JP2010029105A5 - - Google Patents
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- JP2010029105A5 JP2010029105A5 JP2008194440A JP2008194440A JP2010029105A5 JP 2010029105 A5 JP2010029105 A5 JP 2010029105A5 JP 2008194440 A JP2008194440 A JP 2008194440A JP 2008194440 A JP2008194440 A JP 2008194440A JP 2010029105 A5 JP2010029105 A5 JP 2010029105A5
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- traveling
- speed
- continuously variable
- variable transmission
- hydrostatic continuously
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- 230000005540 biological transmission Effects 0.000 claims description 155
- 230000002706 hydrostatic Effects 0.000 claims description 109
- 238000005520 cutting process Methods 0.000 claims description 95
- 239000003921 oil Substances 0.000 claims description 17
- 239000010720 hydraulic oil Substances 0.000 claims description 3
- 230000003068 static Effects 0.000 claims 1
- 235000013339 cereals Nutrition 0.000 description 38
- 238000003306 harvesting Methods 0.000 description 21
- 230000002829 reduced Effects 0.000 description 13
- 238000010586 diagram Methods 0.000 description 9
- 230000032258 transport Effects 0.000 description 8
- 230000001360 synchronised Effects 0.000 description 7
- 239000000969 carrier Substances 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 239000010902 straw Substances 0.000 description 5
- 230000001629 suppression Effects 0.000 description 5
- 241000209094 Oryza Species 0.000 description 2
- 235000007164 Oryza sativa Nutrition 0.000 description 2
- 235000012970 cakes Nutrition 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 235000009566 rice Nutrition 0.000 description 2
- 241000102542 Kara Species 0.000 description 1
- 230000000875 corresponding Effects 0.000 description 1
- 230000003247 decreasing Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002147 killing Effects 0.000 description 1
- 230000036961 partial Effects 0.000 description 1
- 230000001340 slower Effects 0.000 description 1
- 238000009333 weeding Methods 0.000 description 1
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を有する作業車両において、前記走行用静油圧式無段変速装置の操作レバーの傾倒操作による変速を、低速、標準、高速、全範囲と切り替える構成は、公知である（特許文献１参照）。
また、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を有する作業車両において、前記走行用静油圧式無段変速装置の操作レバー近傍に、速度設定手段を設けた構成も、公知である（特許文献２参照）。
Further, conventionally, in a work vehicle having a traveling device capable of steplessly changing a traveling speed by a traveling hydrostatic continuously variable transmission, speed setting means is provided in the vicinity of an operation lever of the traveling hydrostatic continuously variable transmission. The structure provided with is also known (see Patent Document 2).
前記公知例は、両者共に、単に、走行用静油圧式無段変速装置の操作レバーの傾倒操作による変速を、低速、標準、高速、全範囲と切り替え、あるいは、車速設定するだけであるから、刈取部の回転数を変速された走行速度に同調して回転数を増減に変速させることはできないという課題がある。
即ち、高速の移動走行と低速の刈取作業とを反復するコンバインでは、単に、車速設定したのでは、高速の移動走行を基準にすると、低速の刈取作業に不具合が生じ、低速の刈取作業を基準にすると、移動時間が長くなって、作業性が低下する。
本願は、路上走行と刈取作業の二面性を有し、しかも、走行速度に刈取部の回転数を同調させる構成でありながら、コンバインの走行操作を簡単・適格に行えるように、刈取部への同調させる走行速度と、移動速度との切替等の走行操作等の不便性、作業性の低下を解決するようにして、操作性および作業性を向上させたものである。
In both of the known examples, both of them simply change the shift by the tilting operation of the operation lever of the hydrostatic continuously variable transmission device for traveling, to low speed, standard, high speed, full range, or set the vehicle speed. There is a problem that the rotational speed of the cutting unit cannot be increased or decreased in synchronization with the shifted traveling speed.
In other words, in a combine that repeats high-speed traveling and low-speed mowing, simply setting the vehicle speed causes a problem in low-speed mowing when the high-speed traveling is used as a reference. In this case, the movement time becomes longer and workability is lowered.
The present application has the duality of running on the road and mowing work, and is configured to synchronize the rotational speed of the mowing unit with the running speed, so that the traveling operation of the combine can be performed easily and properly. The operability and workability are improved by solving the inconveniences of travel operations such as switching between the traveling speed to be synchronized with the traveling speed and the reduction in workability.
請求項１記載の発明は、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）を走行速度に同調して変速駆動する構成とし、前記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）の傾斜角度を調節する主変速レバー（１３）を設け、前記走行用静油圧式無段変速装置（１２）の主変速レバー（１３）の傾倒操作により変速された走行速度に同調して変速駆動する構成とし、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）の傾斜角度を低速走行側と高速走行側とへ切替可能に構成し、該モータ斜板（１７）の傾斜角度が低速走行側に切替えられた状態で、前記主変速レバー（１３）が最高速位置に操作されたときの車速を変更調節する速度調整ダイヤル（５１）を設けたことを特徴とするコンバインとしたものである。
油圧モータ（１６）のモータ斜板（１７）の斜板角度を低速走行側に切替えて行う刈取作業では、速度調整ダイヤル（５１）により圃場条件や作物条件に応じて設定最高速度を落として作業を行うことができ、作業条件に応じて最適な走行速度で走行させることができ、操作性および作業性が向上する。
また、刈取作業では油圧モータ（１６）のモータ斜板（１７）の傾斜角度を低速走行側に切替えて行うので、刈取作業を行うために油圧モータ（１６）を低速走行側に切替えれば、速度調整ダイヤル（５１）で設定した圃場条件や作物条件に応じた最適な走行速度で常時走行させることができ、操作性および作業性が向上する。
請求項２記載の発明は、請求項１において、前記速度調整ダイヤル（５１）による最高速度の設定は前記油圧モータ（１６）の斜板角度が低速走行側に切り替えられている場合に有効とし、前記油圧モータ（１６）の斜板角度が高速走行側に切り替えられた場合には速度調整ダイヤル（５１）による最高速度の設定を自動的に無効にするように構成したことを特徴とするコンバインとしたものである。
高速移動するために、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ると、速度調整ダイヤル（５１）による最高速度の設定を自動的に無効にするので、一旦、刈取作業が終了したとき、移動のために油圧モータ（１６）の斜板角度を高速走行側に切り替えれば、高速走行可能になって、速度調整ダイヤル（５１）により行っていた減速設定を一々戻す操作を不要にし、移動時間を短縮でき、高速の移動走行と低速の刈取作業とを反復するコンバインの操作性および作業能率を向上させることができる。
請求項３記載の発明は、請求項２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の斜板角度を高速走行側に切替えた状態で旋回するとき、油圧モータ１６のモータ斜板１７の傾斜角度を低速走行側へ自動的に切替えるように構成したことを特徴とするコンバインとしたものである。
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）を高速走行に切替えた状態で旋回すると、自動的に油圧モータ（１６）のモータ斜板（１７）の斜板角度を低速走行側に自動的に切替え、低速で高トルク走行が可能となって、エンジン（２２）の馬力ドロップを抑制減少させ、旋回走行を円滑にして作業性が向上する。
請求項４記載の発明は、請求項１又は請求項２又は請求項３において、前記刈取部（４）を駆動する刈取搬送用静油圧式無段変速装置（２１）を設け、該刈取搬送用静油圧式無段変速装置（２１）の出力回転を変速することで刈取部（４）を走行速度に同調して駆動する構成とし、前記走行用静油圧式無段変速装置（１２）には、前記油圧ポンプ（１４）に入力される回転により駆動されるチャージポンプ（８５）を設け、該チャージポンプ（８５）からの送油を、走行用静油圧式無段変速装置（１２）内の油圧回路側と刈取搬送用静油圧式無段変速装置（２１）内の油圧回路側とに分流して供給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。
請求項５記載の発明は、請求項４において、前記チャージポンプ（８５）から走行用静油圧式無段変速装置（１２）内の油圧回路側へ供給される作動油を、該走行用静油圧式無段変速装置（１２）内の油圧回路と、前記ポンプ斜板（１５）の傾斜角度を変更する複動シリンダ（９５）とに供給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。
Invention of claim 1, wherein, reaper forward (4) provided in the variable speed driving apparatus a traveling speed steplessly by traveling hydrostatic continuously variable transmission (12) (3), the travel device (3 ) Is provided with a threshing device ( 2 ) , and the reaping part ( 4 ) is driven to shift in synchronization with the traveling speed. The hydraulic pump ( 14 ) of the hydrostatic continuously variable transmission for traveling ( 12 ) ) pump swash plate (15 main shift lever for adjusting the inclination angle of) (13) is provided in, is shifted by the tilting operation of the main shift lever of the travel hydrostatic continuously variable transmission (12) (13) The drive swash plate ( 17 ) of the hydraulic motor ( 16 ) of the traveling hydrostatic continuously variable transmission ( 12 ) is driven at a low speed travel side and a high speed travel side. switchably configured to, the motor swash plate (17) In a state in which the oblique angle is switched to the low speed side, Combine, characterized in that said main shift lever (13) is provided with a speed adjustment dial (51) that the change regulation vehicle speed when operated in maximum speed position Ru der what was.
In the cutting operation performed by switching the swash plate angle of the motor swash plate ( 17 ) of the hydraulic motor ( 16 ) to the low speed traveling side, the maximum adjustment speed is lowered according to the field condition and crop condition by the speed adjustment dial ( 51 ). Can be performed at an optimum traveling speed according to the working conditions, and operability and workability are improved.
Further, the cutting work is performed by switching the inclination angle of the motor swash plate (17) of the hydraulic motor (16) to the low-speed running side, if switching the hydraulic motor (16) in order to perform the cutting work low speed side, It is possible to always run at an optimum running speed according to the field conditions and crop conditions set by the speed adjustment dial ( 51 ) , and the operability and workability are improved.
The invention according to claim 2 is characterized in that, in claim 1, the setting of the maximum speed by the speed adjustment dial ( 51 ) is effective when the swash plate angle of the hydraulic motor ( 16 ) is switched to the low speed traveling side, A combine configured to automatically disable the setting of the maximum speed by the speed adjustment dial ( 51 ) when the swash plate angle of the hydraulic motor ( 16 ) is switched to a high speed travel side; Ru der those.
When the inclination angle of the motor swash plate ( 17 ) of the hydraulic motor ( 16 ) is switched to the high-speed traveling side for high-speed movement, the maximum speed setting by the speed adjustment dial ( 51 ) is automatically invalidated. When the cutting operation is completed, if the swash plate angle of the hydraulic motor ( 16 ) is switched to the high speed traveling side for movement, high speed traveling is possible, and the deceleration setting performed by the speed adjustment dial ( 51 ) is set one by one. The returning operation is unnecessary, the travel time can be shortened, and the operability and work efficiency of the combine that repeats the high-speed travel and the low-speed cutting operation can be improved.
The invention of claim 3 is the motor of the hydraulic motor 16 according to claim 2, wherein the motor of the hydraulic motor 16 is turned when the swash plate angle of the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to the high speed traveling side. Ru der those with combined, characterized in that to constitute a tilt angle of the swash plate 17 to automatically switch to the low speed side.
When the motor swash plate of the hydraulic motor (16) of the travel hydrostatic continuously variable transmission (12) to (17) pivots in a state of switching to the high speed running, automatic motor swash plate of the hydraulic motor (16) (17 ) Is automatically switched to the low speed running side, and high torque running is possible at low speed, the horsepower drop of the engine ( 22 ) is suppressed and reduced, the turning running is smoothed, and the workability is improved.
According to a fourth aspect of the present invention, in the first, second, or third aspect, there is provided a hydrostatic continuously variable transmission (21) for cutting and conveying that drives the cutting unit (4), and The cutting section (4) is driven in synchronization with the traveling speed by shifting the output rotation of the hydrostatic continuously variable transmission (21). The traveling hydrostatic continuously variable transmission (12) includes , A charge pump (85) driven by rotation input to the hydraulic pump (14) is provided, and the oil feed from the charge pump (85) is sent to the hydrostatic continuously variable transmission (12) for traveling. The combine is characterized in that it is divided and supplied to the hydraulic circuit side and the hydraulic circuit side in the harvesting and conveying hydrostatic continuously variable transmission (21).
According to a fifth aspect of the present invention, in the fourth aspect, the hydraulic oil supplied from the charge pump (85) to the hydraulic circuit side in the traveling hydrostatic continuously variable transmission (12) is supplied to the traveling hydrostatic pressure. This is a combine that is configured to supply the hydraulic circuit in the continuously variable transmission (12) and the double-acting cylinder (95) that changes the inclination angle of the pump swash plate (15). is there.
請求項１記載の発明では、刈取部（４）を走行速度に同調させて変速させるので、刈取部（４）から穀稈を円滑に搬送でき、速度調整ダイヤル（５１）により圃場条件や作物条件に応じて設定最高速度を落として作業を行って、作業条件に応じて最適な走行速度で走行させることができ、操作性および作業能率を向上させることができる。
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て、高速移動するために、油圧モータ（１６）のモータ斜板（１７）の斜板角度を高速走行側に切り替えれば、速度調整ダイヤル（５１）による最高速度の設定を自動的に無効にするので、油圧モータ（１６）のモータ斜板（１７）を切替操作すれば、速度調整ダイヤル（５１）により行っていた減速設定を一々戻す操作を不要にでき、高速の移動走行と低速の刈取作業とを反復するコンバインの操作性および作業能率を向上させることができる。
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て、高速移動するために、油圧モータ（１６）のモータ斜板（１７）の斜板角度を高速走行側に切替えた状態で旋回しても、自動的に油圧モータ（１６）のモータ斜板（１７）を低速走行側に自動的に切替えるので、低速で高トルク走行が可能となって、エンジン（２２）の馬力ドロップを抑制減少させ、旋回走行を円滑にして作業能率を向上させることができる。
請求項４記載の発明では、上記請求項１又は請求項２又は請求項３記載の発明の効果に加えて、走行用静油圧式無段変速装置（１２）及び刈取搬送用静油圧式無段変速装置（２１）のチャージポンプ（８５）を共用することで、走行用静油圧式無段変速装置（１２）及び刈取搬送用静油圧式無段変速装置（２１）を備えるコンバインを安価に構成できる。
請求項５記載の発明では、上記請求項４記載の発明の効果に加えて、チャージポンプ（８５）からの送油によって複動シリンダ（９５）を作動させることができる。
In the first aspect of the present invention, since the speed change by tuning reaper (4) to the running speed, reaper (4) culms can smoothly conveyed from, field conditions and crop conditions by the speed adjustment dial (51) Accordingly, it is possible to perform the work with the set maximum speed being lowered according to the conditions, and to run at the optimum running speed according to the working conditions, and to improve the operability and work efficiency.
In the invention described in claim 2, in addition to the effect of the invention described in claim 1, if the swash plate angle of the motor swash plate ( 17 ) of the hydraulic motor ( 16 ) is switched to the high speed traveling side in order to move at high speed. , because it automatically disable the setting of the maximum speed by the speed adjustment dial (51), if the switching operation of the motor swash plate of the hydraulic motor (16) (17), has been performed by the speed adjustment dial (51) decelerating The operation of returning the settings one by one can be made unnecessary, and the operability and work efficiency of the combine that repeats the high-speed traveling and the low-speed cutting operation can be improved.
In the invention of claim 3, wherein, in addition to the effect of the invention of the 請 Motomeko 2 wherein, in order to fast moving, switching the motor swash plate of the hydraulic motor (16) to the swash plate angle of (17) to the high speed side The motor swash plate ( 17 ) of the hydraulic motor ( 16 ) is automatically switched to the low-speed traveling side even when the vehicle is turned, so that high-torque traveling at low speed is possible, and the engine ( 22 ) The horsepower drop can be suppressed and reduced, and the turning efficiency can be made smooth to improve the work efficiency.
In the invention of claim 4, in addition to the effect of the invention of claim 1 or claim 2 or claim 3, the hydrostatic continuously variable transmission (12) for traveling and the hydrostatic continuously variable transmission for cutting and conveying By combining the charge pump (85) of the transmission (21), a combine including the hydrostatic continuously variable transmission (12) for traveling and the hydrostatic continuously variable transmission (21) for harvesting and conveying is configured at low cost. it can.
In the invention according to claim 5, in addition to the effect of the invention according to claim 4, the double-acting cylinder (95) can be operated by oil feeding from the charge pump (85).
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 cerealed in the threshing room. Although it conveys until it discharges | emits from a straw discharge port (illustration omitted), the structure which conveys the grain straw harvested by the cutting part 4 to the grain straw supply conveyance apparatus 10 is arbitrary.
前記穀稈供給搬送装置１０は、挾扼杆（図示省略）と搬送供給チェン（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、搬送供給チェンに弾着して穀稈を挟持搬送する。搬送供給チェンは無端チェンにより構成し、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刈取搬送用静油圧式無段変速装置２１により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および刈取搬送用静油圧式無段変速装置２１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。
The cereal supply / conveyance device 10 includes a cocoon (not shown) and a conveyance / supply chain (feed chain, not shown). The rice cake 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 conveyance supply chain to convey and hold the rice cake. The conveyance supply chain is configured by an endless chain, and is configured to move by being guided by an arbitrarily configured 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 synchronized with the traveling speed of the traveling device 3 and is hydrostatic for cutting conveyance. Shifting is performed by the continuously variable transmission 21.
In other words, the hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for harvesting and transporting increase / decrease according to the amount of tilting operation of the main transmission lever 13, for example, as shown in FIG. The speed is changed by the standard work line A for increasing the transmission rotation at a predetermined ratio with respect to the speed and the overturning work line B for increasing the speed in a shorter time than the standard work line A.
また、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３）、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を高速走行Ｃと低速走行Ｄとの切替可能に構成する。
具体的には、主変速レバー１３の傾倒操作角度をＨＳＴ開度センサによって検出し、後述する本機コントローラ５５からソレノイド９３への出力によってバルブ９４を切替え、複動シリンダ９５の作動によってポンプ斜板１５の角度を変更することによって無段変速が行われる。また、モータ側の変速は、本機コントローラ５５からソレノイド９６への出力によってバルブ９７を切替え、油圧シリンダ１９の作動によってモータ斜板１７の角度を二位置に切り替えることによって行われる。
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（シリンダ）である。
The traveling hydrostatic continuously variable transmission 12 changes the inclination of the pump swash plate 15 of the hydraulic pump 14 to change the amount of oil supplied to the hydraulic motor 16 steplessly and transmits the rotation (see FIG. 3) The hydraulic motor 16 is also provided with a motor swash plate 17 capable of switching the inclination angle in two stages, and the upper limit of the traveling speed of the airframe is configured to be switchable between the high speed traveling C and the low speed traveling D.
Specifically, the tilting operation angle of the main transmission lever 13 is detected by an HST opening sensor, the valve 94 is switched by an output from a controller 55 of this machine, which will be described later, to a solenoid 93, and the pump swash plate is actuated by the operation of the double-acting cylinder 95. By changing the angle of 15, continuously variable transmission is performed. Further, the motor-side speed change is performed by switching the valve 97 by the output from the controller 55 of the main unit controller 55 and switching the angle of the motor swash plate 17 to two positions by the operation of the hydraulic cylinder 19.
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 (cylinder) for switching the motor swash plate 17.
しかして、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。
また、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により変速するので、通常は刈取搬送用静油圧式無段変速装置２１が刈取部４を走行速度に同調させて変速するが、所定条件のときは、刈取搬送用静油圧式無段変速装置２１単独で刈取部４および／またはシンクロ用前側供給搬送装置１１を駆動するように構成する。
そのため、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。
Thus, the synchronization with the running speed by the chopping and conveying hydrostatic continuously variable transmission 21 dedicated to the chopping and conveying is performed by driving the threshing device 2 and the cereal supply and conveying device 10 with constant driving rotation from the engine 22. While making the operation stable, the transfer to the cereal supply and transfer device 10 is made smooth and reliable.
In addition, since the transmission rotation to the cutting unit 4 and the front-side supply / conveyor 11 for synchronization is shifted by the hydrostatic continuously variable transmission 21 for harvesting and conveying, the hydrostatic continuously variable transmission 21 for harvesting and conveying is normally used for the harvesting and conveying. The part 4 is shifted in synchronization with the traveling speed. When the predetermined condition is satisfied, the cutting part 4 and / or the synchro front supply / conveyor 11 are driven by the cutting and conveying hydrostatic continuously variable transmission 21 alone. Constitute.
Therefore, even during the predetermined travel speed from the state where the airframe is stopped, the mowing and transporting hydrostatic continuously variable transmission 21 can drive the mowing unit 4 and the front supply / conveyor 11 for synchronization at a sufficient number of revolutions. The mowing unit 4 and the threshing device 2 are driven stably immediately after the start, and the mowing 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.
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、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、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、３９は刈取用中間出力軸、４０は搬送シンクロ用出力軸、４１は穀稈供給搬送中間出力軸、４１Ａは供給搬送用プーリー、４２は唐箕、４３は穀稈供給搬送装置１０の駆動歯車、４４は刈取脱穀クラッチ、４５は刈取用中間出力軸３９に設けた刈取中間出力プーリー，４６は刈取中間入力プーリー、４７は刈取中間出力プーリー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。 The structure of the rotation transmission mechanism from the engine 22 to the traveling hydrostatic continuously variable transmission 12 and the harvesting and conveying hydrostatic continuously variable transmission 21 is arbitrary. For example, 25A represents a traveling 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, and 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, and 37 is a cutting conveyance The cutting HST input shaft of the hydrostatic continuously variable transmission 21 for cutting, 38 is the cutting HST output shaft of the hydrostatic continuously variable transmission 21 for cutting and conveying, 39 is the intermediate output shaft for cutting, 40 is the output shaft for conveying synchronization, 41 is cereal Feeding and conveying intermediate output shaft, 41A is a feeding and conveying pulley, 42 is a tang, 43 is a drive gear of the cereal feeding and conveying device 10, 44 is a mowing threshing clutch, and 45 is a mowing intermediate output pulley provided on the mowing intermediate output shaft 39. , 46 is a cutting intermediate input pulley, 47 is a cutting intermediate output pulley 45 and a belt wound around the cutting intermediate input pulley 46, 50 is a gear case provided with a cutting intermediate gear 36, a cutting intermediate output shaft 39, and the like. A hydrostatic continuously variable transmission 21 for cutting and conveying is provided on the 50 control section 6 side. Therefore, the airframe weight balance and the attachment balance of the gear case 50 are improved.
ギヤケース５０の穀稈供給搬送装置１０側の刈取用中間出力軸３９と搬送シンクロ用出力軸４０と穀稈供給搬送中間出力軸４１には、刈取中間出力プーリー４５に掛け回したベルト４７等の張力が作用するが、この張力の作用する反対側のギヤケース５０に刈取搬送用静油圧式無段変速装置２１を設けているので、バランスが良好になる。
しかして、前記走行用静油圧式無段変速装置１２の油圧モータ１６を低速走行に切替えた状態で、主変速レバー１３の最高速位置の車速を設定する速度調整ダイヤル５１を設ける。
油圧モータ１６を低速走行に切替えて行う刈取作業では、圃場条件や作物条件に応じて設定最高速度を設定して作業を行うことができ、作業条件に応じて最適な走行速度で走行させることができ、操作性および作業性を向上させる。
刈取作業では油圧モータ１６を低速走行側に切替えて行うので、常時、圃場条件や作物条件に応じた最適な走行速度で走行させることができる。
即ち、速度調整ダイヤル５１は図３の速度ラインＥと速度ラインＦの間で無段階で最高速度を設定する。
The intermediate output shaft 39 for harvesting on the side of the grain supply / conveyor 10 of the gear case 50, the output shaft 40 for synchro transmission, and the intermediate output shaft 41 for supply of the grain supply / conveyor are tensions of the belt 47 and the like wound around the intermediate output pulley 45 for harvesting. However, since the gear case 50 on the opposite side to which this tension acts is provided with the hydrostatic continuously variable transmission 21 for cutting and conveying, the balance becomes good.
Accordingly, a speed adjustment dial 51 is provided for setting the vehicle speed at the highest speed position of the main transmission lever 13 in a state where the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to low speed traveling.
In the cutting work performed by switching the hydraulic motor 16 to the low speed traveling, the operation can be performed by setting the set maximum speed according to the field condition and the crop condition, and the traveling can be performed at the optimum traveling speed according to the working condition. This improves operability and workability.
Since the mowing operation is performed by switching the hydraulic motor 16 to the low-speed traveling side, it is possible to always travel at an optimum traveling speed according to the field conditions and crop conditions.
That is, the speed adjustment dial 51 sets the maximum speed steplessly between the speed line E and the speed line F in FIG.
この場合、通常、移動状態では油圧モータ１６のモータ斜板１７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、油圧モータ１６を低速走行側に切替えて行うので、刈取作業を行うために油圧モータ１６を低速走行側に切替えれば、速度調整ダイヤル５１で設定した圃場条件や作物条件に応じた最適な走行速度で走行させることができ、操作性および作業性を向上させる。
前記速度調整ダイヤル５１による最高速度の設定変更（調節）は油圧モータ１６が低速走行の場合に有効とし、油圧モータ１６が高速走行の場合には自動的に速度調整ダイヤル５１による最高速度の設定を無効にして油圧ポンプ１４の初期設定（最大性能発揮状態）における最高出力回転とするように構成する。
一旦、刈取作業が終了したとき、移動のために油圧モータ１６を高速走行側に切り替えれば、高速走行可能になって、速度調整ダイヤル５１により行っていた減速設定を一々戻す操作を不要にし、移動時間を短縮でき、高速の移動走行と低速の刈取作業とを反復するコンバインの操作性および作業性を向上させる。
In this case, normally, in the moving state, 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 hydraulic motor 16 is switched to the low-speed traveling side. If the hydraulic motor 16 is switched to the low-speed traveling side, the traveling can be performed at the optimum traveling speed according to the field conditions and crop conditions set by the speed adjustment dial 51, and the operability and workability are improved.
The maximum speed setting change (adjustment) by the speed adjustment dial 51 is effective when the hydraulic motor 16 is traveling at a low speed, and the maximum speed is automatically set by the speed adjustment dial 51 when the hydraulic motor 16 is at a high speed. It is configured to be disabled and set to the maximum output rotation at the initial setting (maximum performance exerted state) of the hydraulic pump 14.
Once the mowing operation is completed, if the hydraulic motor 16 is switched to the high-speed traveling side for movement, high-speed traveling is possible, and the operation for returning the deceleration setting performed by the speed adjustment dial 51 is unnecessary, and the movement is performed. Time can be shortened, and the operability and workability of a combine that repeats high-speed traveling and low-speed mowing work are improved.
仮に、速度調整ダイヤル５１による最高速度の設定が油圧モータ１６の低速走行のみならず高速走行の場合にも有効とすると、例えば、速度調整ダイヤル５１による最高速度の設定を減速設定していると、油圧モータ１６を高速走行に切り替えても、移動する際の走行速度が遅くなって、移動時間が長くなり、また、油圧モータ１６が高速状態のときに速度調整ダイヤル５１による設定変更するようにすると、油圧モータ１６の低速状態と高速状態の夫々で設定（調節）操作が必要となって、操作が煩雑になるが、本願では速度調整ダイヤル５１による最高速度の設定（調整・変更）は油圧モータ１６が低速走行の場合に有効としているので、刈取作業では圃場条件や作物条件に応じて設定最高速度を落として作業を行うことができ、作業条件に応じて最適な走行速度で走行させることができ、また、一旦、刈取作業が終了したときは、一々速度調整ダイヤル５１により行った減速設定を戻す操作を不要にして、高速走行により移動することができ、操作性および作業性を向上させる。 If the setting of the maximum speed by the speed adjustment dial 51 is effective not only when the hydraulic motor 16 travels at a low speed but also at a high speed, for example, if the setting of the maximum speed by the speed adjustment dial 51 is set as a deceleration setting, Even if the hydraulic motor 16 is switched to high-speed traveling, the traveling speed at the time of movement slows down and the traveling time becomes long, and when the hydraulic motor 16 is in a high-speed state, the setting is changed by the speed adjustment dial 51. The setting (adjustment) operation is required in each of the low-speed state and the high-speed state of the hydraulic motor 16, and the operation becomes complicated. In this application, the maximum speed setting (adjustment / change) by the speed adjustment dial 51 is performed by the hydraulic motor. 16 is effective when the vehicle is traveling at a low speed. Therefore, in the cutting operation, the maximum speed can be reduced according to the field condition and the crop condition. According to the travel speed, and once the mowing operation is completed, the operation of returning the deceleration setting performed by the speed adjustment dial 51 is not necessary and the vehicle is moved at a high speed. Can improve operability and workability.
また、刈取作業では、油圧モータ１６を低速走行側に切替えて行うので、走行用静油圧式無段変速装置１２の油圧モータ１６が高速状態で主変速レバー１３を最高速に操作して油圧ポンプ１４の回転を最大にすることはなく、仮に、図２の油圧モータ１６の回転を最大にしたときの最高走行速度ラインＣに同調させて刈取部４を増速駆動させて刈取作業したとすると、走行速度の上がりすぎによる刈刃９の刈跡の悪化、藁量の増加による刈取部４の詰まり・破損を招くが、本願では、これを防止する。
したがって、速度調整ダイヤル５１が設定しうる最高走行速度は作業最高速度ラインＤ以下となるように構成する。
５５は本機コートローラ、５６は走行用静油圧式無段変速装置１２（刈取搬送用静油圧式無段変速装置２１）のＨＳＴコントローラ、５７はエンジン２２に設けたエンジンコントローラ、５８は車速センサーである。
なお、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の高速走行側と低速走行側への切替構成は任意であり、切替スイッチを設けて手動操作により切替える構成や、作業クラッチ（刈取クラッチあるいは脱穀クラッチ）の入りの検出により自動的に切替える構成でもよい。
In the cutting operation, the hydraulic motor 16 is switched to the low-speed traveling side, so that the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 operates the main transmission lever 13 at the highest speed while the hydraulic motor 16 operates at a high speed. 14 is not maximized, and it is assumed that the cutting operation is performed by driving the cutting unit 4 at an increased speed in synchronization with the maximum traveling speed line C when the rotation of the hydraulic motor 16 of FIG. 2 is maximized. , deterioration of Kariato the cutting blade 9 by the excessive increase of the running speed, but lead to clogging or damage of the reaper 4 due to the increase in straw weight, in the present application, to prevent this.
Accordingly, the maximum travel speed that can be set by the speed adjustment dial 51 is set to be equal to or lower than the maximum work speed line D.
55 is a coat roller of the machine, 56 is an HST controller of the hydrostatic continuously variable transmission 12 for traveling (hydrostatic continuously variable transmission 21 for cutting and conveying), 57 is an engine controller provided in the engine 22, and 58 is a vehicle speed sensor. It is.
Note that the switching configuration of the hydraulic swash plate 17 of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 to the high-speed traveling side and the low-speed traveling side is arbitrary, and a configuration in which a changeover switch is provided and switched by manual operation, A configuration may be adopted in which switching is performed automatically upon detection of engagement of a work clutch (a mowing clutch or a threshing clutch).
しかして、前記走行用静油圧式無段変速装置１２の油圧モータ１６を高速走行に切替えた状態で、旋回するとき、自動的に油圧モータ１６のモータ斜板１７を低速走行に切替えるように構成する（図８）。
そのため、走行用静油圧式無段変速装置１２を低速で高出力トルクで出力するようにして、エンジン２２の馬力ドロップを抑制減少させ、作業性を向上させる。
この場合、操縦部６のパワステレバー（パワステレバーポジションセンサ）６０の倒し量が一定以上のとき、または、スピン旋回スイッチ６１がＯＮ状態で、旋回するとき、自動的に油圧モータ１６のモータ斜板１７を低速走行に切り替える。
したがって、旋回走行が円滑に行え、操作性および作業性を向上させる。
Thus, the motor swash plate 17 of the hydraulic motor 16 is automatically switched to low-speed traveling when turning while the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to high-speed traveling. (FIG. 8).
For this reason, the traveling hydrostatic continuously variable transmission 12 is output at a low speed and with a high output torque to suppress and reduce the horsepower drop of the engine 22 and improve workability.
In this case, when the turning amount of the power steering lever (power steering lever position sensor) 60 of the control unit 6 is more than a certain value, or when the spin turning switch 61 is turned on, the motor swash plate of the hydraulic motor 16 is automatically turned. 17 is switched to low speed driving.
Therefore, turning can be performed smoothly, and operability and workability are improved.
また、刈取作業の工程で旋回走行に移行する際、エンジン２２の負荷率が低く、旋回してもエンジン２２の回転が低下しない場合は、車速を維持するように構成する。
旋回開始時の負荷が少ないときは高速旋回して、作業効率を向上させる。
即ち、直進走行に比し旋回走行では走行抵抗が大きくなってエンジン２２の負荷が上昇するが、一方で脱穀装置２等の他の装置部分の負荷が少ないときは、旋回してもエンジン２２の回転が低下しないことあり、このときは車速を維持して、移動時間を短縮して作業性を向上させる。
この場合、作業者が減速操作したときは、作業者の操作を優先して減速する。
また、旋回するときにエンジン２２の負荷率が高い場合は、パワステレバー６０の倒し量に応じて車速を減速するように構成する（図９）。
通常の減速操作は主変速レバー１３により行っており、パワステレバー６０は旋回半径の大小を操作するが、エンジン２２の負荷が高いときは主変速レバー１３によらずにパワステレバー６０の倒し量に応じて自動的に車速を減速することによって（図９）、エンジン２２の回転が落ちるのを抑制減少させ、旋回走行が円滑に行うと共に、パワステレバー６０の操作だけで旋回操作および減速操作を行って、操作性および作業性を向上させる。
In addition, when shifting to turning in the mowing process, if the load factor of the engine 22 is low and the rotation of the engine 22 does not decrease even after turning, the vehicle speed is maintained.
When the load at the start of turning is small, it turns at high speed to improve work efficiency.
In other words, the running resistance increases and the load on the engine 22 increases in the cornering as compared with the straight traveling. On the other hand, when the load on the other devices such as the threshing device 2 is small, the engine 22 In some cases, the rotation does not decrease. At this time, the vehicle speed is maintained, the traveling time is shortened, and workability is improved.
In this case, when the operator performs a deceleration operation, the operator's operation is preferentially decelerated.
Further, when the engine 22 has a high load factor when making a turn, the vehicle speed is reduced according to the amount of tilting of the power steering lever 60 (FIG. 9).
The normal speed reduction operation is performed by the main speed change lever 13, and the power steering lever 60 operates the turning radius. However, when the load on the engine 22 is high, the power steering lever 60 is not tilted by the main speed change lever 13 but the amount of tilting of the power steering lever 60 is reduced. Accordingly, by automatically decelerating the vehicle speed (FIG. 9), the decrease in the rotation of the engine 22 is suppressed and the turning traveling is smoothly performed, and the turning operation and the deceleration operation are performed only by operating the power steering lever 60. Improve operability and workability.
エンジン２２の負荷率の判定検出する手段は任意であるが、本願ではエンジン回転センサ６２によりエンジン回転数を検出して行っている。
この場合の減速は、油圧ポンプ１４の斜板１５あるいは油圧モータ１６のモータ斜板１７の何れかの傾斜角度の変更で行う。
しかして、図１０は、ミッションケース１８の展開状態の概略図であり、上部に走行用静油圧式無段変速装置１２の油圧モータ１６から出力される入力軸６５を設け、入力軸６５に出力歯車６６を設ける。出力歯車６６にはサイドクラッチ軸６７に固定の受動歯車６８を常時噛合せる。６９はサイドクラッチ軸サイドクラッチ軸６７に設けた左右サイドクラッチである。
サイドクラッチ軸６７の受動歯車６８には遊星歯車機構７０の駆動軸７１に固定の駆動歯車７２を噛み合わせる。遊星歯車機構７０は公知構成であり、浅い円筒形状のキャリア７３に遊星歯車７４を設け、駆動軸７１に遊嵌状態に設けた遊星歯車７５に中間遊星歯車７６を介して噛み合わせる。キャリア７３にはキャリア７３の回転に制動を付与する多板式のブレーキ７７を設ける。
The means for determining and detecting the load factor of the engine 22 is arbitrary, but in the present application, the engine speed is detected by the engine speed sensor 62.
The deceleration in this case is performed by changing the inclination angle of either the swash plate 15 of the hydraulic pump 14 or the motor swash plate 17 of the hydraulic motor 16.
FIG. 10 is a schematic diagram of the unfolded state of the mission case 18, and an input shaft 65 output from the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is provided on the upper portion, and output to the input shaft 65. A gear 66 is provided. A passive gear 68 fixed to the side clutch shaft 67 is always meshed with the output gear 66. Reference numeral 69 denotes a left and right side clutch provided on the side clutch shaft side clutch shaft 67.
A drive gear 72 fixed to a drive shaft 71 of the planetary gear mechanism 70 is engaged with the passive gear 68 of the side clutch shaft 67. The planetary gear mechanism 70 has a known configuration, and a planetary gear 74 is provided on a shallow cylindrical carrier 73 and meshed with a planetary gear 75 provided in a loosely fitted state on the drive shaft 71 via an intermediate planetary gear 76. The carrier 73 is provided with a multi-plate brake 77 that applies braking to the rotation of the carrier 73.
左右のサイドクラッチ６９を入りの状態では直進し、パワステを傾倒させるとブレーキ７７により旋回内側となるキャリア７３に制動を掛けて緩旋回を開始し、更に、ブレーキ７７により旋回内側となるキャリア７３に制動を掛けて旋回内側の車軸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７３に制動を掛けると旋回外側と旋回内側の車軸の回転が逆転してスピンターンとなる。
前記ミッションケース１８は、側面視において、サイドクラッチ６９を機体進行方向前側に配置し、サイドクラッチ６９の後方に遊星歯車機構７０を設ける。サイドクラッチ６９の前方部分のミッションケース１８にはサイドクラッチバルブ７８とブレーキ比例弁７９を設ける。
したがって、ミッションケース１８にサイドクラッチバルブ７８およびブレーキ比例弁７９を設けるので、サイドクラッチバルブ７８とブレーキ比例弁７９をアッシーでの作動確認が容易に可能となり、また、サイドクラッチバルブ７８およびブレーキ比例弁７９がミッションケース１８の前面側にあるので、サイドクラッチバルブ７８およびブレーキ比例弁７９のメンテナンスが容易になる。
When the left and right side clutches 69 are engaged, the vehicle travels straight, and when the power steering is tilted, the brake 77 brakes the carrier 73 on the inner side of the turn to start a gentle turn. When braking is applied and the rotation of the axle on the inside of the turn becomes zero, a brake turn is generated. Further, when braking is applied to the carrier 73, the rotation of the axle on the outside and inside of the turn is reversed to form a spin turn.
In the transmission case 18, the side clutch 69 is disposed on the front side in the aircraft traveling direction in a side view, and a planetary gear mechanism 70 is provided behind the side clutch 69. A side clutch valve 78 and a brake proportional valve 79 are provided in the transmission case 18 in the front portion of the side clutch 69.
Accordingly, since the side clutch valve 78 and the brake proportional valve 79 are provided in the transmission case 18, it is possible to easily check the operation of the side clutch valve 78 and the brake proportional valve 79 at the assembly. Since 79 is on the front side of the transmission case 18, maintenance of the side clutch valve 78 and the brake proportional valve 79 is facilitated.
前記サイドクラッチバルブ７８と前記サイドクラッチ６９とを接続する油路７８Ａは、ミッションケース１８の肉厚部分に形成する。
そのため、サイドクラッチバルブ７８とサイドクラッチ６９とを接続する外部ホースを省略でき、コストダウン・組立工数を低減させる。また、サイドクラッチバルブ７８とサイドクラッチ６９とを接続するホースを省略した分の外部配管スペースを小さくする。
また、左右のサイドクラッチ６９を連結する油路（図示省略）も、ミッションケース１８の肉厚部分に形成する。
ミッションケース１８への油圧接続はＰポートとＴポートの各一本ずつとし、サイドクラッチバルブ７８およびブレーキ比例弁７９は操縦部６のステップの下方に設ける。
そのため、操縦部６のステップ下方の構成品が少なくでき、操縦部６の操作席をオープン可能に構成するのが容易となる。
An oil passage 78 </ b> A connecting the side clutch valve 78 and the side clutch 69 is formed in a thick portion of the transmission case 18.
Therefore, the external hose connecting the side clutch valve 78 and the side clutch 69 can be omitted, and the cost reduction and the assembly man-hour can be reduced. Further, the external piping space corresponding to the omission of the hose connecting the side clutch valve 78 and the side clutch 69 is reduced.
An oil passage (not shown) for connecting the left and right side clutches 69 is also formed in the thick portion of the mission case 18.
The hydraulic connection to the mission case 18 is one for each of the P port and the T port, and the side clutch valve 78 and the brake proportional valve 79 are provided below the step of the control unit 6.
Therefore, the number of components below the step of the control unit 6 can be reduced, and the operation seat of the control unit 6 can be easily configured to be openable.
しかして、前記走行用静油圧式無段変速装置１２の油圧モータ１６のモータ斜板１７の傾斜角度は、通常、モータ斜板切替手段（油圧シリンダ）１９を作動させる切替バルブ９７の作動によって切り替えるが、モータ斜板切替手段１９が故障等の不具合が生じたときは低速側に固定される（図１２）。
また、通常は、切替バルブ９４の切替によって、複動シリンダ９５が作動し、油圧ポンプ１４のポンプ斜板１５の傾斜角度が無段階に変更されて、変速走行する。
これに加えて、走行用ＨＳＴ緊急バルブ８１はパワステ操作用の油圧回路の前記サイドクラッチ６９に接続した油路８２と接続し、複動シリンダ９５とは油路８３により接続する。
断線等により切替バルブ９４が電気的に作動しなくなり、走行不良状態にったとき、手動操作または切替バルブ操作用の緊急レバー（図示なし）の操作により走行用ＨＳＴ緊急バルブ８１を操作し、走行可能とする。
このように、切替バルブ９４が作動しなくなった場合に、走行用ＨＳＴ緊急バルブ８１を作動させて複動シリンダ９５を作動させ、油圧ポンプ１４のポンプ斜板１５の傾斜角度を無段階に変更して、変速走行を可能にする。
Accordingly, the inclination angle of the motor swash plate 17 of the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is normally switched by the operation of the switching valve 97 that operates the motor swash plate switching means (hydraulic cylinder) 19. However, when a malfunction such as a failure occurs in the motor swash plate switching means 19, it is fixed to the low speed side (FIG. 12).
Normally, the double-acting cylinder 95 is actuated by switching the switching valve 94, and the tilt angle of the pump swash plate 15 of the hydraulic pump 14 is changed steplessly so that the vehicle travels at a variable speed.
In addition, the traveling HST emergency valve 81 is connected to an oil passage 82 connected to the side clutch 69 of the hydraulic circuit for power steering operation, and is connected to the double-acting cylinder 95 by an oil passage 83.
When the switching valve 94 is not electrically operated due to disconnection or the like and is in a driving failure state, the driving HST emergency valve 81 is operated by operating the emergency lever (not shown) for manual operation or switching valve operation. Make it possible.
Thus, when the switching valve 94 stops operating, the traveling HST emergency valve 81 is operated to operate the double-acting cylinder 95, and the inclination angle of the pump swash plate 15 of the hydraulic pump 14 is changed steplessly. To enable variable speed travel.
また、図１３は、走行用静油圧式無段変速装置１２の油圧回路のチャージポンプ８５を分流弁８６を介してパワステ操作用の油圧回路の前記サイドクラッチ６９に油路８７により接続した構成を示す
８８はポンプであり、ブレーキ比例弁７９に送油する。
従来はレデュースバルブ減圧してパワステ操作用の油圧回路のサイドクラッチ６９に送油していたため、ポンプ８８の流量を十分に発揮させていなかったので、ポンプ８８からサイドクラッチ６９への送油回路を省略し、他の例えば刈取上下シリンダ等の油圧回路へ回して、ポンプ８８の流量を十分に利用でき、刈取上下の作動速度を速くして、操作性や作業性を向上させる。
また、レデュースバルブも廃止でき、コストメリットがある。
しかして、前記刈取搬送用静油圧式無段変速装置２１内には油圧ポンプ８９と油圧モータ９０が設けられ（図３）、油圧ポンプ８９と油圧モータ９０の油圧回路にはチェックバルブ９１を設けて、油圧ポンプ８９の回転が逆転域になったとき、逆回転を油圧モータ９０へ伝達させないようにしている。
そのため、刈取部４を逆転駆動させることを防止して、刈取部４の破損を防止する。
13 shows a configuration in which the charge pump 85 of the hydraulic circuit of the hydrostatic continuously variable transmission 12 for travel is connected to the side clutch 69 of the hydraulic circuit for power steering operation via an oil passage 87 via a diversion valve 86. Reference numeral 88 denotes a pump which feeds oil to the brake proportional valve 79.
In the past, the reduce valve was depressurized and oil was sent to the side clutch 69 of the hydraulic circuit for power steering operation, so the flow rate of the pump 88 was not fully exhibited. Omitted and turned to another hydraulic circuit such as a cutting upper and lower cylinders, the flow rate of the pump 88 can be fully utilized, and the operating speed of the cutting upper and lower is increased to improve operability and workability.
In addition, the reduce valve can be abolished, and there is a cost merit.
Therefore, a hydraulic pump 89 and a hydraulic motor 90 are provided in the hydrostatic continuously variable transmission 21 for harvesting and conveying (FIG. 3), and a check valve 91 is provided in the hydraulic circuit of the hydraulic pump 89 and the hydraulic motor 90. Thus, when the rotation of the hydraulic pump 89 is in the reverse rotation range, the reverse rotation is not transmitted to the hydraulic motor 90.
Therefore, the cutting unit 4 is prevented from being driven in reverse, and the cutting unit 4 is prevented from being damaged.
刈取搬送用静油圧式無段変速装置２１から刈取部４への伝動回路中にワンウエイクラッチを設ける必要が無く、コストダウンしうるコストメリットを大きくする。
前記刈取搬送用静油圧式無段変速装置２１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からのオイルを分流して供給するように構成する。
したがって、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とチャージポンプ８５を共用するので、コストメリットを高くする。
また、チャージポンプ８５によるオイルの供給は、ラインフィルタ９２を出たあとに分流させる回路に構成する。
したがって、ラインフィルタ９２を共用できるので、夫々専用のラインフィルタ９２を設置する設置スペースや配管を不要にでき、コストメリットを高くし、また、オイル管理も容易になる。
There is no need to provide a one-way clutch in the transmission circuit from the hydrostatic continuously variable transmission 21 for harvesting conveyance to the harvesting unit 4, and the cost merit that can reduce the cost is increased.
The cutting and conveying hydrostatic continuously variable transmission 21 is configured to supply the oil from the charge pump 85 of the traveling hydrostatic continuously variable transmission 12 in a divided manner.
Therefore, since the hydrostatic continuously variable transmission 12 for traveling, the hydrostatic continuously variable transmission 21 for cutting and conveying, and the charge pump 85 are shared, the cost merit is increased.
In addition, the supply of oil by the charge pump 85 is configured as a circuit for diverting the flow after leaving the line filter 92.
Therefore, since the line filter 92 can be shared, the installation space and piping for installing the dedicated line filter 92 can be eliminated, the cost merit is increased, and oil management is facilitated.
前記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は、主変速レバー１３の傾倒角度に応じて、同期させて作動させるが、同期および作動させるための構成は任意であり、例えば、主変速レバーと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をリンク等の機械的構成により連結したり、主変速レバーの傾倒角度を電気的に検出し、この信号により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を電気的に制御するようにしてもよい。 The hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for harvesting and conveying are operated in synchronism in accordance with the tilt angle of the main transmission lever 13, but are configured to synchronize and operate. Is optional. For example, the main transmission lever and the hydrostatic continuously variable transmission device 12 for traveling and the hydrostatic continuously variable transmission device 21 for cutting and conveying are connected by a mechanical structure such as a link, or the inclination of the main transmission lever is tilted. The angle may be detected electrically, and the hydrostatic continuously variable transmission 12 for traveling and the hydrostatic continuously variable transmission 21 for cutting and conveying may be electrically controlled by this signal.
（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.
しかして、走行装置３の走行速度を変速する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するが、更に、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も傾斜角度を二段階に切替可能（切替操作手段の構成は任意）に構成し、低速走行と高速走行との切替え可能に構成しているから、通常走行速度（低速走行側）で刈取作業（標準作業および倒伏作業）を行い、高速走行速度（高速走行側）で走行して移動時間を短縮する。
この場合、走行用静油圧式無段変速装置１２の油圧モータ１６を低速走行に切替えた状態で、主変速レバー１３の最高速位置の車速を設定する速度調整ダイヤル速度調整ダイヤル５１を設けているので、油圧モータ１６を低速走行に切替えて行う刈取作業では、圃場条件や作物条件に応じて設定最高速度を落として作業を行うことができ、作業条件に応じて最適な走行速度で走行させることができ、操作性および作業性を向上させる。
Thus, the traveling hydrostatic continuously variable transmission 12 for shifting the traveling speed of the traveling device 3 increases / decreases in accordance with the tilting operation amount of the main transmission lever 13, but further, the traveling hydrostatic continuously variable transmission for traveling. Since the motor swash plate 17 of the hydraulic motor 16 of the device 12 is also configured to be able to switch the inclination angle in two stages (the configuration of the switching operation means is arbitrary), and is configured to be able to switch between low speed running and high speed running. The cutting operation (standard work and overturning work) is performed at the traveling speed ( low speed traveling side), and the traveling time is shortened by traveling at the high traveling speed (high speed traveling side).
In this case, a speed adjustment dial 51 for setting the vehicle speed at the highest speed position of the main transmission lever 13 is provided in a state where the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to low speed traveling. Therefore, in the cutting work performed by switching the hydraulic motor 16 to the low-speed traveling, the operation can be performed with the set maximum speed being lowered according to the field condition or the crop condition, and the traveling is performed at the optimum traveling speed according to the working condition. Can improve operability and workability.
速度調整ダイヤル５１による主変速レバー１３を最高速位置へ操作したときの最高速度の設定変更（調節）は、油圧モータ１６が低速走行側に切り替えられている場合に有効とし、油圧モータ１６が高速走行側の場合には自動的に速度調整ダイヤル５１による最高速度の設定を無効にし、主変速レバー１３を最高速位置へ操作すれば走行用静油圧式無段変速装置１２が発揮するように設定された範囲内の最高走行速度で走行するように構成しているから、刈取作業では主変速レバー１３を最高速操作したときの最高走行速度を、速度調整ダイヤル５１により作業条件に応じた最適な低速状態で作業を行えるようにでき、作業者の意図に合致した作業状態にでき、操作性および作業性を向上させ、しかも、速度調整ダイヤル５１は油圧モータ１６が低速走行側のとき有効であり、一旦、刈取作業が終了して移動するときには、油圧モータ１６を高速走行側に切り替えればよく、速度調整ダイヤル５１により行っていた減速設定を一々戻す操作を不要にして、高速走行による移動を可能にでき、操作性および作業性を向上させる。 The setting change (adjustment) of the maximum speed when the main speed change lever 13 is operated to the highest speed position by the speed adjustment dial 51 is effective when the hydraulic motor 16 is switched to the low speed traveling side, and the hydraulic motor 16 is operated at a higher speed. In the case of the traveling side, the setting of the maximum speed by the speed adjustment dial 51 is automatically invalidated, and the setting is made so that the traveling hydrostatic continuously variable transmission 12 is exhibited when the main transmission lever 13 is operated to the maximum speed position. In the cutting operation, the maximum traveling speed when the main speed change lever 13 is operated at the highest speed is determined by the speed adjustment dial 51 according to the working conditions. The work can be performed at a low speed, the work can be brought into a work state that matches the operator's intention, and the operability and workability are improved. Is effective when the vehicle is on the low-speed traveling side, and once the mowing operation is finished, the hydraulic motor 16 may be switched to the high-speed traveling side, and the operation of returning the deceleration setting performed by the speed adjustment dial 51 is unnecessary. Thus, movement by high-speed traveling can be performed, and operability and workability are improved.
また、走行用静油圧式無段変速装置１２の油圧モータ１６が低速状態であれば、速度調整ダイヤル５１による走行速度の設定を主変速レバー１３を最高速位置にまで操作したときでも、刈取部４が刈取作業可能な走行速度となるように予め設定でき、誤操作による走行速度の上がりすぎによる刈刃９の刈跡の悪化、藁量の増加による刈取部４の詰まり・破損を防止する。
しかして、前記走行用静油圧式無段変速装置１２の油圧モータ１６を高速走行に切替えた状態で、旋回するとき、自動的に油圧モータ１６のモータ斜板１７を低速走行に切替えるように構成しているので、通常の移動は高速走行で移動して移動時間を短縮し、旋回するときは、走行用静油圧式無段変速装置１２を低速で高出力トルクで出力して、エンジン２２の馬力ドロップを抑制減少させ、走行を安定させ、操作性および作業性を向上させる。
If the hydraulic motor 16 of the traveling hydrostatic continuously variable transmission 12 is in a low speed state, even when the travel speed is set by the speed adjustment dial 51 and the main transmission lever 13 is operated to the maximum speed position, the cutting unit 4 can be set in advance so as to have a traveling speed at which the cutting operation can be performed, and the cutting of the cutting blade 9 due to an excessive increase in the traveling speed due to an erroneous operation is prevented, and the cutting portion 4 is prevented from being clogged or damaged due to an increase in the amount of dredging.
Thus, the motor swash plate 17 of the hydraulic motor 16 is automatically switched to low-speed traveling when turning while the hydraulic motor 16 of the hydrostatic continuously variable transmission 12 for traveling is switched to high-speed traveling. Therefore, the normal movement moves at high speed to shorten the movement time, and when turning, the hydrostatic continuously variable transmission 12 for traveling is output at low speed with high output torque, and the engine 22 Reduces horsepower drop, stabilizes running, and improves operability and workability.
例えば、操縦部６のパワステレバー６０の倒し量が一定以上のとき、または、スピン旋回スイッチスピン旋回スイッチ６１がＯＮのときに、旋回すると、自動的に油圧モータ１６のモータ斜板１７を低速走行に切り替えるので、旋回走行が円滑に行え、操作性および作業性を向上させる。
また、刈取作業の工程で旋回走行に移行する際、エンジン２２の負荷率が低く、旋回してもエンジン２２の回転が低下しない場合は、車速を維持するように構成しているので、旋回開始時の負荷が少ないときは高速旋回して、作業効率を向上させる。
即ち、直進走行に比し旋回走行では走行抵抗が大きくなってエンジン２２の負荷が上昇するが、一方で脱穀装置２等の他の装置部分の負荷が少ないときは、旋回してもエンジン２２の回転が低下しないことあり、このときは車速を維持して、移動時間を短縮して作業性を向上させる。
この場合、作業者が減速操作したときは、作業者の操作を優先して減速する。
また、旋回するときにエンジン２２の負荷率が高い場合は、パワステレバー６０の倒し量に応じて車速を減速するように構成するから、エンジン２２の負荷が高いときは主変速レバー１３によらずにパワステレバー６０の倒し量に応じて自動的に車速を減速することによって、エンジン２２の回転が落ちるのを抑制減少させ、旋回走行を円滑に行うと共に、パワステレバー６０の操作だけで旋回操作および減速操作を行って、操作性および作業性を向上させる。
For example, when the amount of killing of Pas Wasutereba 60 of steering unit 6 is more than a predetermined, or when a spin turn switch spin turn switch 61 is ON, when turning, automatically low-speed running of the motor swash plate 17 of hydraulic motor 16 Thus, the vehicle can smoothly turn and improve operability and workability.
In addition, when shifting to turning during the mowing process, if the load factor of the engine 22 is low and the rotation of the engine 22 does not decrease even after turning, the vehicle speed is maintained, so turning starts. When the load on the hour is light, turn at high speed to improve work efficiency.
In other words, the running resistance increases and the load on the engine 22 increases in the cornering as compared with the straight traveling. On the other hand, when the load on the other devices such as the threshing device 2 is small, the engine 22 In some cases, the rotation does not decrease. At this time, the vehicle speed is maintained, the traveling time is shortened, and workability is improved.
In this case, when the operator performs a deceleration operation, the operator's operation is preferentially decelerated.
Further, when the engine 22 is turning, when the load factor of the engine 22 is high, the vehicle speed is reduced according to the amount of tilt of the power steering lever 60. Therefore, when the load of the engine 22 is high, the main transmission lever 13 is not used. Further, by automatically decelerating the vehicle speed in accordance with the amount of tilt of the power steering lever 60, the rotation of the engine 22 is suppressed and reduced, and the vehicle can smoothly turn. Decelerate operation to improve operability and workability.
即ち、旋回するときにエンジン２２の負荷率が高い場合でも、パワステレバー６０の倒し量に応じて車速を減速するので、エンジン２２の負荷が高くてもパワステレバー６０の倒し量における最高速度まで自動的に車速を減速するので、エンジン２２の回転が落ちるのを抑制減少させつつ、高速で旋回走行を行える。
しかして、走行用静油圧式無段変速装置１２の速度調整ダイヤル５１による走行車速の設定制御は、走行用静油圧式無段変速装置１２による走行速度の上限設定の変更であり、この主変速レバー１３の操作による走行速度に同調するように刈取部４の回転を自動制御すればよいので、刈取部４の回転を同調させるための構成は任意であり、走行装置３と刈取部４の同調制御は走行用静油圧式無段変速装置１２単独でも行えるが本願では走行用静油圧式無段変速装置１２とは別個の刈取部４の専用の刈取搬送用静油圧式無段変速装置２１により行っているので、この刈取部４の専用の刈取搬送用静油圧式無段変速装置２１による特有の作用について以下詳述する。
That is, even when the load factor of the engine 22 is high when making a turn, the vehicle speed is reduced according to the amount of tilting of the power steering lever 60. Therefore, even if the load of the engine 22 is high, the maximum speed in the tilting amount of the power steering lever 60 is automatically achieved. Since the vehicle speed is reduced, the turning speed of the engine 22 can be reduced and suppressed while the vehicle 22 is turning at high speed.
Thus, the travel vehicle speed setting control by the speed adjustment dial 51 of the travel hydrostatic continuously variable transmission 12 is a change in the upper limit setting of the travel speed by the travel hydrostatic continuously variable transmission 12. Since the rotation of the cutting unit 4 may be automatically controlled so as to synchronize with the traveling speed by the operation of the lever 13, the configuration for synchronizing the rotation of the cutting unit 4 is arbitrary, and the synchronization of the traveling device 3 and the cutting unit 4 is performed. Although the control can be performed by the traveling hydrostatic continuously variable transmission 12 alone, in the present application, a dedicated cutting and conveying hydrostatic continuously variable transmission 21 of the cutting unit 4 separate from the traveling hydrostatic continuously variable transmission 12 is used. Since the operation is performed, the specific action of the mowing unit 4 for exclusive use of the mowing and conveying hydrostatic continuously variable transmission 21 will be described in detail below.
走行装置３の走行速度は主変速レバー１３の操作により走行速度を変速し、この走行速度に対して、例えば、図２の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より上昇率の高い加速をするようにした倒伏作業ラインＢとを選択的に採用して、刈取部４およびシンクロ用前側供給搬送装置１１を駆動させる。
そして、シンクロ用前側供給搬送装置１１は植立状態で刈取部４から搬送される穀稈の姿勢を横倒し状態に変えて引き継ぐので、シンクロ用前側供給搬送装置１１と穀稈供給搬送装置１０との間で搬送速度に若干の差があっても、搬送姿勢が横向きなので、円滑に引き継げる。
即ち、実施例の刈取部４およびシンクロ用前側供給搬送装置１１は、刈取搬送専用の刈取搬送用静油圧式無段変速装置２１により走行速度に同調させて変速しているので、脱穀装置２と穀稈供給搬送装置１０をエンジン２２からの一定駆動回転で駆動して脱穀効率を向上させつつ、刈取部４およびシンクロ用前側供給搬送装置１１の回転を走行速度に同調させて刈取搬送用静油圧式無段変速装置２１により変速して、穀稈供給搬送装置１０への引継を円滑・確実にする。
The travel speed of the travel device 3 is changed by operating the main speed change lever 13, and the standard work line A for increasing the transmission rotation at a predetermined rate relative to the travel speed of FIG. Then, the lowering work line B that is accelerated at a higher rate than that of the standard work line A is selectively adopted to drive the cutting unit 4 and the synchro front supply / conveyance device 11.
And since the front supply conveyance apparatus 11 for synchros changes the attitude | position of the grain straw conveyed from the cutting part 4 in a planting state to a horizontal state, it takes over, and the front supply conveyance apparatus 11 for synchros and the grain supply and conveyance apparatus 10 Even if there is a slight difference in the conveyance speed between them, the conveyance posture is sideways, so it can be taken over smoothly.
That is, the reaping unit 4 and the synchro front supply / conveyance device 11 of the embodiment are shifted in synchronism with the traveling speed by the chopping / conveying hydrostatic continuously variable transmission 21 dedicated for reaping / conveying. The cereal supply / conveyance device 10 is driven by a constant driving rotation from the engine 22 to improve the threshing efficiency, and the rotation of the reaping portion 4 and the front-side supply / conveyance device 11 for synchronization is synchronized with the traveling speed, and the hydrostatic pressure for reaping / conveyance The speed is changed by the type continuously variable transmission 21 so that the transfer to the grain supply / conveyance device 10 is smooth and reliable.
また、刈取部４およびシンクロ用前側供給搬送装置１１への伝動回転は、刈取搬送用静油圧式無段変速装置２１により変速するので、通常は走行速度に同調させて変速するが、所定条件のときは、刈取搬送用静油圧式無段変速装置２１単独で刈取部４および／またはシンクロ用前側供給搬送装置１１を駆動させることができるので、作業態様を広げ、汎用性を向上させられる。
即ち、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るので、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、刈取搬送用静油圧式無段変速装置２１単独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を駆動させることができるので、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する供給作業を容易にでき、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 transmission rotation to the cutting unit 4 and the synchro front supply / conveyance device 11 is shifted by the chopping / conveying hydrostatic continuously variable transmission 21, so that the transmission is normally synchronized with the traveling speed. When this is done, the harvesting part 4 and / or the front supply / conveyor 11 for synchronization can be driven by the hydrostatic continuously variable transmission 21 for harvesting and conveying, so that the working mode can be expanded and the versatility can be improved.
That is, even during the predetermined travel speed from the state where the machine body is stopped, the cutting part 4 and the front supply / conveyor 11 for synchronization can be driven at a sufficient number of revolutions by the hydrostatic continuously variable transmission 21 for cutting and conveying. The mowing unit 4 and the threshing device 2 are driven stably immediately after the start of traveling, and the mowing work and the threshing work can be performed stably and reliably.
Further, when the rotation of the traveling hydrostatic continuously variable transmission 12 from the traveling hydrostatic continuously variable transmission 12 to the traveling device 3 is stopped, the synchro front supply / conveyor 11 is driven by the cutting and conveying hydrostatic continuously variable transmission 21 alone. Since the front supply / conveyor device 11 for synchro can be driven in the traveling stop state, the supply operation for supplying hand-cut cereals to the front supply / conveyor device 11 for synchros and the cereal supply / conveyor device 10 can be facilitated and harvested. In addition, the workability and operability of the threshing operation can be improved.
しかして、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 of the engine 22 is transmitted to the intermediate pulley 28, and the intermediate pulley 28 transmits the rotation to the intermediate transmission shaft 31 of the case via the intermediate shaft 29 and the intermediate gear 30. And the cereal supply / conveyance intermediate output shaft 41 and the hydrostatic continuously variable transmission 21 for harvesting / conveying.
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が刈取ＨＳＴ出力軸３８により出力され、刈取ＨＳＴ出力軸３８は刈取用中間出力軸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、特に、刈取搬送用静油圧式無段変速装置２１により刈取部４およびシンクロ用前側供給搬送装置１１を走行速度に同調させる構成であっても、走行用静油圧式無段変速装置１２単独により走行速度に同調させる構成に組み合わせることや、各種スイッチ等の組み合わせも含めて、実施例の相互の組合せは可能であり、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。特に、走行装置３と刈取部４の同調制御させる構成は任意であり、刈取搬送用静油圧式無段変速装置２１の存在は要件ではない。
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 transfer intermediate output shaft 41 is input to the pump of the chopping transfer hydrostatic continuously variable transmission 21 and the rotation shifted from the motor of the chopping transfer hydrostatic continuously variable transmission 21 is the cutting HST output shaft 38. The mowing HST output shaft 38 drives and rotates the mowing unit 4 and the synchro front supply / transport device 11 by the mowing intermediate output shaft 39 and the transport synchro output shaft 40.
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. In particular, even when the cutting unit 4 and the synchro front supply / conveyor 11 are synchronized with the traveling speed by the hydrostatic continuously variable transmission 21 for cutting and transporting, the traveling hydrostatic continuously variable transmission 12 for traveling is used alone. It is possible to combine the embodiments in combination with a configuration that is tuned to the speed and combinations of various switches, etc., and these expressions are not intended to limit the configuration and operation, etc. Of course, there are cases where effects are produced. In particular, the configuration in which the traveling device 3 and the reaping unit 4 are synchronously controlled is arbitrary, and the existence of the hydrostatic continuously variable transmission 21 for reaping and conveying is not a requirement.
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、３８…刈取ＨＳＴ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、４６…刈取中間入力プーリー、４７…ベルト、５０…ギヤケース、５１…速度調整ダイヤル、５５…本機コートローラ、５６…ＨＳＴコントローラ、５７…エンジンコントローラ、５８…車速センサー、６０…パワステレバー、６１…スピン旋回スイッチ、６２…エンジン回転センサ、６５…入力軸、６６…出力歯車、６７…サイドクラッチ軸、６８…受動歯車、６９…サイドクラッチ、７０…遊星歯車機構、７１…駆動軸、７３…キャリア、７４…遊星歯車、７５…遊星歯車、７６…中間遊星歯車、７７…ブレーキ、７８…サイドクラッチバルブ、７９…ブレーキ比例弁、８０…切替バルブ、８１…走行用ＨＳＴ緊急バルブ、８２…油路、８３…油路、８５…チャージポンプ、８６…分流弁、８７…油路、８９…油圧ポンプ、９０…油圧モータ、９１…チェックバルブ、９２…ラインフィルタ、９３…ソレノイド、９４…切替バルブ、９５…複動シリンダ、９６…ソレノイド、９７…切替バルブ。 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 ... treatment cylinder, 35 ... processing cylinder, 36 ... intermediate gear for cutting, 37 ... cutting HST input shaft, 38 ... cutting HST output shaft, 39 ... intermediate output shaft for cutting, 40 ... output shaft for conveying synchronization, 41 ... grain稈 Supply conveyance intermediate output shaft, 2 ... Kara, 43 ... Drive gear, 44 ... Cutting threshing clutch, 45 ... Cutting intermediate output pulley, 46 ... Cutting intermediate input pulley, 47 ... Belt, 50 ... Gear case, 51 ... Speed adjustment dial, 55 ... Coated roller, 56 ... HST controller, 57 ... Engine controller, 58 ... Vehicle speed sensor, 60 ... Power steering lever, 61 ... Spin rotation switch, 62 ... Engine rotation sensor, 65 ... Input shaft, 66 ... Output gear, 67 ... Side clutch shaft, 68 ... Passive gear, 69 ... side clutch, 70 ... planetary gear mechanism, 71 ... drive shaft, 73 ... carrier, 74 ... planetary gear, 75 ... planetary gear, 76 ... intermediate planetary gear, 77 ... brake, 78 ... side clutch valve, 79 ... Brake proportional valve, 80 ... Switch valve, 81 ... HST emergency valve for travel, 82 ... Oil path, 83 ... Oil path 85 ... Charge pump, 86 ... Diversion valve, 87 ... Oil passage, 89 ... Hydraulic pump, 90 ... Hydraulic motor, 91 ... Check valve, 92 ... Line filter, 93 ... Solenoid, 94 ... Switching valve, 95 ... Double acting cylinder, 96 ... Solenoid, 97 ... Switching valve.
Claims (5)
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| JP2012036288A (en) * | 2010-08-06 | 2012-02-23 | Sumitomo Bakelite Co Ltd | Silicone rubber-based curable composition and medical tube |
| JP4892104B1 (en) * | 2011-01-20 | 2012-03-07 | 株式会社クボタ | Powder spraying device |
| JP6245749B2 (en) * | 2014-02-13 | 2017-12-13 | ヤンマー株式会社 | Work vehicle |
| JP6184380B2 (en) * | 2014-08-01 | 2017-08-23 | 株式会社クボタ | Speed control device for traveling work vehicle |
| WO2023199581A1 (en) * | 2022-04-13 | 2023-10-19 | 株式会社やまびこ | Unmanned travelling work machine system |
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| JPH0265727A (en) * | 1988-08-30 | 1990-03-06 | Yanmar Agricult Equip Co Ltd | Conveying device of grain culm in combine |
| JP3902343B2 (en) * | 1998-10-01 | 2007-04-04 | ヤンマー農機株式会社 | Mobile farm machine |
| JP2000188935A (en) * | 2000-01-01 | 2000-07-11 | Iseki & Co Ltd | Carrying transmission mechanism for combine harvester |
| JP4529920B2 (en) * | 2006-02-28 | 2010-08-25 | 井関農機株式会社 | Combine |
| JP4643608B2 (en) * | 2007-05-07 | 2011-03-02 | ヤンマー株式会社 | Combine |
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