JP5035328B2

JP5035328B2 - Combine

Info

Publication number: JP5035328B2
Application number: JP2009271939A
Authority: JP
Inventors: 靖藤田
Original assignee: Iseki and Co Ltd
Current assignee: Iseki and Co Ltd
Priority date: 2009-11-30
Filing date: 2009-11-30
Publication date: 2012-09-26
Anticipated expiration: 2029-11-30
Also published as: CN102077729B; JP2011110020A; TWI376192B; TW201117709A; KR101072853B1; KR20110060770A; CN102077729A

Description

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

従来より、走行用静油圧式無段変速装置で駆動される走行装置の上側に、脱穀装置とグレンタンクを左右に並べて設け、グレンタンクの前側に操縦部を設け、操縦部および脱穀装置の前側に刈取装置を設け、走行用静油圧式無段変速装置の油圧ポンプの斜板であるポンプ斜板の傾斜角度を変更する変速レバーを設けたコンバインが知られている。 Conventionally, a threshing device and a Glen tank are provided side by side on the upper side of a traveling device driven by a hydrostatic continuously variable transmission for traveling, a control unit is provided on the front side of the Glen tank, and the front side of the control unit and the threshing device There is known a combine that is provided with a cutting device and a shift lever for changing the inclination angle of a pump swash plate, which is a swash plate of a hydraulic pump of a hydrostatic continuously variable transmission for traveling.

そして、特許文献１に開示されているように、走行用静油圧式無段変速装置で駆動される走行装置を有する作業車両において、変速レバーを最高速位置に操作した場合の最高車速を設定する最高車速設定ダイヤルを設ける技術が知られている。 And as disclosed in Patent Document 1, in a work vehicle having a traveling device driven by a hydrostatic continuously variable transmission for traveling, the maximum vehicle speed when the shift lever is operated to the maximum speed position is set. A technique for providing a maximum vehicle speed setting dial is known.

特開２００７−２３０５１８号公報JP 2007-230518 A

しかしながら、高速での圃場間移動と低速での刈取作業とを反復するコンバインでは、圃場間移動時を基準として最高車速を設定すると、刈取作業時に車速が増速しすぎ、圃場面の凹凸に対して刈取装置の高さ調節が間に合わずに刈取装置が圃場面に突っ込んで破損したり、倒伏した穀稈を引起装置で引き起こせずに刈り残しを生じたり、刈取装置を穀稈列に沿わせて操向する操作が困難となる等の問題が起こる。 However, in a combine that repeats high-speed movement between fields and low-speed cutting operations, if the maximum vehicle speed is set based on the movement between the fields, the vehicle speed increases excessively during cutting operations, and The height of the reaping device cannot be adjusted in time, and the reaping device plunges into the field and breaks, or the fallen cereal is not caused by the pulling device and the reaping is left behind. Problems such as difficulty in maneuvering.

一方、刈取作業時を基準として最高車速を設定すると、路上走行に適した高速走行ができず、圃場間移動に時間を要して作業能率が低下してしまう。 On the other hand, if the maximum vehicle speed is set with reference to the time of cutting work, high-speed traveling suitable for road traveling cannot be performed, and it takes time to move between fields, resulting in reduced work efficiency.

本発明は、上述の課題を解決するために、次のような技術的手段を講じる。
即ち、請求項１記載の発明は、走行用静油圧式無段変速装置（１２）で駆動される走行装置（３）の上側に脱穀装置（２）とグレンタンク（５）を左右に並べて設け、該グレンタンク（５）の前側に操縦部（６）を設け、該操縦部（６）および脱穀装置（２）の前側に刈取装置（４）を設け、前記走行用静油圧式無段変速装置（１２）の油圧ポンプ（１４）の斜板であるポンプ斜板（１５）の傾斜角度を変更する変速レバー（１３）を設けたコンバインにおいて、前記走行用静油圧式無段変速装置（１２）の油圧モータ（１６）の斜板であるモータ斜板（１７）の傾斜角度を低速走行側と高速走行側とに切替可能な構成とし、前記変速レバー（１３）を最高速位置に操作した場合の最高車速を変更設定する最高車速設定ダイヤル（５１）を設け、該最高車速設定ダイヤル（５１）による最高車速の設定を、前記モータ斜板（１７）の傾斜角度が低速走行側に切り替えられた状態でのみ有効とし、該最高車速設定ダイヤル（５１）で最高車速を設定した後にモータ斜板（１７）の傾斜角度が低速走行側から高速走行側に切り替えられた場合には、前記最高車速設定ダイヤル（５１）による最高車速の設定を無効にする構成としたことを特徴とするコンバインとしたものである。 In order to solve the above-mentioned problems, the present invention takes the following technical means.
That is, the invention described in claim 1 is provided with the threshing device (2) and the grain tank (5) arranged side by side on the upper side of the traveling device (3) driven by the hydrostatic continuously variable transmission (12) for traveling. The front part of the Glen tank (5) is provided with a control part (6), the control part (6) and the threshing device (2) are provided with a cutting device (4), and the hydrostatic continuously variable transmission for traveling is provided. In a combine provided with a transmission lever (13) for changing the inclination angle of a pump swash plate (15) which is a swash plate of a hydraulic pump (14) of the device (12), the hydrostatic continuously variable transmission (12 The inclination angle of the motor swash plate (17), which is the swash plate of the hydraulic motor (16), can be switched between the low speed traveling side and the high speed traveling side, and the shift lever (13) is operated to the maximum speed position. Set the maximum vehicle speed setting dial (51) to change the maximum vehicle speed The maximum vehicle speed setting by the maximum vehicle speed setting dial (51) is valid only when the inclination angle of the motor swash plate (17) is switched to the low-speed traveling side, and the maximum vehicle speed setting dial (51) is the highest. When the inclination angle of the motor swash plate (17) is switched from the low speed traveling side to the high speed traveling side after the vehicle speed is set, the maximum vehicle speed setting by the maximum vehicle speed setting dial (51) is invalidated. It is a combine characterized by that.

請求項２記載の発明は、前記刈取装置（４）を駆動する刈取搬送用静油圧式無段変速装置（２１）内の第２油圧ポンプ（８９）と第２油圧モータ（９０）の間に閉回路を形成し、該閉回路に、前記走行用静油圧式無段変速装置（１２）のチャージポンプ（８５）から送られる作動油を分流弁（９２Ａ）で分流して供給する構成とした請求項１記載のコンバインとしたものである。
請求項３記載の発明は、前記第２油圧ポンプ（８９）と第２油圧モータ（９０）の間に形成した閉回路における高圧側の油路と低圧側の油路とを短絡させる短絡油路を設け、該短絡油路にチェックバルブ（９１）を設けて、前記第２油圧ポンプ（８９）からの作動油の吐き出し方向が逆転した場合に、この作動油が第２油圧モータ（９０）側へ送油されることを防止する構成とした請求項２記載のコンバインとしたものである。
請求項４記載の発明は、刈取クラッチまたは脱穀クラッチが接続操作された場合に、前記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）の傾斜角度が高速走行側から低速走行側に自動的に切り替わる構成とした請求項１または請求項２または請求項３記載のコンバインとしたものである。 According to a second aspect of the present invention, there is provided between the second hydraulic pump (89) and the second hydraulic motor (90) in the hydrostatic continuously variable transmission (21) for cutting and conveying that drives the cutting device (4). A closed circuit is formed, and hydraulic oil sent from the charge pump (85) of the traveling hydrostatic continuously variable transmission (12) is divided and supplied to the closed circuit by the diversion valve (92A). The combine according to claim 1.
According to a third aspect of the present invention, there is provided a short-circuit oil passage for short-circuiting a high-pressure side oil passage and a low-pressure side oil passage in a closed circuit formed between the second hydraulic pump (89) and the second hydraulic motor (90). When the check valve (91) is provided in the short-circuit oil passage and the discharge direction of the hydraulic oil from the second hydraulic pump (89) is reversed, the hydraulic oil is moved to the second hydraulic motor (90) side. The combine according to claim 2, which is configured to prevent oil from being fed to the vehicle.
According to a fourth aspect of the present invention, the inclination angle of the motor swash plate (17) of the hydraulic motor (16) of the traveling hydrostatic continuously variable transmission (12) when the reaping clutch or the threshing clutch is connected. The combine according to claim 1, claim 2, or claim 3, which is configured to automatically switch from the high speed travel side to the low speed travel side.

請求項１記載の発明によると、最高車速設定ダイヤル（５１）の操作により、走行用静油圧式無段変速装置（１２）の油圧モータ（１６）の斜板であるモータ斜板（１７）の傾斜角度を低速走行側に切り替えた状態で、変速レバー（１３）を最高速位置に操作した場合の最高車速を変更設定するので、車速の変速範囲を圃場条件や作物条件に適した範囲に制限でき、刈取作業におけるコンバインの操作性および刈取作業の能率を高めることができる。 According to the first aspect of the present invention, by operating the maximum vehicle speed setting dial (51), the motor swash plate (17), which is the swash plate of the hydraulic motor (16) of the hydrostatic continuously variable transmission (12) for traveling. Since the maximum vehicle speed is changed and set when the shift lever (13) is operated to the maximum speed position with the tilt angle switched to the low speed traveling side, the speed range of the vehicle speed is limited to a range suitable for the field conditions and crop conditions. Therefore, the operability of the combine in the harvesting work and the efficiency of the harvesting work can be improved.

そして、圃場間移動のために走行用静油圧式無段変速装置（１２）の油圧モータ（１６）のモータ斜板（１７）の傾斜角度を高速走行側に切り替えると、上述の刈取作業時の最高車速の設定を無効にするので、この最高車速の設定を手動で解除する操作を省略でき、高速での圃場間移動と低速での刈取作業とを反復するコンバインの操作性および刈取作業の能率を更に高めることができる。
請求項２記載の発明によると、上記請求項１記載の発明の効果を奏するうえに、走行用静油圧式無段変速装置（１２）と刈取搬送用静油圧式無段変速装置（２１）とでチャージポンプ（８５）を共用することで、製造コストを低減して安価に提供することができる。
請求項３記載の発明によると、上記請求項２記載の発明の効果を奏するうえに、刈取装置（４）の逆転駆動を防止して、刈取装置（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）から刈取装置（４）への伝動経路中にワンウェイクラッチを設ける必要が無く、製造コストを低減して安価に提供することができる。
請求項４記載の発明によると、上記請求項１または請求項２または請求項３記載の発明の効果を奏するうえに、刈取クラッチまたは脱穀クラッチが接続操作された場合に、走行用静油圧式無段変速装置（１２）の油圧モータ（１６）のモータ斜板（１７）の傾斜角度が高速走行側から低速走行側に自動的に切り変わることで、刈取脱穀作業に適した低速走行状態とすることができる。 When the inclination angle of the motor swash plate (17) of the hydraulic motor (16) of the hydrostatic continuously variable transmission for traveling (12) is switched to the high-speed traveling side for movement between fields, the above-mentioned cutting operation is performed. Since the setting of the maximum vehicle speed is invalidated, the operation of manually canceling this maximum vehicle speed setting can be omitted, and the operability of the combine that repeats the movement between fields at high speed and the cutting operation at low speed and the efficiency of the cutting operation Can be further increased.
According to invention of Claim 2, in addition to having the effect of the invention of Claim 1, the hydrostatic continuously variable transmission (12) for traveling and the hydrostatic continuously variable transmission (21) for harvesting and conveying By sharing the charge pump (85), the manufacturing cost can be reduced and provided at a low cost.
According to the invention described in claim 3, in addition to the effects of the invention described in claim 2, it is possible to prevent the reaping device (4) from being reversely driven and to prevent the reaping device (4) from being damaged. Further, it is not necessary to provide a one-way clutch in the transmission path from the hydrostatic continuously variable transmission (21) for harvesting conveyance to the harvesting device (4), and the production cost can be reduced and provided at a low cost.
According to the invention described in claim 4, in addition to the effects of the invention described in claim 1, 2 or 3 above, when the reaping clutch or the threshing clutch is connected and operated, The inclination angle of the motor swash plate (17) of the hydraulic motor (16) of the step transmission (12) is automatically switched from the high-speed traveling side to the low-speed traveling side, so that the low-speed traveling state suitable for the cutting and threshing operation is achieved. be able to.

コンバインの側面図Combine side view コンバインの伝動機構の説明図Explanatory diagram of combine transmission mechanism ミッションケース内の伝動機構の説明図Illustration of the transmission mechanism in the mission case 走行用静油圧式無段変速装置および刈取搬送用静油圧式無段変速装置の油圧回路Hydraulic circuit for travel hydrostatic continuously variable transmission and hydrostatic continuously variable transmission for cutting and conveying ブロック回路図Block circuit diagram 最高車速設定ダイヤルの配置を示す説明図Explanatory drawing showing the layout of the maximum vehicle speed setting dial 車速と変速レバー操作位置の関係を示すグラフGraph showing the relationship between vehicle speed and shift lever operation position 車速と刈取駆動速度の関係を示すグラフGraph showing the relationship between vehicle speed and cutting drive speed

本発明の実施の形態を、図面に基づいて説明する。
図１にコンバインの機体構成を示す。
このコンバインは、機体フレーム１の下側にクローラ３Ａを備えた走行装置３を設け、機体フレ−ム１の上部左側に脱穀装置２を搭載し、この脱穀装置２の右側に排出オーガ７を備えたグレンタンク５を搭載し、このグレンタンク５の前側に操縦部６を設け、この操縦部６と脱穀装置２の前側に刈取装置４を設けた構成とする。 Embodiments of the present invention will be described with reference to the drawings.
Fig. 1 shows the fuselage structure.
This combine is provided with a traveling device 3 provided with a crawler 3 A on the lower side of the machine frame 1, a threshing device 2 is mounted on the upper left side of the machine frame 1, and a discharge auger 7 is provided on the right side of the threshing device 2. The grain tank 5 is mounted, a control unit 6 is provided on the front side of the grain tank 5, and a reaping device 4 is provided on the front side of the control unit 6 and the threshing device 2.

前記刈取装置４は、前側から、分草体８、引起装置８ａ、刈刃９、搬送装置９Ａを備えた構成とする。
前記脱穀装置２の上部外側には、刈取装置４側の搬送装置９Ａから搬送されてくる穀稈を脱穀室に供給するフィードチェン１０を設け、このフィードチェン１０の上側には、フィードチェン１０に対向する挟扼杆（図示省略）を設ける。 The cutting device 4 includes a weeding body 8, a pulling device 8a, a cutting blade 9, and a conveying device 9A from the front side.
A feed chain 10 is provided outside the upper part of the threshing device 2 to supply cereals conveyed from the conveying device 9A on the reaping device 4 side to the threshing chamber. Opposing pinches (not shown) are provided.

また、このフィードチェン１０の始端部内側には、搬送装置９Ａからフィードチェン１０へ穀稈を受け渡す補助チェン１１を設ける。
図２にコンバインの伝動機構を示す。 In addition, an auxiliary chain 11 is provided on the inner side of the start end of the feed chain 10 so as to deliver the cereal to the feed chain 10 from the conveying device 9A.
FIG. 2 shows a combine transmission mechanism.

操縦部６の下部に搭載したエンジン２２の出力軸２２Ａに刈取脱穀用出力プーリー２５Ｂを固定し、この刈取脱穀用出力プーリー２５Ｂと、中間軸２９の一端に固定した中間プーリー２８に、刈取脱穀クラッチ４４を備えた伝動ベルト４４Ａを掛け回す。そして、中間軸２９の他端に固定した中間歯車３０とギヤケース５０内の中間伝動軸３１に固定した中間歯車３０ａを噛み合わせ、中間伝動軸３１の一端に固定した傘歯車３２と脱穀伝動軸３３の一端に固定した傘歯車３２Ａを噛み合わせる。更に、脱穀伝動軸３３の他端に固定した中間プーリー３３Ａからベルト伝動機構３３Ｂを介して、扱胴３４と処理胴３５を回転駆動する構成とする。 A harvesting and threshing output pulley 25B is fixed to the output shaft 22A of the engine 22 mounted on the lower part of the control unit 6, and the harvesting and threshing output pulley 25B and an intermediate pulley 28 fixed to one end of the intermediate shaft 29 are connected to the cutting and threshing clutch. The transmission belt 44 A provided with 44 is hung around. Then, the intermediate gear 30 fixed to the other end of the intermediate shaft 29 and the intermediate gear 30 a fixed to the intermediate transmission shaft 31 in the gear case 50 are meshed, and the bevel gear 32 fixed to one end of the intermediate transmission shaft 31 and the threshing transmission shaft 33. The bevel gear 32A fixed to one end of the gear is engaged. Furthermore, it is set as the structure which rotationally drives the handling cylinder 34 and the process cylinder 35 via the belt transmission mechanism 33B from the intermediate pulley 33A fixed to the other end of the threshing transmission shaft 33.

また、前記中間伝動軸３１の他端に固定した中間歯車３６と、中間出力軸４１の一端に固定した中間歯車３６Ａを噛み合わせ、該中間出力軸４１の他端部に固定した出力プーリー４１Ａから、ベルト伝動機構４１Ｂを介して、唐箕４２をはじめとする選別部４２Ｂと、フィードチェン１０の後部を掛け回したスプロケット４３を駆動する構成とする。 Further, the intermediate gear 36 fixed to the other end of the intermediate transmission shaft 31 and the intermediate gear 36A fixed to one end of the intermediate output shaft 41 are meshed, and an output pulley 41A fixed to the other end of the intermediate output shaft 41 is engaged. The sprocket 43 around the rear part of the feed chain 10 and the sorting part 42B including the Kara 42 are driven via the belt transmission mechanism 41B.

そして、前記ギヤケース５０の操縦部６側の面に刈取搬送用静油圧式無段変速装置２１を取り付け、該刈取搬送用静油圧式無段変速装置２１の入力軸３７に固定した入力ギヤ３７Ａを、前記中間歯車３６Ａに噛み合わせる。また、刈取搬送用静油圧式無段変速装置２１の出力軸３８とスプラインで接続される伝動軸３８Ａから、ギヤ伝動機構３８Ｂ，３８Ｃを介して、刈取出力プーリー４５を固定した刈取出力軸３９と、補助チェン１１を掛け回すスプロケット４０Ａを固定した出力軸４０を分岐伝動する構成とする。前記刈取出力プーリー４５と刈取装置４の入力軸４６Ａの外側端部に固定した刈取入力プーリー４６に伝動ベルト４７を掛け回す。 A hydrostatic continuously variable transmission 21 for harvesting and conveying is attached to the surface of the gear case 50 on the control unit 6 side, and an input gear 37A fixed to the input shaft 37 of the hydrostatic continuously variable transmission 21 for harvesting and conveying is provided. Mesh with the intermediate gear 36A. Further, a cutting output shaft 39 having a cutting output pulley 45 fixed thereto via a gear transmission mechanism 38B, 38C from a transmission shaft 38A connected to the output shaft 38 of the cutting and conveying hydrostatic continuously variable transmission 21 by a spline; The output shaft 40 to which the sprocket 40A around which the auxiliary chain 11 is hung is fixed is transmitted in a branched manner. A transmission belt 47 is wound around the cutting output pulley 45 and the cutting input pulley 46 fixed to the outer end of the input shaft 46A of the cutting device 4.

一方、前記エンジン２２の出力軸２２Ａに固定した走行用出力プーリー２５Ａと、走行用のミッションケース１８の上部に取り付けた走行用静油圧式無段変速装置１２の入力軸１２Ａに固定した入力プーリー２６に、伝動ベルト１２Ｂを掛け回す。 On the other hand, a traveling output pulley 25A fixed to the output shaft 22A of the engine 22 and an input pulley 26 fixed to the input shaft 12A of the traveling hydrostatic continuously variable transmission 12 attached to the top of the traveling mission case 18 are provided. Then, the transmission belt 12B is hung around.

図３にミッションケース１８内の伝動機構を示す。
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の出力で駆動される入力軸６５を設け、この入力軸６５に固定した出力歯車６６を、中間軸６６Ａに固定した中間ギヤ６６Ｂに噛み合わせる。そして、中間軸６６Ａに固定した中間ギヤ６６Ｃを、サイドクラッチ軸６７の中央部に固定した受動歯車６８に噛み合わせる。この受動歯車６８の左右両側には、左右のサイドクラッチ６９，６９を設ける。 FIG. 3 shows a transmission mechanism in the mission case 18.
An input shaft 65 driven by the output of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is provided on the upper part of the transmission case 18, and an output gear 66 fixed to the input shaft 65 is fixed to the intermediate shaft 66A. Mesh with the intermediate gear 66B. Then, the intermediate gear 66C fixed to the intermediate shaft 66A is meshed with the passive gear 68 fixed to the center portion of the side clutch shaft 67. Left and right side clutches 69 and 69 are provided on the left and right sides of the passive gear 68.

そして、前記受動歯車６８を伝動軸７１の中央部に固定した第二受動歯車７２に噛み合わせ、この第二受動歯車７２の左右両側には、左右の遊星歯車機構７０，７０を左右対称に設ける。この遊星歯車機構７０は、有効直径の異なる二つの歯部を備えた複数の遊星歯車７４を、円筒形状のキャリア７３の円周方向に、間隔をおいて夫々軸受し、この遊星歯車７４の小径歯部と中間遊星歯車７６を噛み合わせ、この中間遊星歯車７６と駆動軸７１に回転自在に軸受した出力歯車７５の小径歯部を噛み合わせ、前記遊星歯車７４の大径歯部を前記伝動軸７１に固定した太陽歯車７１Ａに噛み合わせた構成とする。また、前記キャリア７３とミッションケース１８の間には、キャリア７３の回転を制動する多板式のブレーキ７７を設ける。 The passive gear 68 is meshed with a second passive gear 72 fixed to the center of the transmission shaft 71, and left and right planetary gear mechanisms 70, 70 are provided symmetrically on the left and right sides of the second passive gear 72. . In this planetary gear mechanism 70, a plurality of planetary gears 74 having two tooth portions having different effective diameters are respectively bearing in the circumferential direction of the cylindrical carrier 73 at intervals, and the planetary gear 74 has a small diameter. The tooth portion and the intermediate planetary gear 76 are engaged with each other, the intermediate planetary gear 76 and the small-diameter tooth portion of the output gear 75 rotatably supported on the drive shaft 71 are engaged, and the large-diameter tooth portion of the planetary gear 74 is connected to the transmission shaft. The sun gear 71 A fixed to 71 is engaged. A multi-plate brake 77 that brakes the rotation of the carrier 73 is provided between the carrier 73 and the transmission case 18.

そして、前記出力歯車７５の大径歯部を、中間軸７５Ａに回転自在に軸受した中間歯車７５Ｂの大径歯部に噛み合わせ、この中間歯車７５Ｂの小径歯部を、減速軸７５Ｃの一端に固定した大径歯車７５Ｄに噛み合わせる。更に、前記減速軸７５Ｃの他端部に固定した小径歯車７５Ｅを、車軸７６Ｆの一端部に固定した車軸歯車７６Ｇに噛み合わせる。この車軸７６Ｆの他端部に固定した駆動スプロケット７６Ｈにクローラ３Ａの前部を掛け回して駆動する構成とする。７１Ｂは、前記駆動軸７１を制動する駐車ブレーキである。 Then, the large-diameter tooth portion of the output gear 75 is meshed with the large-diameter tooth portion of the intermediate gear 75B rotatably supported on the intermediate shaft 75A, and the small-diameter tooth portion of the intermediate gear 75B is connected to one end of the reduction shaft 75C. Engage with the fixed large-diameter gear 75D. Further, the small diameter gear 75E fixed to the other end portion of the reduction shaft 75C is meshed with the axle gear 76G fixed to one end portion of the axle 76F. A driving sprocket 76H fixed to the other end of the axle 76F is driven by driving the front portion of the crawler 3A. A parking brake 71B brakes the drive shaft 71.

以上の構成により、左右のサイドクラッチ６９を接続した状態で直進走行し、操向レバー６Ａを傾倒操作すると、まず、この傾倒操作側のサイドクラッチ６９が遮断され、操向レバー６Ａの傾倒操作角度が大きくなるほど、旋回内側の車軸７６Ｆの回転速度が低下し、キャリア７３が停止した状態では、旋回外側と旋回内側の車軸７６Ｆが互いに逆向きに回転してスピンターンする。 With the above configuration, when the vehicle runs straight with the left and right side clutches 69 connected and the steering lever 6A is tilted, the side clutch 69 on the tilting operation side is first disconnected, and the tilting operation angle of the steering lever 6A is As the speed increases, the rotational speed of the axle 76F on the inside of the turn decreases, and in a state where the carrier 73 is stopped, the axle 76F on the outside of the turn and the axle 76F on the inside of the turn rotate in opposite directions to spin-turn.

尚、前記中間軸６６Ａの端部をミッションケース１８の外部へ突出させ、この中間軸６６Ａの突出端部に、角軸またはスプライン軸に形成した回転操作部６６Ｄを設ける。これによって、前記走行用静油圧式無段変速装置１２の油圧モータ１６の出力軸と前記入力軸６５をスプライン嵌合によって接続する構成とした場合には、走行用静油圧式無段変速装置１２をミッションケース１８に取り付ける際に、回転操作部６６を回転操作することで、入力軸６５のスプラインの位相と、走行用静油圧式無段変速装置１２側の油圧モータ１６の出力軸のスプラインの位相とを容易に合わせることができる。この結果、走行用静油圧式無段変速装置１２の取り付け作業を容易に行なうことができる。 The end portion of the intermediate shaft 66A is protruded to the outside of the transmission case 18, and a rotation operation portion 66D formed on a square shaft or a spline shaft is provided at the protruding end portion of the intermediate shaft 66A. Accordingly, when the output shaft of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 and the input shaft 65 are connected by spline fitting, the traveling hydrostatic continuously variable transmission 12 is provided. Is attached to the transmission case 18 by rotating the rotary operation unit 66, so that the spline phase of the input shaft 65 and the spline of the output shaft of the hydraulic motor 16 on the traveling hydrostatic continuously variable transmission 12 side are adjusted. The phase can be easily matched. As a result, it is possible to easily attach the traveling hydrostatic continuously variable transmission 12.

図４に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の油圧回路を示す。
前記走行用静油圧式無段変速装置１２は、油圧ポンプ１４の斜板であるポンプ斜板１５の傾斜角度を変更することで、この油圧ポンプ１４から油圧モータ１６への送油量を変更し、この油圧モータ１６の出力軸の回転速度を無段階に変速する構成とする。そして、このポンプ斜板１５の傾斜角度を変更する複動シリンダ９５を設け、この複動シリンダ９５へ作動油を供給するバルブ９４を設け、このバルブ９４の開度を無段階に調節するソレノイド９３を設ける。また、油圧ポンプ１４の入力軸１２Ａと同軸で駆動されるチャージポンプ８５を設け、このチャージポンプ８５の吐き出し油を、油圧ポンプ１４と油圧モータ１６の間を連通する閉回路１２Ｔに補給する構成とする。 FIG. 4 shows hydraulic circuits of the hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for harvesting and conveying.
The travel hydrostatic continuously variable transmission 12 changes the oil feed amount from the hydraulic pump 14 to the hydraulic motor 16 by changing the inclination angle of the pump swash plate 15 which is the swash plate of the hydraulic pump 14. The rotation speed of the output shaft of the hydraulic motor 16 is changed steplessly. A double-action cylinder 95 that changes the inclination angle of the pump swash plate 15 is provided, a valve 94 that supplies hydraulic oil to the double-action cylinder 95 is provided, and a solenoid 93 that adjusts the opening degree of the valve 94 steplessly. Is provided. Further, a charge pump 85 that is driven coaxially with the input shaft 12A of the hydraulic pump 14 is provided, and the discharged oil from the charge pump 85 is supplied to a closed circuit 12T that communicates between the hydraulic pump 14 and the hydraulic motor 16. To do.

また、この油圧モータ１６の斜板であるモータ斜板１７の傾斜角度を二段階に切り替える油圧シリンダ１９を設け、この油圧シリンダへ作動油を供給するバルブ９７を設け、このバルブ９７を切替作動させるソレノイド９６を設ける。このモータ斜板１７の傾斜角度の切り替えによって、この油圧モータ１６の出力軸の回転速度を低速走行側と高速走行側とに切り替え可能とする。 Further, a hydraulic cylinder 19 is provided for switching the inclination angle of the motor swash plate 17 which is the swash plate of the hydraulic motor 16 in two stages, a valve 97 for supplying hydraulic oil to the hydraulic cylinder is provided, and the valve 97 is switched. A solenoid 96 is provided. By switching the inclination angle of the motor swash plate 17, the rotational speed of the output shaft of the hydraulic motor 16 can be switched between the low speed traveling side and the high speed traveling side.

そして、前記刈取搬送用静油圧式無段変速装置２１内の閉回路には、前記走行用静油圧式無段変速装置１２のチャージポンプ８５から送られる作動油を、分流弁９２Ａで分流して供給する構成とする。このように、走行用静油圧式無段変速装置１２と刈取搬送用静油圧式無段変速装置２１でチャージポンプ８５を共用するので、製造コストを低減して安価に提供することができる。尚、前記分流弁９２Ａの送油方向上手にはフィルタ９２を設ける。また、この刈取搬送用静油圧式無段変速装置２１の油圧ポンプ（第２油圧ポンプ）８９と油圧モータ（第２油圧モータ）９０の間を連通させる閉回路において、高圧側の油路と低圧側の油路を短絡させる油路を設け、この油路にチェックバルブ９１を設ける。これによって、油圧ポンプ８９からの作動油の吐き出し方向が逆向きになった場合に、この作動油を油圧モータ９０へ送油することがなくなり、油圧モータ９０の逆転を防止することができる。この結果、刈取装置４の逆転駆動を防止して、刈取装置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から刈取装置４への伝動経路中にワンウェイクラッチを設ける必要が無く、製造コストを低減して安価に提供することができる。 Then, the hydraulic oil sent from the charge pump 85 of the traveling hydrostatic continuously variable transmission 12 is shunted by the diverter valve 92A to the closed circuit in the harvesting and conveying hydrostatic continuously variable transmission 21. It is set as the structure supplied. In this way, since the charge pump 85 is shared by the traveling hydrostatic continuously variable transmission 12 for travel and the hydrostatic continuously variable transmission 21 for harvesting and conveying, the manufacturing cost can be reduced and provided at low cost. A filter 92 is provided at the upper side of the oil feeding direction of the diversion valve 92A. Further, in a closed circuit that allows communication between the hydraulic pump (second hydraulic pump) 89 and the hydraulic motor (second hydraulic motor) 90 of the chopping and conveying hydrostatic continuously variable transmission 21, An oil passage that short-circuits the oil passage on the side is provided, and a check valve 91 is provided in this oil passage. Accordingly, when the discharge direction of the hydraulic oil from the hydraulic pump 89 is reversed, the hydraulic oil is not sent to the hydraulic motor 90, and the reverse rotation of the hydraulic motor 90 can be prevented. As a result, the reverse drive of the reaping device 4 can be prevented, and the reaping device 4 can be prevented from being damaged. In addition, it is not necessary to provide a one-way clutch in the transmission path from the harvesting / conveying hydrostatic continuously variable transmission 21 to the harvesting device 4, and the production cost can be reduced and provided at a low cost.

図５にブロック回路図を示す。
メインコントローラ５５とエンジンコントローラ５７と静油圧式無段変速装置コントローラ５６の間を通信可能に接続して車内ＬＡＮを構成する。 FIG. 5 shows a block circuit diagram.
The main controller 55, the engine controller 57, and the hydrostatic continuously variable transmission controller 56 are communicably connected to form an in-vehicle LAN.

前記メインコントローラ５５の入力側には、操縦部６の側部に設けた変速レバー１３の前後操作角度を検出するポテンショメータ１３Ａと、操縦部６の前部に設けた操向レバー６Ａの左右操作角度を検出するポテンショメータ６Ｂと、車速を検出する車速センサー５８と、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を高速走行側と低速走行側に切り替える副変速スイッチ１７Ｂと、左右のクローラを互いに逆転させて旋回するスピンターンを実行させる際に操作するスピンターンスイッチ６１と、変速レバー１３を最高速位置に操作した場合の最高車速を変更設定する最高車速設定ダイヤル５１と、走行用静油圧式無段変速装置１２の油圧ポンプ１４のポンプ斜板１５の傾斜角度を検出する斜板角度センサ１５Ｓと、駐車ブレーキ７１Ｂを入り操作する駐車ブレーキペダル（図示省略）の踏み込み角度を検出する駐車ブレーキセンサ７１Ｓを接続する。 On the input side of the main controller 55, a potentiometer 13 A for detecting the front / rear operation angle of the speed change lever 13 provided on the side of the control unit 6 and the left / right operation angle of the control lever 6 A provided on the front of the control unit 6 A potentiometer 6B that detects the vehicle speed, a vehicle speed sensor 58 that detects the vehicle speed, and a sub-transmission switch 17B that switches the motor swash plate 17 of the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling between the high-speed traveling side and the low-speed traveling side. A spin turn switch 61 that is operated to execute a spin turn in which the left and right crawlers are rotated in reverse, and a maximum vehicle speed setting dial 51 that changes and sets the maximum vehicle speed when the shift lever 13 is operated to the maximum speed position; A swash plate angle sensor 15S for detecting the tilt angle of the pump swash plate 15 of the hydraulic pump 14 of the hydrostatic continuously variable transmission 12 for traveling; Connecting the parking brake sensor 71S for detecting a depression angle of the parking brake pedal operated by entering the parking brake 71B (not shown).

前記最高車速設定ダイヤル５１は、図６に示すように、操縦部６の前部左側に配置した前上がり傾斜姿勢のパネル５１Ａの下部に設ける。このパネル５１Ａには、自動制御機能の入り切り操作用の多数のスイッチ（図示省略）を集中配置している。 As shown in FIG. 6, the maximum vehicle speed setting dial 51 is provided at a lower portion of a panel 51 A in a front rising and inclined posture arranged on the left side of the front portion of the control unit 6. A large number of switches (not shown) for turning on and off the automatic control function are centrally arranged on the panel 51A.

また、メインコントローラ５５の出力側には、左右のサイドクラッチ６９を遮断操作する左右のサイドクラッチソレノイド６９Ｌ，６９Ｒと、左右のブレーキ７７への送油圧を制御する比例減圧弁を作動させる左右のブレーキソレノイド７７Ｌ，７７Ｒと、モータ斜板１７の傾斜角度を切り替えるバルブ９７のソレノイド９６と、刈取搬送用静油圧式無段変速装置２１の油圧ポンプ８９の斜板角度を変更操作する変速モータ２１Ａを接続する。また、前記副変速スイッチ１７Ｂを、刈取クラッチまたは脱穀クラッチが接続操作されたことを検出するスイッチに代えてもよい。これにより、刈取クラッチまたは脱穀クラッチが接続操作された場合に、走行用静油圧式無段変速装置１２の油圧モータ１６のモータ斜板１７の傾斜角度が、高速走行側から低速走行側に自動的に切り変わり、刈取脱穀作業に適した低速走行状態となる。 Also, on the output side of the main controller 55, left and right side clutch solenoids 69L and 69R that operate to cut off the left and right side clutch 69, and left and right brakes that operate a proportional pressure reducing valve that controls the hydraulic pressure to the left and right brakes 77 are operated. The solenoids 77L and 77R, the solenoid 96 of the valve 97 for switching the inclination angle of the motor swash plate 17, and the speed change motor 21A for changing the swash plate angle of the hydraulic pump 89 of the hydrostatic continuously variable transmission 21 for cutting and conveying are connected. To do. Further, the auxiliary transmission switch 17B may be replaced with a switch for detecting that the cutting clutch or the threshing clutch is connected. Thus, when the cutting clutch or the threshing clutch is connected, the inclination angle of the motor swash plate 17 of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is automatically changed from the high speed traveling side to the low speed traveling side. It becomes a low-speed traveling state suitable for cutting and threshing work.

また、前記静油圧式無段変速装置コントローラ５６の出力側には、ポンプ斜板１５の傾斜角度を変更するバルブ９４を切替作動させるソレノイド９３を接続する。尚、前記エンジンコントローラ５７に接続されたセンサー等の機器は図示省略している。 A solenoid 93 for switching the valve 94 for changing the tilt angle of the pump swash plate 15 is connected to the output side of the hydrostatic continuously variable transmission controller 56. Note that devices such as sensors connected to the engine controller 57 are not shown.

以上の回路構成により、変速レバー１３の前後操作角度をポテンショメータ１３Ａによって検出し、メインコントローラ５５を介して静油圧式無段変速装置コントローラ５６からソレノイド９３へ出力がなされる。このソレノイド９３への出力によってバルブ９４が切り替わり、複動シリンダ９５の作動によってポンプ斜板１５の角度を無段階に変更し、油圧ポンプ１４から油圧モータ１６への送油量が増加して、この油圧モータ１６の出力回転速度が増速する。また、モータ側の変速は、副変速スイッチ１７Ｂの操作に基づき、メインコントローラ５５からソレノイド９６への出力によってバルブ９７を切り替え、油圧シリンダ１９の作動によってモータ斜板１７の傾斜角度を低速走行側と高速走行側との二位置に切り替えることによって行われる。このように、走行用静油圧式無段変速装置１２の油圧モータ１６を二段階に変速することで副変速機能を奏するものとし、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。 With the above circuit configuration, the forward / backward operating angle of the speed change lever 13 is detected by the potentiometer 13A, and an output is made from the hydrostatic continuously variable transmission controller 56 to the solenoid 93 via the main controller 55. The valve 94 is switched by the output to the solenoid 93, the angle of the pump swash plate 15 is changed steplessly by the operation of the double acting cylinder 95, and the amount of oil fed from the hydraulic pump 14 to the hydraulic motor 16 increases. The output rotation speed of the hydraulic motor 16 increases. Further, the gear shift on the motor side is performed by switching the valve 97 by the output from the main controller 55 to the solenoid 96 based on the operation of the sub shift switch 17B, and the tilt angle of the motor swash plate 17 is set to the low speed travel side by the operation of the hydraulic cylinder 19. This is done by switching to the two positions on the high speed side. As described above, the sub-shift function is achieved by shifting the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 in two stages, and the mechanical sub-transmission mechanism in the transmission case 18 is omitted. .

しかして、前記最高車速設定ダイヤル５１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の傾斜角度を低速走行側に切り替えた状態で、変速レバー１３を最高速位置に操作した際の、油圧ポンプ１４のポンプ斜板１５の最大傾斜角度を無段階に変更設定するものである。 Thus, the maximum vehicle speed setting dial 51 moves the shift lever 13 to the highest speed position in a state where the inclination angle of the motor swash plate 17 of the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to the low speed traveling side. The maximum inclination angle of the pump swash plate 15 of the hydraulic pump 14 is changed and set steplessly.

即ち、図７に示すグラフのように、縦軸に変速レバー１３の前進側の操作位置をとり、横軸に車速をとって、変速レバー１３の操作位置と車速との比例関係を示す比例ラインを描いた場合、最高車速設定ダイヤル５１の回転操作によって、勾配の異なる高速側の比例ラインＥと低速側の比例ラインＦの間で、比例ラインの勾配が無段階に変更される。具体的には、変速レバー１３の単位操作量におけるポンプ斜板１５の傾斜角度の変化量が、最高車速設定ダイヤル５１の回転操作によって変更されるよう、ポテンショメータ１３Ａの検出値と斜板角度センサ１５Ｓの検出値との関係を、メインコントローラ５５に予め設定している。 That is, as in the graph shown in FIG. 7, a proportional line indicating the proportional relationship between the operation position of the speed change lever 13 and the vehicle speed, with the operation position on the forward side of the speed change lever 13 on the vertical axis and the vehicle speed on the horizontal axis. When the maximum vehicle speed setting dial 51 is rotated, the gradient of the proportional line is changed steplessly between the proportional line E on the high speed side and the proportional line F on the low speed side with different gradients. Specifically, the detected value of the potentiometer 13A and the swash plate angle sensor 15S are changed so that the change amount of the tilt angle of the pump swash plate 15 in the unit operation amount of the shift lever 13 is changed by the rotation operation of the maximum vehicle speed setting dial 51. The relationship with the detected value is set in the main controller 55 in advance.

これによって、例えば、比例ラインＥにおいて変速レバー１３を最高速位置に操作した場合の車速Ｖ１は、比例ラインＦにおいて変速レバー１３を最高位置に操作した場合の車速Ｖ２よりも高くなる。 Accordingly, for example, the vehicle speed V1 when the shift lever 13 is operated to the highest speed position in the proportional line E is higher than the vehicle speed V2 when the shift lever 13 is operated to the highest position in the proportional line F.

通常、移動状態では油圧モータ１６のモータ斜板１７の傾斜角度を高速走行側に切り替えており、刈取作業に移行するときには、このモータ斜板１７の傾斜角度を低速走行側に切り替える。このように、刈取作業を行うためにモータ斜板１７の傾斜角度を低速走行側に切り替えれば、車速の変速範囲を最高車速設定ダイヤル５１で設定した圃場条件や作物条件に適した範囲に制限でき、刈取作業におけるコンバインの操作性および刈取作業の能率を高めることができる。 Usually, in the moving state, the inclination angle of the motor swash plate 17 of the hydraulic motor 16 is switched to the high speed traveling side, and when shifting to the cutting operation, the inclination angle of the motor swash plate 17 is switched to the low speed traveling side. Thus, if the inclination angle of the motor swash plate 17 is switched to the low-speed traveling side to perform the cutting operation, the speed range of the vehicle speed can be limited to a range suitable for the field condition and the crop condition set by the maximum vehicle speed setting dial 51. The operability of the combine in the cutting work and the efficiency of the cutting work can be improved.

また、この最高車速設定ダイヤル５１による最高速度の設定変更（調節）は油圧モータ１６のモータ斜板１７の傾斜角度が低速走行側に切り替えられた状態でのみ有効とする。そして、最高車速設定ダイヤル５１で最高車速を設定した後にモータ斜板１７の傾斜角度が低速走行側から高速走行側に切り替えられた場合には、前回の最高車速設定ダイヤル５１による最高車速の設定を無効にし、最高車速の制限を解除する構成とする。 The maximum speed setting change (adjustment) by the maximum vehicle speed setting dial 51 is effective only when the inclination angle of the motor swash plate 17 of the hydraulic motor 16 is switched to the low speed traveling side. When the maximum vehicle speed is set by the maximum vehicle speed setting dial 51 and the inclination angle of the motor swash plate 17 is switched from the low-speed traveling side to the high-speed traveling side, the maximum vehicle speed is set by the previous maximum vehicle speed setting dial 51. It is set to be invalidated and the restriction on the maximum vehicle speed is released.

即ち、低速走行での刈取作業が終了したとき、圃場間移動のために油圧モータ１６のモータ斜板１７の傾斜角度を高速走行側に切り替えれば、最高車速の制限が解除されて高速走行が可能になるので、最高車速設定ダイヤル５１により行っていた最高車速の設定を手動で解除する操作を省略でき、高速での圃場間移動と低速での刈取作業とを反復するコンバインの操作性および刈取作業の能率を更に高めることができる。 That is, when the cutting operation at low speed is completed, the maximum vehicle speed restriction is released and high speed driving is possible if the inclination angle of the motor swash plate 17 of the hydraulic motor 16 is switched to the high speed driving side for movement between fields. Therefore, the operation of manually releasing the setting of the maximum vehicle speed performed by the maximum vehicle speed setting dial 51 can be omitted, and the operability and the cutting operation of the combine for repeating the movement between the fields at a high speed and the cutting operation at a low speed. The efficiency of can be further increased.

しかして、車速に同調して刈取搬送用静油圧式無段変速装置２１が変速作動する構成とする。
即ち、刈取搬送用静油圧式無段変速装置２１は、変速レバー１３の操作位置を検出するポテンショメータ１３Ａの検出結果、または車速センサ５８の検出結果に応じて変速制御する構成とする。 Therefore, the hydrostatic continuously variable transmission 21 for cutting and conveying is configured to shift in synchronization with the vehicle speed.
In other words, the hydrostatic continuously variable transmission 21 for cutting and conveying is configured to perform shift control according to the detection result of the potentiometer 13A that detects the operation position of the shift lever 13 or the detection result of the vehicle speed sensor 58.

例えば、図８のように、走行速度に対して所定の比率で刈取駆動速度が増速する標準作業ラインＡと、この標準作業ラインＡよりも急勾配で刈取駆動速度が増速する倒伏作業ラインＢを設定する。Ｄはモータ斜板１７の傾斜角度を低速走行側に切り替えた状態での最高速度、Ｃはモータ斜板１７の傾斜角度を高速走行側に切り替えた状態での最高速度を示す。 For example, as shown in FIG. 8, a standard work line A in which the cutting drive speed is increased at a predetermined ratio with respect to the traveling speed, and a lodging work line in which the cutting drive speed is increased more steeply than the standard work line A. Set B. D indicates the maximum speed when the tilt angle of the motor swash plate 17 is switched to the low speed travel side, and C indicates the maximum speed when the tilt angle of the motor swash plate 17 is switched to the high speed travel side.

しかして、脱穀装置２とフィードチェン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、刈取搬送用静油圧式無段変速装置２１で駆動される刈取装置４と補助チェン１１の駆動速度を走行速度に同調させることで、刈取装置４からフィードチェン１０への穀稈の引継を円滑かつ確実にする。 Accordingly, the threshing device 4 and the feed chain 10 are driven by a constant drive rotation from the engine 22 to stabilize the threshing operation, and the reaping device 4 and the auxiliary driven by the hydrostatic continuously variable transmission 21 for reaping and conveying. By synchronizing the drive speed of the chain 11 with the traveling speed, it is possible to smoothly and reliably take over the cereal from the reaping device 4 to the feed chain 10.

また、走行用静油圧式無段変速装置１２を停止させた状態で、刈取搬送用静油圧式無段変速装置２１を駆動すると、走行停止状態で刈取装置４と補助チェン１１が駆動する。これによって、補助チェン１１およびフィードチェン１０へ手刈り穀稈を供給でき、刈取脱穀作業の能率を向上させることができる。 When the hydrostatic continuously variable transmission 21 for cutting and conveying is driven in a state where the hydrostatic continuously variable transmission 12 for traveling is stopped, the reaping device 4 and the auxiliary chain 11 are driven in a stopped state. As a result, the hand-harvested cereal can be supplied to the auxiliary chain 11 and the feed chain 10, and the efficiency of the cutting and threshing work can be improved.

また、駐車ブレーキペダルが踏み込み操作されると、駐車ブレーキセンサ７１Ｓで検出される踏み込み角度に応じて、メインコントローラ５５から静油圧式無段変速装置コントローラ５６を介してソレノイド９３へ出力がなされ、このソレノイド９３への出力によってバルブ９４が切り替わり、複動シリンダ９５の作動によってポンプ斜板１５の傾斜角度を低速側へ変更し、油圧ポンプ１４から油圧モータ１６への送油量が減少して、この油圧モータ１６の出力回転速度が減速する。これによって、駐車ブレーキペダルの踏み込み角度に応じて車速が減速し、停車状態に至る。駐車ブレーキペダルと駐車ブレーキ７１Ｂの間は、機械式の連繋機構を介して接続しており、駐車ブレーキペダルの踏み込み途中で上述の油圧モータ１６の出力回転が停止し、この後に駐車ブレーキ７１Ｂが完全に入り状態となるよう、タイミングを設定している。これによって、駐車ブレーキペダルを踏み込んで停車する場合に、衝撃を緩和して円滑に停車させることができる。 Further, when the parking brake pedal is depressed, an output is made from the main controller 55 to the solenoid 93 via the hydrostatic continuously variable transmission controller 56 in accordance with the depression angle detected by the parking brake sensor 71S. The valve 94 is switched by the output to the solenoid 93, the tilt angle of the pump swash plate 15 is changed to the low speed side by the operation of the double acting cylinder 95, and the amount of oil fed from the hydraulic pump 14 to the hydraulic motor 16 is reduced. The output rotation speed of the hydraulic motor 16 is reduced. As a result, the vehicle speed is reduced according to the depression angle of the parking brake pedal, and the vehicle is stopped. The parking brake pedal and the parking brake 71B are connected via a mechanical linkage mechanism, and the output rotation of the hydraulic motor 16 stops while the parking brake pedal is being depressed. The timing is set so that it enters the state. As a result, when the parking brake pedal is depressed and stopped, the impact can be reduced and the vehicle can be stopped smoothly.

２脱穀装置
３走行装置
４刈取装置
５グレンタンク
６操縦部
１２走行用静油圧式無段変速装置
１３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
２１刈取搬送用静油圧式無段変速装置
５１最高車速設定ダイヤル
８５チャージポンプ
８９油圧ポンプ（第２油圧ポンプ）
９０油圧モータ（第２油圧モータ）
９１チェックバルブ
９２Ａ分流弁 DESCRIPTION OF SYMBOLS 2 Threshing device 3 Traveling device 4 Mowing device 5 Glen tank 6 Control part 12 Hydrostatic continuously variable transmission 13 for traveling 13 Shift lever 14 Hydraulic pump 15 Pump swash plate 16 Hydraulic motor 17 Motor swash plate 21 Step transmission 51 Maximum vehicle speed setting dial 85 Charge pump 89 Hydraulic pump (second hydraulic pump)
90 Hydraulic motor (second hydraulic motor)
91 Check valve 92A Split valve

Claims

A threshing device (2) and a Glen tank (5) are provided side by side on the upper side of the traveling device (3) driven by the hydrostatic continuously variable transmission (12) for traveling, and the front side of the Glen tank (5). A control unit (6) is provided, a cutting device (4) is provided in front of the control unit (6) and the threshing device (2), and the hydraulic pump (14) of the traveling hydrostatic continuously variable transmission (12) In a combine provided with a transmission lever (13) for changing the inclination angle of the pump swash plate (15), which is a swash plate, the swash plate of the hydraulic motor (16) of the hydrostatic continuously variable transmission (12) for travel The inclination angle of the motor swash plate (17) can be switched between the low speed traveling side and the high speed traveling side, and the maximum vehicle speed is changed and set when the shift lever (13) is operated to the maximum speed position. A setting dial (51) is provided, and the maximum vehicle speed setting dial ( The setting of the maximum vehicle speed according to 1) is effective only when the inclination angle of the motor swash plate (17) is switched to the low-speed traveling side, and after setting the maximum vehicle speed with the maximum vehicle speed setting dial (51), The combine characterized in that when the inclination angle of the plate (17) is switched from the low speed traveling side to the high speed traveling side, the setting of the maximum vehicle speed by the maximum vehicle speed setting dial (51) is invalidated.

A closed circuit is formed between the second hydraulic pump (89) and the second hydraulic motor (90) in the hydrostatic continuously variable transmission (21) for cutting and conveying that drives the cutting device (4). The combine according to claim 1, wherein the hydraulic oil sent from the charge pump (85) of the traveling hydrostatic continuously variable transmission (12) is supplied to the circuit by being diverted by the diversion valve (92A).

A short-circuit oil passage that short-circuits the high-pressure side oil passage and the low-pressure side oil passage in a closed circuit formed between the second hydraulic pump (89) and the second hydraulic motor (90) is provided, A check valve (91) is provided to prevent the hydraulic oil from being fed to the second hydraulic motor (90) side when the hydraulic oil discharge direction from the second hydraulic pump (89) is reversed. The combine according to claim 2 , wherein the combine is configured.

When the reaping clutch or the threshing clutch is connected, the inclination angle of the motor swash plate (17) of the hydraulic motor (16) of the traveling hydrostatic continuously variable transmission (12) is changed from the high speed traveling side to the low speed traveling side. The combine according to claim 1, claim 2, or claim 3, wherein the combine is automatically switched.