever 13 is tilted, a constant rotation of the engine 22 is steplessly 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. Thus, the rotation transmitted to the cutting unit 4 and the front supply / conveyor 11 for synchronization is also changed.

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。
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。 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.
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。
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 the present application, a harvesting planetary gear mechanism 70 is provided between the harvesting HST output shaft 38 of the hydrostatic continuously variable transmission 21 for harvesting conveyance and the harvesting intermediate output pulley and the harvesting output pulley 45. The mowing planetary gear mechanism 70 is configured to rotate and output the mowing HST output shaft 38 to the mowing output pulley 45 when the rotational speed of the mowing HST output shaft 38 becomes equal to or higher than a predetermined rotational speed. A driving rotation having a sufficient rotational torque can be output to the cutting output pulley 45.
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。
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。
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。 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.
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.
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。
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。 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.
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。
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, 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.
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。
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。
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。 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.
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.
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。
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。 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. .
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−ム、２…脱穀装置、３…走行装置、４…刈取部、５…グレンタンク、１０…穀稈供給搬送装置、１１…シンクロ用前側供給搬送装置、１２…走行用静油圧式無段変速装置、１３…主変速レバー、１４…油圧ポンプ、１５…ポンプ斜板、１６…油圧モータ、１７…モータ斜板、１８…ミッションケース、２１…刈取搬送用静油圧式無段変速装置、２２…エンジン、２６…入力プーリー、２７…ミッションケース、２８…中間プーリー、２９…中間軸、３０…中間歯車、３１…中間伝動軸、３２…脱穀用傘歯車、３３…脱穀伝動軸、３４…扱胴、３５…処理胴、３６…刈取用中間歯車、３７…刈取ＨＳＴ入力軸（入力軸）、３８…刈取ＨＳＴ出力軸（出力軸）、３９…刈取用中間出力軸、４０…搬送シンクロ用出力軸、４１…穀稈供給搬送中間出力軸、４２…唐箕、４３…駆動歯車、４４…刈取脱穀クラッチ、４５…刈取中間出力プーリー（刈取出力プーリー）、４５Ａ…刈取出力軸、４６…刈取中間入力プーリー、４７…ベルト、５０…ギヤケース、５２…モータ出力軸、５３…出力歯車、５５…入力歯車、５４…入力軸、５６…サイドクラッチ軸、５７…受動歯車、５８…サイドクラッチ、６０…遊星歯車機構、６１…駆動軸、６２…キャリア、６３…遊星歯車、６４…遊星歯車、６５…中間遊星歯車、６６…ブレーキ、６７…駆動歯車、７０…刈取用遊星歯車機構、７２…キャリア、７３…遊星歯車、７４…サンギヤ、７４Ａ…ボス、７５…出力遊星歯車、７６…入力歯車、７７…環状歯車、７８…ギヤ、７９Ａ…回転体、７９Ｂ…回転検出手段、８０…ワンウェイクラッチ、８２…シンクロ用歯車、８３…中間軸、８４…歯車、８５…歯車、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、９１…枠体、９２…防塵ネット、９３…遮風プレート、９４…ガイド機構、９５…案内レール、９６…案内体、９８…軸、１００…長孔、１０１…案内体、１０２…バネ、１０３…伝動軸、１０４…移動部材、１０５…塵埃吸引口、１１０…操作パネル、１１１…レバー、１１２…操作溝、１１３…閉塞部材、１１４…プレート、１１５…溝、１１６…ブラシ。 DESCRIPTION OF SYMBOLS 1 ... Airframe frame, 2 ... Threshing device, 3 ... Traveling device, 4 ... Cutting part, 5 ... Glen tank, 10 ... Grain supply / conveyance device, 11 ... Front supply conveyance device for synchro, 12 ... Hydrostatic pressure for traveling Continuously variable transmission, 13 ... main transmission lever, 14 ... hydraulic pump, 15 ... pump swash plate, 16 ... hydraulic motor, 17 ... motor swash plate, 18 ... mission case, 21 ... hydrostatic continuously variable transmission for cutting and conveying Equipment: 22 ... Engine, 26 ... Input pulley, 27 ... Transmission case, 28 ... Intermediate pulley, 29 ... Intermediate shaft, 30 ... Intermediate gear, 31 ... Intermediate transmission shaft, 32 ... Threshing bevel gear, 33 ... Threshing transmission shaft, 34 ... Handling cylinder, 35 ... Processing cylinder, 36 ... Cutting intermediate gear, 37 ... Cutting HST input shaft (input shaft), 38 ... Cutting HST output shaft (output shaft), 39 ... Intermediate output shaft for cutting, 40 ... Conveying Output shaft for synchro, 41 ... Feeding intermediate output shaft, 42 ... Kara, 43 ... Drive gear, 44 ... Cutting threshing clutch, 45 ... Cutting intermediate output pulley (cutting output pulley), 45A ... Cutting output shaft, 46 ... Cutting intermediate input pulley, 47 ... Belt, DESCRIPTION OF SYMBOLS 50 ... Gear case, 52 ... Motor output shaft, 53 ... Output gear, 55 ... Input gear, 54 ... Input shaft, 56 ... Side clutch shaft, 57 ... Passive gear, 58 ... Side clutch, 60 ... Planetary gear mechanism, 61 ... Drive Shaft 62 ... Carrier 63 ... Planetary gear 64 ... Planetary gear 65 ... Intermediate planetary gear 66 ... Brake 67 ... Drive gear 70 ... Planetary gear mechanism for harvesting 72 ... Carrier 73 ... Planetary gear 74 ... Sun gear, 74A ... boss, 75 ... output planetary gear, 76 ... input gear, 77 ... annular gear, 78 ... gear, 79A ... rotor, 79B ... rotation detecting means, 80 ... one way Clutch, 82 ... Synchro gear, 83 ... Intermediate shaft, 84 ... Gear, 85 ... Gear, 86 ... Driver's seat, 87 ... Engine room, 88 ... Engine cooling fan, 89 ... Radiator, 90 ... Radiator cover, 91 ... Frame Body, 92 ... Dust-proof net, 93 ... Wind shield plate, 94 ... Guide mechanism, 95 ... Guide rail, 96 ... Guide body, 98 ... Shaft, 100 ... Long hole, 101 ... Guide body, 102 ... Spring, 103 ... Transmission shaft , 104, a moving member, 105, a dust suction port, 110, an operation panel, 111, a lever, 112, an operation groove, 113, a closing member, 114, a plate, 115, a groove, 116, a brush.

Claims

走行用静油圧式無段変速装置（１２）により走行速度を無段階に変速可能な走行装置（３）の前方に刈取部（４）を設け、走行装置（３）の上方には脱穀装置（２）を設け、前記刈取部（４）は走行装置（３）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（２１）により変速駆動する構成とし、刈取搬送用静油圧式無段変速装置（２１）の出力軸である第１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（７０）を設け、刈取用遊星歯車機構（７０）は、キャリア（７２）に遊星歯車（７３）を回転自在に軸支すると共に環状歯車（７７）を一体に設け、環状歯車（７７）にエンジン（２２）から駆動される入力軸（３７）に取付けたギヤ（７８）を噛み合わせ、前記第１出力軸（３８）に取付けたサンギヤ（７４）を遊星歯車（７３）に噛み合わせ、該遊星歯車（７３）を前記刈取出力プーリー（４５）を備えた刈取出力軸（４５Ａ）に固定の入力歯車（７６）に噛み合わせる構成とし、刈取部（４）によって刈り取られた穀稈を脱穀装置（２）の扱室に供給する穀稈供給搬送装置（１０）を備え、該穀稈供給搬送装置（１０）の搬送始端側に前側供給搬送装置（１１）を設け、エンジン（２２）の駆動力が中間軸（２９）を介してギヤケース（５０）に入力する構成とし、該ギヤケース（５０）内の伝動機構における中間軸（２９）と刈取搬送用静油圧式無段変速装置（２１）の入力軸である前記入力軸（３７）との間の部位から、扱胴（３４）を連動する脱穀伝動軸（３３）と、穀稈供給搬送装置（１０）を連動する中間出力軸（４１）を、定速で駆動する構成とし、前記第１出力軸（３８）から、刈取用遊星歯車機構（７０）を介して、刈取部（４）を連動する刈取出力軸（４５Ａ）と、前側供給搬送装置（１１）を連動する第２出力軸（４０）を、車速に同調した速度で駆動する構成としたコンバイン。 A cutting part (4) is provided in front of the traveling device (3) capable of continuously changing the traveling speed by the hydrostatic continuously variable transmission (12) for traveling, and a threshing device (3) is disposed above the traveling device (3). 2), and the cutting part (4) is driven by a hydrostatic continuously variable transmission (21) for cutting and conveying in synchronism with the traveling speed of the traveling device (3). A cutting planetary gear mechanism (70) is provided between the first output shaft (38), which is the output shaft of the continuously variable transmission (21), and the cutting output pulley (45), and the cutting planetary gear mechanism (70) is provided. ) Rotatably supports the planetary gear (73) on the carrier (72) and is provided with the annular gear (77) integrally, and the input shaft (37) driven from the engine (22) to the annular gear (77). engaging a gear (78) attached to and mounted on the front Symbol first output shaft (38) Engaging Ngiya (74) to the planetary gear (73), and configured to engage the planetary gear (73) cutting the output shaft with the cutting output pulley (45) a fixed input gear (45A) (76) , Provided with a cereal supply transport device (10) for supplying cereals harvested by the mowing unit (4) to the handling room of the threshing device (2); A supply conveyance device (11) is provided, and the driving force of the engine (22) is input to the gear case (50) via the intermediate shaft (29), and the intermediate shaft (29) in the transmission mechanism in the gear case (50). And a threshing transmission shaft (33) interlocking with a handling cylinder (34) from a portion between the input shaft (37) which is an input shaft of the hydrostatic continuously variable transmission (21) for cutting and conveying, Intermediate output shaft (4 ) At a constant speed, and from the first output shaft (38) via the planetary gear mechanism (70) for cutting, the cutting output shaft (45A) interlocking with the cutting portion (4), and the front side A combine configured to drive the second output shaft (40) interlocking with the supply / conveyance device (11) at a speed synchronized with the vehicle speed .

請求項１記載の発明において、前記刈取出力プーリー（４５）から刈取部（４）に至る伝動系路中にワンウェイクラッチ（８０）を設け、前記第１出力軸（３８）を所定の速度で回転させている状態で刈取出力軸（４５Ａ）の回転が停止し、該第１出力軸（３８）を所定の速度よりも高速で回転させると刈取出力軸（４５Ａ）が正転し、該第１出力軸（３８）を所定の速度よりも低速で回転させると刈取出力軸（４５Ａ）が逆転する構成としたコンバイン。 The invention according to claim 1, wherein a one-way clutch (80) is provided in a transmission system path from the cutting output pulley (45) to the cutting unit (4), and the first output shaft (38) is rotated at a predetermined speed. When the rotation of the cutting output shaft (45A) is stopped while the first output shaft (38) is rotated at a speed higher than a predetermined speed, the cutting output shaft (45A) is rotated in the forward direction. A combine configured to reverse the cutting output shaft (45A) when the output shaft (38) is rotated at a speed lower than a predetermined speed .

請求項２記載の発明において、前記エンジン（２２）の出力軸と前記中間軸（２９）の間にクラッチ（４４）を設け、前記中間出力軸（４１）から脱穀装置２の唐箕（４２）を連動する構成としたコンバイン。In the invention of claim 2, a clutch (44) is provided between the output shaft of the engine (22) and the intermediate shaft (29), and the tang (42) of the threshing device 2 is connected to the intermediate output shaft (41). Combine that works in conjunction.

請求項３記載の発明において、前記エンジン（２２）の外側には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）の外側にはラジエーター（８９）を設け、該ラジエーター（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、ラジエーターカバー（９０）の幅方向に往復移動自在に設けたコンバイン。In the invention of claim 3, an engine cooling fan (88) is provided outside the engine (22), a radiator (89) is provided outside the engine cooling fan (88), and the radiator (89) ) Is provided with a radiator cover (90) having a dustproof net (92), and a vertically long wind shield plate (93) having a predetermined width is provided on the inside of the dustproof net (92). ) Combined with the reciprocating movement in the width direction.