以下、本発明の実施例を図面に基づいて詳述する。図１はコンバインの全体の左側面図、図２は同平面図、図３は同右側面図であり、図中１は左右一対の走行クローラ２を装設する左右一対のトラックフレーム、３は前記の左右トラックフレーム１に架設する機台、４はフィードチェン５を左側に張架し扱胴６及び処理胴６ａを内蔵している脱穀機である脱穀部、７は引起機構８及び刈刃９及び穀稈搬送機構１０などを備える刈取部、１１は刈取フレーム１２を介して刈取部７を昇降させる油圧昇降シリンダ、１３は排藁チェン１４終端を臨ませる排藁処理部、１５は脱穀部４からの穀粒を揚穀筒１５ａを介して搬入する穀物タンク、１６・１７は前記タンク１５の穀粒を機外に搬出する縦及び横排出オーガ、１８は運転操作ハンドル１９及び運転席２０を備える運転キャビン、２１は運転キャビン１８下方に設けるエンジンであり、連続的に穀稈を刈取って脱穀するように構成している。
Embodiments of the present invention will be described below in detail with reference to the drawings. 1 is a left side view of the entire combine, FIG. 2 is a plan view thereof, and FIG. 3 is a right side view thereof. In FIG. 1, 1 is a pair of left and right track frames for mounting a pair of left and right traveling crawlers. A machine base erected on the left and right track frames 1, a threshing unit 4 is a threshing machine that stretches the feed chain 5 on the left side and incorporates a handling cylinder 6 and a processing cylinder 6 a, 7 is a pulling mechanism 8 and a cutting blade 9, a harvesting unit including the grain feeder 10, 11 is a hydraulic lifting cylinder that raises and lowers the harvesting unit 7 via the harvesting frame 12, 13 is a slaughtering unit that faces the terminal end of the sewage chain 14, and 15 is a threshing unit. 4 is a grain tank for carrying grains from the milling cylinder 15a, 16 and 17 are vertical and lateral discharge augers for carrying the grains of the tank 15 out of the machine, and 18 are a driving operation handle 19 and a driver seat 20. Driving cabin with 21 driving key An engine that bin 18 provided below, are configured to threshing continuously harvests culms.
さらに、図４乃至図９に示す如く、機台３前側で左右の走行クローラ２の間にミッションケース２２を配設させ、ミッションケース２２とエンジン２１を略直列に前後に設け、ミッションケース２２を介して走行クローラ２にエンジン２１の駆動力を伝えると共に、脱穀部４前側の機台３上面に左右の支持台２３・２４を立設させ、支持台２３・２４に刈取フレーム１２を介して刈取部７を昇降自在及び横移動可能に設ける。また、支持台２３・２４後側の機台３上面にカウンタケース２５を設け、脱穀部４及び刈取部７にカウンタケース２５を介してエンジン２１の駆動力を伝える。
Further, as shown in FIGS. 4 to 9, a mission case 22 is disposed between the left and right traveling crawlers 2 on the front side of the machine base 3, the mission case 22 and the engine 21 are provided substantially in series, and the mission case 22 is provided. The driving force of the engine 21 is transmitted to the traveling crawler 2 via the left and right support bases 23 and 24 erected on the upper surface of the machine base 3 on the front side of the threshing unit 4, and the support bases 23 and 24 are cut through the cutting frame 12. The part 7 is provided so as to be movable up and down and laterally movable. Further, a counter case 25 is provided on the upper surface of the machine base 3 on the rear side of the support bases 23 and 24, and the driving force of the engine 21 is transmitted to the threshing unit 4 and the mowing unit 7 through the counter case 25.
さらに、ミッションケース２２側方の機台３にキャビン前フレーム２６を立設させ、キャビン１８のステップフレーム２７前部を前フレーム２６上部に回動支点軸２８を介して設け、支点軸２８回りにキャビン１８を前方に回動自在に支持させると共に、右の支持台２４に左のキャビン後フレーム２９を立設させ、機台３に立設させる右のキャビン後フレーム３０との間の機台３上面にエンジン２１を設け、エンジン２１をエンジンルームカバー３１で覆う。また、前記カバー３１の上方で左右の後フレーム２９・３０上部をキャビン横フレーム３２によって連結させ、キャビン横フレーム３２に台ブラケット３３を設け、キャビン１８のステップフレーム２７後部を横フレーム３２に上載させて係脱自在に固定させると共に、右の支持台２４と前フレーム２６の間に水平連結フレーム３４を固定させ、水平連結フレーム３４中間と横フレーム３２中間に傾斜連結フレーム３５を固定させ、連結フレーム３４・３５によってフレーム剛性を確保する。また、左の後フレーム２９にオーガ支柱３６を連結させて上側にオーガレスト３７を設け、昇降及び旋回自在に設ける排出オーガ１７をオーガレスト３７の本機収納位置に支持させる。
Further, the cabin front frame 26 is erected on the machine base 3 on the side of the transmission case 22, and the front portion of the step frame 27 of the cabin 18 is provided on the upper portion of the front frame 26 via the rotation fulcrum shaft 28. The cabin 18 is rotatably supported forward, and the left cabin rear frame 29 is erected on the right support 24 and the machine base 3 between the right cabin rear frame 30 erected on the machine base 3. An engine 21 is provided on the upper surface, and the engine 21 is covered with an engine room cover 31. Further, the upper left and right rear frames 29 and 30 are connected to each other by a cabin lateral frame 32 above the cover 31, a base bracket 33 is provided on the cabin lateral frame 32, and the rear portion of the step frame 27 of the cabin 18 is mounted on the lateral frame 32. The horizontal connection frame 34 is fixed between the right support base 24 and the front frame 26, and the inclined connection frame 35 is fixed between the horizontal connection frame 34 and the horizontal frame 32. Frame rigidity is secured by 34 and 35. In addition, an auger support 36 is connected to the left rear frame 29 to provide an auger rest 37 on the upper side, and the discharge auger 17 provided so as to be able to move up and down and turn is supported at the machine storage position of the auger rest 37.
さらに、図１０乃至図１２に示す如く、前記走行クローラ２を駆動するミッションケース２２は、１対の油圧走行ポンプ３８及び油圧走行モータ３９を設けて走行主変速用の油圧式無段変速機構を形成する走行変速部材４０と、１対の油圧旋回ポンプ４１及び油圧旋回モータ４２を設けて旋回用の油圧式無段変速機構を形成する旋回部材４３とを備え、前記エンジン２１の出力軸４４にミッションケース２２の入力軸４５を介して連結させて前記各ポンプ３８・４１を駆動するように構成している。
Further, as shown in FIGS. 10 to 12, the transmission case 22 for driving the traveling crawler 2 is provided with a pair of hydraulic traveling pumps 38 and a hydraulic traveling motor 39 to provide a hydraulic continuously variable transmission mechanism for traveling main transmission. A traveling speed change member 40 to be formed, and a turning member 43 which forms a hydraulic continuously variable transmission mechanism for turning by providing a pair of hydraulic turning pumps 41 and a hydraulic turning motor 42, are provided on the output shaft 44 of the engine 21. The pumps 38 and 41 are configured to be connected via an input shaft 45 of the mission case 22.
また、前記走行モータ３９のモータ軸４６に、副変速機構４７及び差動機構４８を介して左右走行クローラ２の各駆動輪４９を連動連結させるもので、前記差動機構４８は左右対称の１対の遊星ギヤ機構５０を有し、各遊星ギヤ機構５０は１つのサンギヤ５１と、該サンギヤ５１の外周で噛合う３つのプラネタリギヤ５２と、これらプラネタリギヤ５２に噛合うリングギヤ５３などで形成している。
Further, each drive wheel 49 of the left and right traveling crawler 2 is interlockedly connected to the motor shaft 46 of the traveling motor 39 via a sub-transmission mechanism 47 and a differential mechanism 48. Each planetary gear mechanism 50 includes a single sun gear 51, three planetary gears 52 that mesh with the outer periphery of the sun gear 51, and a ring gear 53 that meshes with these planetary gears 52. .
前記プラネタリギヤ５２は、サンギヤ５１の遊転軸５４と同軸線上の車軸５５のキャリヤ５６にそれぞれ回転自在に軸支させ、左右のサンギヤ５１を挾んで左右のキャリヤ５６を対向配置させると共に、前記リングギヤ５３は各プラネタリギヤ５２に噛み合う内歯を有して車軸５５に回転自在に軸支させ、車軸５５を延設して駆動輪４９を軸支させている。
The planetary gear 52 is rotatably supported by a free-wheeling shaft 54 of the sun gear 51 and a carrier 56 of an axle 55 on the same axis, so that the left and right carriers 56 are opposed to each other with the left and right sun gears 51 therebetween. Has internal teeth meshing with each planetary gear 52 and is rotatably supported on an axle 55. The axle 55 is extended to support a drive wheel 49.
また、走行変速部材４０は、走行ポンプ３８の斜板角度の変更により走行モータ３９の正逆回転と回転数の制御を行うもので、走行モータ３９の回転を、モータ軸４６と副変速機構４７の低速及び高速ギヤ５７・５８とブレーキ軸５９と分岐軸６０を介して、左右のリングギヤ５３に伝達して左右のキャリヤ５６を回転させるように構成している。また前記ブレーキ軸５９に駐車ブレーキ６１を設けると共に、刈取部７に回転力を伝達する刈取駆動プーリ６２を前記モータ軸４６に設け、刈取部７を車速同調速度で駆動させる。
The traveling speed change member 40 controls forward / reverse rotation and rotational speed of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. The traveling speed of the traveling motor 39 is controlled by the motor shaft 46 and the auxiliary transmission mechanism 47. The low-speed and high-speed gears 57 and 58, the brake shaft 59, and the branch shaft 60 are transmitted to the left and right ring gears 53 to rotate the left and right carriers 56. A parking brake 61 is provided on the brake shaft 59, and a cutting drive pulley 62 that transmits a rotational force to the cutting unit 7 is provided on the motor shaft 46 to drive the cutting unit 7 at a vehicle speed synchronization speed.
上記のように、前記分岐軸６０を介しリングギヤ５３に伝達された走行モータ３９の駆動力を、左右の遊星ギヤ機構５０を介して左右キャリヤ５６に伝達させると共に、左右キャリヤ５６に伝達された回転を左右の駆動輪４９にそれぞれ伝え、左右走行クローラ２を同一方向に同一速度で駆動するように構成している。
As described above, the driving force of the traveling motor 39 transmitted to the ring gear 53 via the branch shaft 60 is transmitted to the left and right carriers 56 via the left and right planetary gear mechanisms 50, and the rotation transmitted to the left and right carriers 56. Is transmitted to the left and right drive wheels 49, respectively, so that the left and right traveling crawlers 2 are driven in the same direction and at the same speed.
さらに、旋回用の油圧式無段変速機構で形成する旋回部材４３は、旋回ポンプ４１の斜板角度の変更により旋回モータ４２の正逆回転と回転数の制御を行うもので、操向出力ブレーキ６３を設けるモータ軸６４と、操向出力クラッチ６５を設けるクラッチ軸６６と、前記の左右サンギヤ５１に常時噛合させる左右入力ギヤ６７・６８を設け、旋回モータ４２の出力用の前記モータ軸６４及び操向出力クラッチ６５を介してクラッチ軸６６を連結させ、クラッチ軸６６に正転ギヤ６９及び逆転ギヤ７０を介して左右の入力ギヤ６７・６８を連結させる。そして、右側のサンギヤ５１に正転ギヤ６９を介してモータ４２回転力を伝え、また左側のサンギヤ５１に逆転ギヤ７０を介してモータ４２回転を伝え、旋回モータ４２を正転（逆転）時、左右同一回転数で、左サンギヤ５１を逆転（正転）させ、かつ右サンギヤ５１を正転（逆転）させ、左右走行クローラ２を逆方向に同一速度で駆動するように構成している。
Further, the turning member 43 formed by the hydraulic continuously variable transmission mechanism for turning controls the forward / reverse rotation and the rotational speed of the turning motor 42 by changing the swash plate angle of the turning pump 41. A motor shaft 64 provided with 63, a clutch shaft 66 provided with a steering output clutch 65, and left and right input gears 67 and 68 that are always meshed with the left and right sun gears 51. The clutch shaft 66 is connected via the steering output clutch 65, and the left and right input gears 67 and 68 are connected to the clutch shaft 66 via the forward rotation gear 69 and the reverse rotation gear 70. Then, the rotational force of the motor 42 is transmitted to the right sun gear 51 via the forward rotation gear 69, and the rotation of the motor 42 is transmitted to the left sun gear 51 via the reverse rotation gear 70. The left sun gear 51 is reversely rotated (forward rotation) and the right sun gear 51 is rotated forward (reverse rotation) at the same left and right rotational speeds, and the left and right traveling crawlers 2 are driven in the reverse direction at the same speed.
而して、旋回モータ４２を停止させて左右サンギヤ５１を静止固定させた状態で、走行モータ３９を駆動すると、走行モータ３９の回転は左右のリングギヤ５３に同一回転数で伝達され、左右遊星ギヤ機構５０のキャリヤ５６を介して左右の走行クローラ２が左右同一回転方向で同一回転数によって駆動され、機体の前後方向直進走行が行われる。一方、走行モータ３９を停止させて左右のリングギヤ５３を静止固定させた状態で、旋回モータ４２を正逆回転駆動すると、左側の遊星ギヤ機構５０が正或いは逆回転、また右側の遊星ギヤ機構５０が逆或いは正回転し、左右走行クローラ２を逆方向に駆動し、機体を左或いは右に旋回させる。また、走行モータ３９を駆動させながら、旋回モータ４２を駆動することにより、機体が左右に旋回して進路が修正されるもので、機体の旋回半径は旋回モータ４２の出力回転数によって決定される。
Thus, when the traveling motor 39 is driven in a state where the turning motor 42 is stopped and the left and right sun gears 51 are stationary, the rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 at the same rotational speed, and the left and right planetary gears. The left and right traveling crawlers 2 are driven at the same rotational speed in the same direction in the left and right directions through the carrier 56 of the mechanism 50, and the vehicle body travels straight forward and backward. On the other hand, when the turning motor 42 is driven to rotate forward and reverse with the traveling motor 39 stopped and the left and right ring gears 53 stationary, the left planetary gear mechanism 50 rotates forward or reverse, and the right planetary gear mechanism 50. Rotates in the reverse or forward direction, drives the left and right traveling crawler 2 in the reverse direction, and turns the aircraft to the left or right. Further, by driving the turning motor 42 while driving the traveling motor 39, the aircraft turns left and right to correct the course, and the turning radius of the aircraft is determined by the output rotation speed of the turning motor 42. .
また、前記入力軸４５にファン軸７１を連結させ、ファン軸７１によってエンジン２１水冷用のラジエータの冷却ファン７２を駆動させると共に、前記の走行及び旋回ポンプ３８・４１の各ポンプ軸７３・７４にギヤ群７５を介して前記ファン軸７１を連結させ、各ポンプ３８・４１に入力軸４５を連結させると共に、走行ポンプ３８のポンプ軸７３と、走行モータ３９のモータ軸４６を、車速定速クラッチ７６を介して連結させる定速軸７７を設け、車速定速クラッチ７６を入にしたとき、定速軸７７を介してポンプ軸７３とモータ軸４６をギヤ連結させ、走行変速部材４０を介することなく、入力軸４５の回転を副変速機構４７に伝え、エンジン２１の定速回転によって左右の走行クローラ２を駆動させ、略一定の車速で走行して収穫作業などを行わせる。なお、旋回ポンプ軸７４上にチャージポンプ７８を設けて駆動する。
Further, a fan shaft 71 is connected to the input shaft 45, and a cooling fan 72 of a radiator for cooling the engine 21 is driven by the fan shaft 71, and the pump shafts 73 and 74 of the traveling and swirling pumps 38 and 41 are connected to the pump shafts 73 and 74. The fan shaft 71 is connected via the gear group 75, the input shaft 45 is connected to each pump 38 and 41, and the pump shaft 73 of the traveling pump 38 and the motor shaft 46 of the traveling motor 39 are connected to the vehicle speed constant speed clutch. When the constant speed shaft 77 to be connected via 76 is provided and the vehicle speed constant speed clutch 76 is turned on, the pump shaft 73 and the motor shaft 46 are gear connected via the constant speed shaft 77 and the traveling speed change member 40 is interposed. Instead, the rotation of the input shaft 45 is transmitted to the sub-transmission mechanism 47, the left and right traveling crawlers 2 are driven by the constant speed rotation of the engine 21, and the harvesting is performed at a substantially constant vehicle speed. To perform the like. A charge pump 78 is provided on the swing pump shaft 74 and driven.
さらに、図１２に示す如く、走行ポンプ３８の斜板７９角度を変更して出力調整する主変速シリンダ８０と、主変速レバー８１及び操向ハンドル１９に連結させて切換える変速バルブ８２と、走行ポンプ３８出力を一定量減速するバルブ８３を設け、前記チャージポンプ７８を各バルブ８２・８３を介して主変速シリンダ８０に油圧接続させるもので、主変速レバー８１によって変速バルブ８２を切換え、主変速シリンダ８０を作動させて走行ポンプ３８の斜板７９角度を変更させ、走行モータ３９のモータ軸４６の回転数を無段階に変化させたり、逆転させる走行変速動作を行わせ、また前記斜板７９の角度調節動作によって変速バルブ８２が中立復帰するフィードバック動作を行わせ、主変速レバー８１の操作量に比例させて前記斜板７９角度を変化させ、走行モータ３９の回転数を変化させて車速を変更させる。
Further, as shown in FIG. 12, a main transmission cylinder 80 that adjusts the output by changing the angle of the swash plate 79 of the traveling pump 38, a transmission valve 82 that is connected to the main transmission lever 81 and the steering handle 19, and a traveling pump. 38, a valve 83 for decelerating the output by a certain amount is provided, and the charge pump 78 is hydraulically connected to the main transmission cylinder 80 via the valves 82 and 83. The main transmission lever 81 switches the transmission valve 82, and the main transmission cylinder 80 is operated to change the angle of the swash plate 79 of the traveling pump 38, to change the rotational speed of the motor shaft 46 of the traveling motor 39 steplessly or to perform a traveling shift operation that reverses the rotation. The swash plate 7 is made proportional to the operation amount of the main transmission lever 81 by performing a feedback operation in which the transmission valve 82 is neutrally returned by the angle adjustment operation. The angle is varied, by varying the rotation speed of the traveling motor 39 to change the vehicle speed.
また、走行モータ３９の斜板８４角度を変更して出力調整する副変速シリンダ８５を設け、前記チャージポンプ７８に電磁副変速バルブ８６を介して副変速シリンダ８５を油圧接続させ、副変速バルブ８６が中立のときに副変速シリンダ８５を油タンクであるミッションケース２２に短絡させ、走行モータ３９の斜板８４角度を主回路油圧によって変化させると共に、副変速バルブ８６の切換によって斜板８４角度を強制的に変化させ、走行モータ３９の出力を高速または低速に変更させる。
Further, a sub-transmission cylinder 85 for adjusting the output by changing the angle of the swash plate 84 of the traveling motor 39 is provided, and the sub-transmission cylinder 85 is hydraulically connected to the charge pump 78 via the electromagnetic sub-transmission valve 86. When the engine is neutral, the auxiliary transmission cylinder 85 is short-circuited to the transmission case 22 which is an oil tank, the angle of the swash plate 84 of the traveling motor 39 is changed by the main circuit oil pressure, and the angle of the swash plate 84 is changed by switching the auxiliary transmission valve 86. The output of the traveling motor 39 is changed to a high speed or a low speed by forcibly changing.
さらに、旋回ポンプ４１の斜板８７角度を変更して出力調整する旋回シリンダ８８を設け、操向ハンドル１９及び主変速レバー８１に連結させて切換える旋回バルブ８９並びに電磁自動操向バルブ９０を介してチャージポンプ７８を旋回シリンダ８８に油圧接続させ、操向ハンドル１９によって旋回バルブ８９を切換え、旋回シリンダ８８を作動させて旋回ポンプ４１の斜板８７角度を変更させ、旋回モータ４２のモータ軸６４の回転数を無段階に変化させたり、逆転させる左右旋回動作を行わせ、また前記斜板８７の角度調節動作によって旋回バルブ８９が中立復帰するフィードバック動作を行わせ、操向ハンドル１９の操作量に比例させて前記斜板８７角度を変化させ、旋回モータ４２の回転数を変化させて左右旋回角度を変更させる。
Further, a slewing cylinder 88 for adjusting the output by changing the angle of the swash plate 87 of the slewing pump 41 is provided, and is connected via the slewing valve 89 and the electromagnetic automatic steering valve 90 which are switched by being connected to the steering handle 19 and the main transmission lever 81. The charge pump 78 is hydraulically connected to the turning cylinder 88, the turning valve 89 is switched by the steering handle 19, the turning cylinder 88 is operated to change the angle of the swash plate 87 of the turning pump 41, and the motor shaft 64 of the turning motor 42 is changed. A left / right turning operation that changes the rotation speed steplessly or reversely is performed, and a feedback operation in which the turning valve 89 is neutrally returned by an angle adjustment operation of the swash plate 87 is performed. The angle of the swash plate 87 is changed proportionally, and the rotation speed of the turning motor 42 is changed to change the left / right turning angle.
また、主変速レバー８１が中立以外の位置に操作され、操向ハンドル１９が直進以外に操作されることにより、主変速レバー８１の操作方向と操作量に比例させて走行ポンプ３８の油圧出力を増減させ、油圧モータ３９を正逆転または増減速させて前後進速度（車速）を変更させると共に、主変速レバー８１の操作量に比例させて旋回ポンプ４１出力を変化させるもので、高速側走行変速によって旋回半径を自動的に小さくし、かつ低速側走行変速によって旋回半径を自動的に大きくし、操向ハンドル１９の一定操作によって走行速度に関係なく左右走行クローラ２の旋回半径を略一定に維持させ、作業走行速度の変更並びに未刈り穀稈列などに機体を沿わせる進路修正などを行わせる。一方、操向ハンドル１９の操作量に比例させて各バルブ８２・８９の制御により旋回ポンプ４１出力と走行ポンプ３８出力を変化させ、旋回半径（操舵角）を小さく（大きく）したとき、走行速度（車速）を比例させて減速させ乍ら、左右の走行クローラ２の速度差を大きくし、左右に旋回させるもので、左右走行クローラ２の駆動速度を変更して条合せ進路修正並びに圃場枕地でのスピンターンによる方向転換を行い、連続的に穀稈を刈取って脱穀する収穫作業を行う。なお、主変速レバー８１が中立のとき、操向ハンドル１９の操作に関係なく、旋回バルブ８９が中立維持され、旋回ポンプ４１の油圧出力が略零に保たれ、旋回モータ４２を停止させる。
Further, when the main transmission lever 81 is operated to a position other than the neutral position and the steering handle 19 is operated other than the straight traveling, the hydraulic output of the traveling pump 38 is proportional to the operation direction and the operation amount of the main transmission lever 81. Increase / decrease, forward / reverse or increase / decrease the hydraulic motor 39 to change the forward / reverse speed (vehicle speed), and change the output of the swing pump 41 in proportion to the amount of operation of the main shift lever 81. Automatically reduces the turning radius and automatically increases the turning radius by low-speed side shifting, and the turning radius of the left and right traveling crawlers 2 is maintained substantially constant by constant operation of the steering handle 19 regardless of the traveling speed. To change the work travel speed and to correct the course so that the machine body is aligned with the uncut grain row. On the other hand, when the turning pump 41 output and the traveling pump 38 output are changed by the control of the valves 82 and 89 in proportion to the operation amount of the steering handle 19, the traveling speed is reduced when the turning radius (steering angle) is made small (large). The speed difference between the left and right traveling crawlers 2 is increased and the left and right traveling crawlers 2 are swung left and right while the vehicle speed is reduced in proportion to the vehicle speed. The direction is changed by spin-turning at, and the harvesting operation is carried out to continuously harvest and thresh grains. When the main transmission lever 81 is neutral, the swing valve 89 is maintained neutral regardless of the operation of the steering handle 19, the hydraulic output of the swing pump 41 is maintained at substantially zero, and the swing motor 42 is stopped.
さらに、図１０乃至図１４に示す如く、前記エンジン２１の出力軸４４を前側及び後側に突設させ、出力軸４４の前側に前記入力軸４５を連結させ、出力軸４４の後側に作業出力プーリ９１を設けると共に、エンジン２１の左側で脱穀部４前側の機台３上面にカウンタケース２５を設け、入力プーリ９２、車速同調プーリ９３、脱穀プーリ９４、刈取プーリ９５、選別プーリ９６をカウンタケース２５に軸支させ、ケース２５後側の入力プーリ９２を作業出力プーリ９１にテンション脱穀クラッチ９７を介してベルト９８連結させ、エンジン２１の駆動力をカウンタケース２５に伝える。また、右支持台２４前側のアイドルプーリ９９を介してミッションケース２２の刈取駆動プーリ６２に前記カウンタケース２５右側の車速同調プーリ９３をベルト１００連結させると共に、機台３の前側上面に立設させる支持台２３・２４に刈取入力ケース１０１を回転自在に軸支させ、前記ケース１０１に刈取フレーム１２を連結させてケース１０１回りに刈取部７を回転させて昇降させるもので、前記ケース１０１左側に刈取入力軸１０２を介して刈取入力プーリ１０３を軸支させ、前記カウンタケース２５左側の刈取プーリ９５を刈取入力プーリ１０３にベルト１０４連結させ、刈取部７の各部に駆動力を伝える。
Further, as shown in FIGS. 10 to 14, the output shaft 44 of the engine 21 is projected on the front side and the rear side, the input shaft 45 is connected to the front side of the output shaft 44, and work is performed on the rear side of the output shaft 44. An output pulley 91 is provided, and a counter case 25 is provided on the upper surface of the machine base 3 in front of the threshing section 4 on the left side of the engine 21. The input pulley 92, the vehicle speed tuning pulley 93, the threshing pulley 94, the cutting pulley 95, and the sorting pulley 96 are countered. The case 25 is pivotally supported, and the input pulley 92 on the rear side of the case 25 is connected to the work output pulley 91 via a belt threshing clutch 97 to transmit the driving force of the engine 21 to the counter case 25. In addition, the vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected to the cutting drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support base 24 and is erected on the front upper surface of the machine base 3. A cutting input case 101 is pivotally supported on the support bases 23 and 24, a cutting frame 12 is connected to the case 101, and the cutting unit 7 is rotated around the case 101 to move up and down. The cutting input pulley 103 is pivotally supported via the cutting input shaft 102, the cutting pulley 95 on the left side of the counter case 25 is connected to the cutting input pulley 103 with the belt 104, and the driving force is transmitted to each part of the cutting unit 7.
また、前記扱胴６の駆動入力プーリ１０５にカウンタケース２５前側の脱穀プーリ９４をベルト１０６連結させ、扱胴６下側の選別唐箕及び揺動選別機構に選別プーリ９６から駆動力を伝え、脱穀部６の各部を駆動すると共に、前記カウンタケース２５の左側面にフィードチェン入力軸１０７を設け、外側に移動可能な前記フィードチェン５の駆動スプロケット１０８に入力軸１０７から動力を伝える。また、前記穀物タンク１５の前側に排出駆動プーリ１０９を設け、該プーリ１０９を前記作業出力プーリ９１に排出クラッチ１１０を介してベルト連結させ、排出オーガ１７にエンジン２１出力を伝えてタンク１５の穀粒を排出させる。
Further, a threshing pulley 94 on the front side of the counter case 25 is connected to the driving input pulley 105 of the handling cylinder 6 with a belt 106, and a driving force is transmitted from the sorting pulley 96 to the sorting and swinging selection mechanism on the lower side of the handling cylinder 6, thereby threshing. While driving each part of the part 6, a feed chain input shaft 107 is provided on the left side surface of the counter case 25, and power is transmitted from the input shaft 107 to the drive sprocket 108 of the feed chain 5 that can move outward. Further, a discharge drive pulley 109 is provided on the front side of the grain tank 15, the pulley 109 is belt-connected to the work output pulley 91 via a discharge clutch 110, and the output of the engine 21 is transmitted to the discharge auger 17 to transfer the grain in the tank 15. Drain the grains.
さらに、前記カウンタケース２５に扱胴入力軸１１１を軸支させ、該軸１１１を前後方向に延設させ、カウンタケース２５前面外側の前記軸１１１前側に脱穀プーリ９４を設け、カウンタケース２５の後面外側の前記軸１１１後側に入力プーリ９２を設け、扱胴入力軸１１１にエンジン２１の一定回転動力を入力させて定速回転させる。また、前記カウンタケース２５の右側に同調入力軸１１２を軸支させ、カウンタケース２５の右側外側の前記軸１１２右側に車速同調プーリ９３を設け、アイドルプーリ９９を介してプーリ６２・９３間にベルト１００を緊張させ、ミッションケース２２からカウンタケース２５に車速同調動力を入力させる。
Further, the barrel input shaft 111 is pivotally supported on the counter case 25, the shaft 111 is extended in the front-rear direction, a threshing pulley 94 is provided on the front side of the shaft 111 outside the front surface of the counter case 25, and the rear surface of the counter case 25 An input pulley 92 is provided on the rear side of the outer shaft 111, and a constant rotational power of the engine 21 is input to the handling cylinder input shaft 111 to rotate at a constant speed. Further, a tuning input shaft 112 is pivotally supported on the right side of the counter case 25, a vehicle speed tuning pulley 93 is provided on the right side of the shaft 112 outside the right side of the counter case 25, and a belt is provided between the pulleys 62 and 93 via the idle pulley 99. 100 is tensioned, and the vehicle speed synchronization power is input from the mission case 22 to the counter case 25.
さらに、前記扱胴入力軸１１１に右側をベベルギヤ１１３連結させるカウンタ軸または選別入力軸である定速軸１１４と、該軸１１４の前側に略平行に設ける車速同調軸１１５とを、カウンタケース２５に軸支させると共に、同調入力軸１１２の車速同調回転力を伝える一方向クラッチ１２０を同調入力軸１１２上に設け、車速同調プーリ９３からの動力を一方向クラッチ１２０によって伝えるギヤ１１７及び刈取クラッチ１１８を介して車速同調軸１１５を回転させるように構成する。
Further, the counter case 25 includes a constant speed shaft 114 that is a counter shaft or a selection input shaft for connecting the bevel gear 113 on the right side to the handle cylinder input shaft 111 and a vehicle speed tuning shaft 115 provided substantially parallel to the front side of the shaft 114. A one-way clutch 120 is provided on the tuning input shaft 112 for transmitting the vehicle speed tuning rotational force of the tuning input shaft 112 and the gear 117 and the cutting clutch 118 for transmitting the power from the vehicle speed tuning pulley 93 by the one-way clutch 120. The vehicle speed tuning shaft 115 is configured to rotate.
さらに、刈取定速機構１２１を形成する刈取定速クラッチ１２２と高速カットギヤ１２３を前記各軸１１４・１１５の間に設け、刈取部７を車速同調または高速カット駆動させる切換シフタ１２４によって前記各ギヤクラッチ１１８・１２２を択一的に係合させ、刈取部７を車速同調駆動して走行速度に連動した速度で刈取部７を駆動する一方、刈取部７を高速カット駆動して車速同調の最高速よりも早い一定回転速度で刈取部７を駆動して倒伏穀稈を刈取る。
Further, a cutting constant speed clutch 122 and a high speed cut gear 123 forming a cutting constant speed mechanism 121 are provided between the shafts 114 and 115, and the gear clutches are switched by a shift shifter 124 that drives the cutting part 7 in synchronization with the vehicle speed or high speed cut. 118 and 122 are selectively engaged, and the cutting unit 7 is driven in synchronization with the vehicle speed to drive the cutting unit 7 at a speed linked to the traveling speed, while the cutting unit 7 is driven at high speed to drive the maximum speed for vehicle speed synchronization. The mowing unit 7 is driven at a constant rotational speed faster than that to harvest the fallen cereal.
また、前記カウンタケース２５の左側で下部後側に定速軸１１４の左側端を突出させ、該軸１１４左側端部に選別プーリ９６を軸支させる。さらに、カウンタケース２５の左側で下部前側に刈取伝動軸１２５を軸支させ、該軸１２５右側を車速同調軸１１５にトルクリミッタ１２６を介して連結させ、カウンタケース２５左側に突出させる前記軸１２５の左側端部に刈取プーリ９５を軸支させると共に、前記刈取入力軸１０２に刈取駆動軸１２７をギヤ１２８連結させ、刈取駆動軸１２７に刈取入力プーリ１０３を軸支させるもので、トルクリミッタ１２６に伝える車速同調入力の入切と、定速駆動入力の入切とを、同一のシフタ１２４によって行い、トルクリミッタ１２６に伝える車速同調入力と定速駆動入力が同時に入になる不具合をなくし、車速同調と定速駆動の各入力がシフタ１２４によって択一選択されて伝えられ、伝動切換の制御を不要にして取扱い性の向上を図る。さらに、前記の左の支持台２３に支点軸１９９を介してギヤ１２８のケースを縦軸回りに回転自在に設け、刈取入力ケース１０１の左側をギヤ１２８のケースに固定させ、各ケース１０１に前記ギヤ１２８を内設させ、刈取入力軸１０２の左端側から刈取り動力を入力させ、前記ケース１０１右端側の刈取フレーム１２に内挿させる刈取伝動軸１３０を介して刈取部７の駆動を行わせる一方、支点軸１２９回りに機体左側に略水平に刈取部７を回転移動させ、機体内側の各ケース２２・２５付近のメンテナンス等を行う。
Further, the left end of the constant speed shaft 114 is protruded to the lower rear side on the left side of the counter case 25, and the sorting pulley 96 is pivotally supported on the left end portion of the shaft 114. Further, the cutting transmission shaft 125 is pivotally supported on the lower front side on the left side of the counter case 25, the right side of the shaft 125 is connected to the vehicle speed tuning shaft 115 via the torque limiter 126, and the shaft 125 is projected to the left side of the counter case 25. A cutting pulley 95 is pivotally supported at the left end, a cutting drive shaft 127 is connected to the cutting input shaft 102 and a gear 128 is coupled, and the cutting input pulley 103 is pivotally supported by the cutting drive shaft 127 and is transmitted to the torque limiter 126. The on / off of the vehicle speed tuning input and the on / off of the constant speed driving input are performed by the same shifter 124 to eliminate the problem that the vehicle speed tuning input and the constant speed driving input transmitted to the torque limiter 126 are simultaneously turned on. Each input of the constant speed drive is selected and transmitted by the shifter 124, and transmission control is not required, thereby improving handling. Further, a case of the gear 128 is provided on the left support base 23 via a fulcrum shaft 199 so as to be rotatable about the vertical axis, and the left side of the cutting input case 101 is fixed to the case of the gear 128, While the gear 128 is installed, the cutting power is input from the left end side of the cutting input shaft 102, and the cutting unit 7 is driven via the cutting transmission shaft 130 inserted into the cutting frame 12 on the right end side of the case 101. Then, the mowing unit 7 is rotated about the fulcrum shaft 129 substantially horizontally on the left side of the machine body, and maintenance of the vicinity of the cases 22 and 25 inside the machine body is performed.
さらに、前記カウンタケース２５の左側上部に前記フィードチェン入力軸１０７を軸支させ、フィードチェンクラッチ１３１を設けるフィードチェン駆動軸１３２に前記入力軸１０７をチェン１３３連結させると共に、定速軸１１４の回転を車速同調軸１１５の回転数変化によって変速して伝えるフィードチェン変速機構１３４を設け、サンギヤ１３５とプラネタリギヤ１３６とリングギヤ１３７を備える遊星ギヤ機構１３８によって無段変速可能に前記機構１３４を形成するもので、定速軸１１４にサンギヤ１３５を係合軸支させ、定速軸１１４に遊転支持させるリングギヤ１３７を車速同調軸１１５にギヤ１３９連結させると共に、プラネタリギヤ１３６を遊転支持させる軸受体１４０を定速軸１１４に遊転支持させ、前記フィードチェンクラッチ１３１を介して前記フィードチェン駆動軸１３２に軸受体１４０をギヤ１４１連結させ、穀稈の搬送に必要な最低回転を確保し乍ら、低い一定回転から高回転にフィードチェン５速度を車速と同調させて変更可能に構成している。
Further, the feed chain input shaft 107 is pivotally supported on the upper left part of the counter case 25, the input shaft 107 is connected to the chain 133 to a feed chain drive shaft 132 provided with a feed chain clutch 131, and the constant speed shaft 114 is rotated. Is provided with a feed chain transmission mechanism 134 that transmits the speed by changing the rotational speed of the vehicle speed tuning shaft 115, and the planetary gear mechanism 138 including the sun gear 135, the planetary gear 136, and the ring gear 137 forms the mechanism 134 so as to be continuously variable. In addition, the sun gear 135 is supported on the constant speed shaft 114 and the ring gear 137, which freely supports the constant speed shaft 114, is connected to the gear 139 to the vehicle speed tuning shaft 115, and the bearing 140, which supports the planetary gear 136, is fixed. The fast shaft 114 is supported in an idle manner, and the feed chain is The bearing body 140 is connected to the gear 141 via the clutch 131 to the feed chain drive shaft 132 to ensure the minimum rotation necessary for conveying the cereal, and the feed chain 5 speed is increased from the low constant rotation to the high rotation. It is configured so that it can be changed in synchronization.
また、切換シフタ１２４を作動させる油圧刈取定速シリンダ１４３と、脱穀クラッチ９７を入にする油圧脱穀シリンダ１４４を、前記カウンタケース２５の上面蓋である油路ベース１４５に固定させると共に、前記車速定速クラッチ７６を入にする車速定速シリンダ１４６を作動させる車速定速バルブ１４７と、刈取定速シリンダ１４３を作動させる刈取定速バルブ１４９と、脱穀シリンダ１４４を作動させる脱穀バルブ１５０とを、前記チャージポンプ７８に並列に油圧接続させる。
Further, a hydraulic cutting speed cylinder 143 for operating the switching shifter 124 and a hydraulic threshing cylinder 144 for receiving the threshing clutch 97 are fixed to an oil passage base 145 which is a top cover of the counter case 25, and the vehicle speed is fixed. The vehicle speed constant speed valve 147 for operating the vehicle speed constant speed cylinder 146 for engaging the speed clutch 76, the cutting constant speed valve 149 for operating the cutting constant speed cylinder 143, and the threshing valve 150 for operating the threshing cylinder 144 are described above. The charge pump 78 is hydraulically connected in parallel.
さらに、図１５、図１６は、刈取部７の駆動速度を切換える刈取変速機構１５１をカウンタケース２５に設けるもので、刈取変速機構１５１を設けない仕様の図１３のカウンタケース２５と同一形状のカウンタケース２５を用い、刈取変速機構１５１を設ける仕様を構成するもので、刈取変速機構１５１を形成する低速ギヤ１５２及び高速ギヤ１５３を前記同調入力軸１１２と刈取変速軸１５４の間に設け、低速及び中立及び高速の各刈取変速を行う刈取変速スライダ１５５によって前記各ギヤ１５２・１５３を刈取変速軸１５４に択一的に係合させ、刈取変速軸１５４を同一軸芯上で連結させる車速同調軸１１５に刈取変速出力を伝えると共に、各軸１１４・１１５間に高速カットギヤ１５６を設け、刈取定速機構１２１を形成する流込みギヤ１２３と高速カットギヤ１５６を前記各軸１１４・１１５の間に設け、刈取部７を流込み駆動または高速カット駆動させる切換スライダ１２４によって前記各軸１１４・１１５に前記各ギヤ１２３・１５６を択一的に係合させ、刈取部７を流込み駆動して走行状態に関係なく刈取部７の穀稈をフィードチェン５側に搬送させる一方、刈取部７を高速カット駆動して車速同調の最高速よりも早い一定回転速度で刈取部７を駆動して倒伏穀稈を刈取る。
Further, FIGS. 15 and 16 show that the counter case 25 is provided with a cutting speed change mechanism 151 for switching the driving speed of the cutting unit 7, and the counter has the same shape as the counter case 25 of FIG. 13 in which the cutting speed change mechanism 151 is not provided. The case 25 is used to constitute a specification for providing the cutting transmission mechanism 151. The low-speed gear 152 and the high-speed gear 153 forming the cutting transmission mechanism 151 are provided between the tuning input shaft 112 and the cutting transmission shaft 154. A vehicle speed tuning shaft 115 that selectively engages each of the gears 152 and 153 with the cutting speed change shaft 154 by a cutting speed change slider 155 that performs neutral and high speed cutting speed changes, and connects the cutting speed change shaft 154 on the same axis. A cutting speed change output is transmitted to the shaft and a high speed cut gear 156 is provided between the shafts 114 and 115 to form a constant cutting speed mechanism 121. A gear 123 and a high speed cut gear 156 are provided between the shafts 114 and 115, and the gears 123 and 156 are selected for the shafts 114 and 115 by a switching slider 124 for driving the cutting portion 7 into a flow or high speed cut. Engaged with each other to drive the reaping portion 7 into the feed chain 5 regardless of the running state, while the reaping portion 7 is conveyed to the feed chain 5 side, while the reaping portion 7 is driven at a high speed to drive the maximum speed of vehicle speed synchronization. The mowing unit 7 is driven at a constant rotational speed faster than that to harvest the fallen cereal.
さらに、図１３、図１４、図１７乃至図２０に示す如く、前記刈取伝動軸１２５にトルクリミッタ１２６を設けるもので、前記カウンタケース２５の側壁の一部を形成する着脱自在な分離ケース２５ａにトルクリミッタ取付け孔１５７を開設させ、前記取付け孔１５７に軸受蓋１５８を外側から嵌合させて着脱自在にボルト１５９止め固定させ、カウンタケース２５の一部を形成する着脱自在な軸受蓋１５８に刈取伝動軸１２５の中間をベアリング軸受１６０により回転及び摺動自在に軸支させる。
Further, as shown in FIGS. 13, 14, 17 to 20, a torque limiter 126 is provided on the cutting transmission shaft 125, and a detachable separating case 25 a forming a part of the side wall of the counter case 25 is provided. A torque limiter mounting hole 157 is opened, a bearing lid 158 is fitted into the mounting hole 157 from the outside, and is detachably fixed with a bolt 159, and a removable bearing lid 158 forming a part of the counter case 25 is trimmed. The middle of the transmission shaft 125 is supported by a bearing bearing 160 so as to be rotatable and slidable.
また、前記カウンタケース２５の外側に突出させる刈取伝動軸１２５の一端側に刈取プーリ９５をキー嵌合固定させると共に、カウンタケース２５の内側に挿入させる刈取伝動軸１２５の他端側に、平ギヤ形のリミッタ伝動ギヤ１６１をベアリング軸受１６２を介して回転自在に軸支させる。なお、前記プーリ９５の外径を軸受蓋１５８の外形よりも大きく形成し、プーリ９５を軸１２５から取外した状態で軸受蓋１５８及びボルト１５９の着脱を行うと共に、前記ギヤ１６１の外径を取付け孔１５７よりも小さく形成し、ギヤ１６１を軸１２５に取付けた状態で、取付け孔１５７に軸１２５と軸受蓋１５８の嵌合部を出入させるもので、前記ギヤ１６１を噛合させる平ギヤ１６３を前記車速同調軸１１５に係合軸支させ、車速同調軸１１５にリミッタ伝動ギヤ１６１を連結させる。
Further, a cutting pulley 95 is key-fitted and fixed to one end side of the cutting transmission shaft 125 that protrudes outside the counter case 25, and a flat gear is connected to the other end side of the cutting transmission shaft 125 that is inserted inside the counter case 25. A shape limiter transmission gear 161 is rotatably supported through a bearing bearing 162. The outer diameter of the pulley 95 is formed larger than the outer diameter of the bearing cover 158, and the bearing cover 158 and the bolt 159 are attached and detached with the pulley 95 removed from the shaft 125, and the outer diameter of the gear 161 is attached. The fitting portion of the shaft 125 and the bearing lid 158 is inserted into and removed from the mounting hole 157 in a state where the gear 161 is mounted on the shaft 125 with the gear 161 being mounted on the shaft 125. An engagement shaft is supported on the vehicle speed tuning shaft 115, and a limiter transmission gear 161 is connected to the vehicle speed tuning shaft 115.
さらに、前記リミッタ伝動ギヤ１６１の側面に一体形成する円筒形のアウタケース１６４と、刈取伝動軸１２５上で対向させるドーナツ板形の受板１６５及び押板１６６と、同一円周上に複数のトルクローラ１６７を略等間隔に配列させるドーナツ板形のトルク板１６８と、刈取伝動軸１２５の軸芯方向の対向する両側方からトルク板１６８のトルクローラ１６７を挾持させるドーナツ平板形の内板１６９及び外板１７０と、前記伝動軸１２５に螺着させて押板１６６に圧接させる着脱自在なナット１７１及び座金１７２とを、前記トルクリミッタ１２６に備え、カウンタケース２５内部にトルクリミッタ１２６本体側のアウタケース１６４などを配設させて油浴させる。
Further, a cylindrical outer case 164 integrally formed on the side surface of the limiter transmission gear 161, a donut plate-shaped receiving plate 165 and a push plate 166 opposed to each other on the cutting transmission shaft 125, and a plurality of torques on the same circumference. A donut plate-shaped torque plate 168 in which the rollers 167 are arranged at substantially equal intervals, and a donut plate-shaped inner plate 169 that holds the torque roller 167 of the torque plate 168 from opposite sides in the axial direction of the cutting transmission shaft 125; The torque limiter 126 includes an outer plate 170 and a detachable nut 171 and a washer 172 that are screwed onto the transmission shaft 125 and press-contacted to the push plate 166, and the outer side of the torque limiter 126 main body is provided inside the counter case 25. A case 164 or the like is disposed and an oil bath is provided.
そして、軸受蓋１５８に刈取伝動軸１２５を軸支させ、該軸１２５にリミッタ伝動ギヤ１６１を抜出し自在に軸支させ、アウタケース１６４の内孔１７３に受板１６５を内挿させ、複数組の内板１６９とトルク板１６８と外板１７０をアウタケース１６４に内挿させ、刈取伝動軸１２５のスプラインに内板１６９の内孔を係合軸支させ、略１２０度間隔に設けるアウタケース１６４のキー溝１７４に外板１７０外周の突起形キー１７５を係合させる。また、トルクバネ１７６を支持させた座板１７７を刈取伝動軸１２５の機外側端部に回転自在に軸支させ、前記軸１２５にトルクナット１７８を螺着させ、トルクリミッタ１２６を軸受蓋１５８及び刈取伝動軸１２５とユニット構造に組立てるもので、トルクナット１７８を締付けてトルクバネ１７６力を調節し、トルクローラ１６７の伝達トルクを設定する。また、前記刈取プーリ９５とこのプーリボス１７９とを各別に形成し、プーリ９５とプーリボス１７９を着脱自在にボルト１８０止め固定させ、プーリボス１７９を刈取伝動軸１２５にキー嵌合させ、プーリボス１７９の機外側面にトルクバネ１７６を圧接させ、カウンタケース２５の外側にトルクナット１７８及びバネ１７６を設ける。
Then, the cutting cover shaft 158 is pivotally supported by the bearing cover 158, the limiter transmission gear 161 is pivotally supported by the shaft 125, the receiving plate 165 is inserted into the inner hole 173 of the outer case 164, and a plurality of sets are set. The inner plate 169, the torque plate 168, and the outer plate 170 are inserted into the outer case 164, the inner hole of the inner plate 169 is engaged with the spline of the cutting transmission shaft 125, and the outer case 164 provided at intervals of approximately 120 degrees. The protruding key 175 on the outer periphery of the outer plate 170 is engaged with the key groove 174. Further, a seat plate 177 supporting the torque spring 176 is rotatably supported on the machine outer end of the cutting transmission shaft 125, a torque nut 178 is screwed onto the shaft 125, and the torque limiter 126 is connected to the bearing cover 158 and the cutting blade. The transmission shaft 125 and the unit structure are assembled. The torque nut 178 is tightened to adjust the torque spring 176 force, and the transmission torque of the torque roller 167 is set. Further, the cutting pulley 95 and the pulley boss 179 are formed separately, the pulley 95 and the pulley boss 179 are detachably fixed with bolts 180, the pulley boss 179 is key-fitted to the cutting drive shaft 125, and the pulley boss 179 is externally mounted. A torque spring 176 is pressed against the side surface, and a torque nut 178 and a spring 176 are provided outside the counter case 25.
また、刈取伝動軸１２５の軸芯部にＬ形の油穴１８１を形成し、油穴１８１の一端側をカウンタケース２５の内部に軸１２５端面で開口させ、油穴１８１の他端側を刈取伝動軸１２５の周面に開口させ、刈取伝動軸１２５の回転によって発生する遠心力により油穴１８１からトルクローラ１６７方向にケース２５の油を移動させ、遠心力によって強制的にトルクローラ１６７に油を送って強制潤滑する。
Further, an L-shaped oil hole 181 is formed in the shaft core portion of the cutting transmission shaft 125, one end side of the oil hole 181 is opened inside the counter case 25 at the end face of the shaft 125, and the other end side of the oil hole 181 is cut off. The oil in the case 25 is opened in the direction of the torque roller 167 from the oil hole 181 by the centrifugal force generated by the rotation of the cutting transmission shaft 125, and the oil is forced to the torque roller 167 by the centrifugal force. To force lubrication.
さらに、前記トルクローラ１６７の円柱形に対して平面視で相似する長方形の支持孔１８２をトルク板１６８に形成し、トルクローラ１６７を支持孔１８２に回転自在に内挿させると共に、支持孔１８２の対向する長辺側の開口縁に一対の舌片１８３を対向させて設け、トルクローラ１６７の外周に舌片１８３を摺接させる。また、トルク板１６８の外周に形成する折曲げ縁１８４と同一方向に舌片１８３を突設させ、トルク板１６８の軸芯方向の幅をトルクローラ１６７の外径よりも小さく形成し、トルク板１６８の両側面にトルクローラ１６７の外周側を突出させて内板１６９と外板１７０に摺接させると共に、ホルダを形成する一対の舌片１８３の先端側をトルクローラ１６７の円周方向に折曲げ、トルクローラ１６７の外周を一対の舌片１８３によって回転自在に挾持させる。
Further, a rectangular support hole 182 similar in plan view to the cylindrical shape of the torque roller 167 is formed in the torque plate 168, and the torque roller 167 is rotatably inserted into the support hole 182 and the support hole 182 A pair of tongue pieces 183 are provided so as to face each other on the opening edge on the opposite long side, and the tongue piece 183 is slidably contacted with the outer periphery of the torque roller 167. Further, a tongue piece 183 is projected in the same direction as the bent edge 184 formed on the outer periphery of the torque plate 168, and the width in the axial direction of the torque plate 168 is made smaller than the outer diameter of the torque roller 167. The outer peripheral side of the torque roller 167 protrudes from both side surfaces of the 168 to make sliding contact with the inner plate 169 and the outer plate 170, and the tip side of the pair of tongue pieces 183 forming the holder is folded in the circumferential direction of the torque roller 167. The outer periphery of the torque roller 167 is bent and is rotatably held by a pair of tongue pieces 183.
さらに、前記トルク板１６８の回転中心を通過する放射線に対してトルクローラ１６７の軸芯線をトルク板１６８の回転下手側に一定の傾斜角度で傾斜させるもので、トルクローラ１６７の転動軸芯線がトルク板１６８の回転中心を含む平面（放射線）に対して一定角度だけ傾斜するようにトルクローラ１６７を配置させ、車速同調軸１１５の平ギヤ１６３を介してアウタケース１６４を回転駆動させると、各トルクローラ１６７が内板１６９と外板１７０に接しながら転動してトルク板１６８も回転する。このとき、各トルクローラ１６７は、外板１７０の回転軌道に対して一定角度だけ傾斜した方向に転動しようとするのを、トルク板１６８で規制されながら外板１７０の回転軌道の方向に移動するため、前記トルクバネ１７６圧に比例した摩擦抵抗が発生し、しかも、各トルクローラ１６７は転動しながら滑り摩擦を発生させるので、静摩擦は発生せず、常に動摩擦による安定した摩擦抵抗力が得られる。また、刈取伝動軸１２５側の刈取駆動負荷が増加したとき、または平ギヤ１６３側の入力速度の変更によりアウタケース１６４の回転速度が高速側に急変したとき、内板１６９と外板１７０の各回転トルク差が増大してトルクローラ１６７の摩擦抵抗力よりも大きくなることにより、内板１６９と外板１７０がトルクローラ１６７に対して摺動して伝達動力が遮断される。
Further, the axis of the torque roller 167 is inclined at a constant inclination angle toward the lower rotation side of the torque plate 168 with respect to the radiation passing through the rotation center of the torque plate 168. When the torque roller 167 is disposed so as to be inclined by a certain angle with respect to a plane (radiation) including the rotation center of the torque plate 168, and the outer case 164 is rotationally driven via the flat gear 163 of the vehicle speed tuning shaft 115, The torque roller 167 rolls in contact with the inner plate 169 and the outer plate 170, and the torque plate 168 also rotates. At this time, each torque roller 167 moves in the direction of the rotation trajectory of the outer plate 170 while being restricted by the torque plate 168 to roll in a direction inclined by a certain angle with respect to the rotation trajectory of the outer plate 170. Therefore, a frictional resistance proportional to the pressure of the torque spring 176 is generated, and each torque roller 167 generates sliding friction while rolling, so that no static friction is generated, and a stable frictional resistance force due to dynamic friction is always obtained. It is done. Further, when the cutting drive load on the cutting transmission shaft 125 side increases or when the rotational speed of the outer case 164 suddenly changes to the high speed side by changing the input speed on the flat gear 163 side, each of the inner plate 169 and the outer plate 170 As the rotational torque difference increases and becomes greater than the frictional resistance force of the torque roller 167, the inner plate 169 and the outer plate 170 slide against the torque roller 167 and the transmission power is cut off.
上記のように、油圧変速機構４０と定速機構１２１のいずれか一方によって作業部である刈取部７に駆動力を伝えると共に、刈取部７を定速回転させる刈取伝動軸１２５にトルクリミッタ１２６を設け、油圧変速機構４０と定速機構１２１を切換えるときの駆動トルク差によって生じるショックをトルクリミッタ１２６によって吸収させると共に、トルクリミッタ１２６を内設させるカウンタケース２５内部の作動油面をトルクリミッタ１２６の軸１２５の設置位置よりも高くし、トルクリミッタ１２６に対して充分に潤滑を行わせる。
As described above, either one of the hydraulic transmission mechanism 40 and the constant speed mechanism 121 transmits the driving force to the cutting unit 7 that is the working unit, and the torque limiter 126 is attached to the cutting transmission shaft 125 that rotates the cutting unit 7 at a constant speed. The shock limiter 126 absorbs a shock caused by a drive torque difference when switching between the hydraulic transmission mechanism 40 and the constant speed mechanism 121, and the hydraulic oil level in the counter case 25 in which the torque limiter 126 is installed is fixed to the torque limiter 126. The height of the shaft 125 is set higher than that of the shaft 125 so that the torque limiter 126 is sufficiently lubricated.
また、プーリボス１７９の外側にトルクナット１７８及びトルクバネ１７６を設け、トルクリミッタ１２６のトルクセットを機外から行い、メンテナンスなど取扱い性の向上を図ると共に、刈取プーリ９５とプーリボス１７９を別体で形成し、刈取プーリ９５とプーリボス１７９をボルト１８０止め固定させ、プーリボス１７９を取付けた状態で刈取プーリ９５を取外し、トルクリミッタ１２６のセットトルクを一定に保った状態で刈取プーリ９５を取外してベルト交換作業などを行う。
In addition, a torque nut 178 and a torque spring 176 are provided outside the pulley boss 179 to perform torque setting of the torque limiter 126 from the outside of the machine to improve handling and maintenance, and the cutting pulley 95 and the pulley boss 179 are formed separately. The cutting pulley 95 and the pulley boss 179 are fixed with bolts 180, the cutting pulley 95 is removed with the pulley boss 179 attached, and the cutting pulley 95 is removed while the set torque of the torque limiter 126 is kept constant, and the belt is replaced. I do.
さらに、図１９、図２０に示す如く、回転軸１２５上で受板１６５と押板１６６を対向させ、複数組の内板１６９とトルク板１６８と外板１７０を前記受板１６５と押板１６６の間に設け、内板１６９を回転軸１２５に係合させ、外板１７０をアウタケース１６４に係合させ、トルク板１６８にトルクローラ１６７を設けると共に、回転軸１２５に螺着させるトルクナット１７８にバネ座板１７７を係止させ、バネ座板１７７と押板１６６の間にバネ１７６を設ける。そして、トルク板１６８に対向させる受板１６５または押板１６６の受圧面１８５・１８６が、セットトルクを発生させる押付け力によって撓んで平面になるように、前記受圧面１８５・１８６を略凹面形に形成するもので、受板１６５及び押板１６６の各受圧面１８５・１８６を、傾斜角Ａ１、Ａ２をなすテーパ構造にし、各板１６５・１６６の外周側が内板１６９に先に当たるように傾斜角Ａ１、Ａ２をなすテーパとして受圧面１８５・１８６を形成する。そして、セットトルクを発生するときの押付け力によって受板１６５または押板１６６が撓んで受圧面１８５・１８６が略平面になり、平滑化された面圧がトルクローラ１６７面にかかり、トルクローラ１６７の偏摩耗を低減して耐久性を向上させることができ、セットトルクの伝達精度も向上させる。また、受板１６５または押板１６６の厚みをセットトルクによって歪まない程度に厚くしなくても、受圧面１８５・１８６圧の平滑化ができるから、省スペースでコンパクトなユニットに構成することができる。
Further, as shown in FIGS. 19 and 20, the receiving plate 165 and the pressing plate 166 are opposed to each other on the rotating shaft 125, and a plurality of sets of inner plate 169, torque plate 168 and outer plate 170 are combined with the receiving plate 165 and the pressing plate 166. A torque nut 178 for engaging the inner plate 169 with the rotating shaft 125, engaging the outer plate 170 with the outer case 164, providing a torque roller 167 on the torque plate 168, and screwing the rotating plate 125. The spring seat plate 177 is locked, and the spring 176 is provided between the spring seat plate 177 and the push plate 166. The pressure receiving surfaces 185 and 186 are made substantially concave so that the pressure receiving surfaces 185 and 186 of the receiving plate 165 or the pressing plate 166 opposed to the torque plate 168 are bent by the pressing force that generates the set torque. The pressure receiving surfaces 185 and 186 of the receiving plate 165 and the pressing plate 166 are tapered so as to form the inclination angles A1 and A2, and the inclination angles so that the outer peripheral sides of the plates 165 and 166 first contact the inner plate 169. The pressure receiving surfaces 185 and 186 are formed as tapers forming A1 and A2. Then, the receiving plate 165 or the pressing plate 166 is bent by the pressing force when the set torque is generated, and the pressure receiving surfaces 185 and 186 become substantially flat, and the smoothed surface pressure is applied to the torque roller 167 surface, and the torque roller 167 It is possible to improve the durability by reducing the uneven wear and improve the transmission accuracy of the set torque. Further, since the pressure receiving surfaces 185 and 186 can be smoothed without increasing the thickness of the receiving plate 165 or the pressing plate 166 to such an extent that the receiving plate 165 or the pressing plate 166 is not distorted by the set torque, a space-saving and compact unit can be configured. .
また、図１７、図２０に示す如く、受板１６５に段部１８７を設け、該段部１８７をベアリング軸受１６２のインナー部１８８に当接させてセットトルクを受圧させると共に、押板１６６に段部１８９を設け、該段部１８９を座金１７２に当接させ、ナット１７１によって固定させる座金１７２と押板１６６の間で押板１６６の円周側に空間を形成し、ナット１７１の締付力が座金１７２を介して段部１８９から押板１６６に直線的に作用するように構成している。また、プーリボス１７９にビス１９０止め固定させる合成樹脂製の軸カバー１９１を設け、トルクバネ１７６及びトルクナット１７８などを前記軸カバー１９１に内設させ、軸カバー１９１を外した状態でカウンタケース２５外側でトルクナット１７８を操作し、トルクリミッタ１２６のセットトルクを調節する。また、複数の内板１６９の間の夫々に向けて回転軸１２５の外周の複数個所に油穴１８１を夫々開口させ、油穴１８１からアウタケース１６４のキー溝１７４を介して外部に油が遠心力によって移動し、トルクローラ１６７の強制潤滑を行う。
17 and 20, the receiving plate 165 is provided with a stepped portion 187. The stepped portion 187 is brought into contact with the inner portion 188 of the bearing bearing 162 to receive the set torque, and the pressing plate 166 has a stepped portion. A portion 189 is provided, a space is formed on the circumferential side of the pressing plate 166 between the washer 172 fixed to the nut 171 and the pressing plate 166 by bringing the step 189 into contact with the washer 172, and the tightening force of the nut 171 Is configured to linearly act on the pressing plate 166 from the step 189 via the washer 172. Further, a shaft cover 191 made of synthetic resin for fixing the screw 190 to the pulley boss 179 is provided, and a torque spring 176, a torque nut 178, and the like are provided inside the shaft cover 191. With the shaft cover 191 removed, the counter case 25 is disposed outside. The torque nut 178 is operated to adjust the set torque of the torque limiter 126. In addition, oil holes 181 are opened at a plurality of locations on the outer periphery of the rotating shaft 125 toward each of the plurality of inner plates 169, and the oil is centrifuged from the oil holes 181 to the outside through the key grooves 174 of the outer case 164. The torque roller 167 is forcedly lubricated by the force.
上記から明らかなように、回転軸１２５上で受板１６５と押板１６６を対向させ、複数組の内板１６９とトルク板１６８と外板１７０を前記受板１６５と押板１６６の間に設け、内板１６９を回転軸１２５に係合させ、外板１７０をアウタケース１６４に係合させ、トルク板１６８にトルクローラ１６７を設けると共に、回転軸１２５に螺着させるトルクナット１７８にバネ座板１７７を係止させ、バネ座板１７７と押板１６６の間にバネ１７６を設けるトルクリミッタ１２６において、前記内板１６９で仕切られる複数の閉塞部に夫々開口させて給油可能に回転軸１２５に油穴１８１を形成するもので、内板１６９及び外板１７０及びトルク板１６８を多層状に設けても、トルクローラ１６７に対して潤滑油を充分に供給でき、伝達トルクを適正に維持でき、耐久性を向上させることができ、トルクリミッタ１２６機能の向上などを図ることができる。
As apparent from the above, the receiving plate 165 and the pressing plate 166 are opposed to each other on the rotating shaft 125, and a plurality of sets of inner plate 169, torque plate 168 and outer plate 170 are provided between the receiving plate 165 and the pressing plate 166. The inner plate 169 is engaged with the rotary shaft 125, the outer plate 170 is engaged with the outer case 164, the torque roller 167 is provided on the torque plate 168, and the spring seat plate is attached to the torque nut 178 screwed to the rotary shaft 125. In the torque limiter 126 in which the spring 176 is provided between the spring seat plate 177 and the push plate 166, the rotary shaft 125 is oiled so that oil can be supplied by opening each of the closed portions partitioned by the inner plate 169. Even if the inner plate 169, the outer plate 170, and the torque plate 168 are provided in multiple layers, the lubricating oil can be sufficiently supplied to the torque roller 167, and the transmission torque is formed. Properly be maintained, it is possible to improve the durability, and the like can be achieved improvement of the torque limiter 126 functions.
また、外板１７０を係合させるアウタケース１６４のキー溝１７４から閉塞部の油を排出させ、トルクローラ１６７周辺の油を遠心力によってキー溝１７４から効率良く放出させることができ、トルクローラ１６７に対する油の供給を促進させることができ、トルクローラ１６７の潤滑を効率良く行わせると共に、トルクナット１７８の押圧力が直接作用するように、座金１７２と押板１６６の間で押板１６６の円周側に空間を形成し、ナット１７１の締付力を座金１７２を介して押板１６６に直接的に作用させることができ、押板１６６の受圧面１８６を平滑化してトルクローラ１６７の偏荷重を防ぐことができる。
Further, the oil in the closed portion can be discharged from the key groove 174 of the outer case 164 with which the outer plate 170 is engaged, and the oil around the torque roller 167 can be efficiently discharged from the key groove 174 by centrifugal force. The oil supply to the pressure plate 166 can be promoted, the torque roller 167 is lubricated efficiently, and the pressing force of the torque nut 178 acts directly, so that the circle of the press plate 166 is interposed between the washer 172 and the press plate 166. A space is formed on the circumferential side, and the tightening force of the nut 171 can be applied directly to the pressing plate 166 via the washer 172, and the pressure receiving surface 186 of the pressing plate 166 is smoothed to offset the load on the torque roller 167. Can be prevented.
さらに、図１乃至図４、図９に示す如く、前記運転席２０後側のキャビン１８内部にコラムコントローラ１９２を設ける。また、前記の左右の支持台２３・２４の前面板１９３に走行コントローラ１９４を設ける。また、前記エンジンルームカバー３１外側のキャビンフレーム３０にエンジンコントローラ１９５を設ける。また、穀物タンク１５後側の脱穀部４機枠に脱穀コントローラ１９６を設け、各コントローラ１９２・１９４・１９５・１９６をキャン通信により接続させると共に、穀物タンク１５下側の機台３上面に、刈取部７の昇降用並びに機体の水平制御用並びに排出オーガ１７の移動用の油圧バルブセット１９７を設けるもので、エンジンルームカバー３１機外側の外気導入カバー１９８、並びに縦排出オーガ１６回りに水平回動させる穀物タンク１５を側方に回動自在に設けると共に、前記の左の支持台２３上部に支点軸１９９を介してギヤ１２８の収納ケース２００を縦軸回りに回転自在に設け、刈取フレーム１２を支える刈取入力ケース１０１の左側をギヤ１２８の収納ケース２００に固定させ、刈取入力ケース１０１に前記ギヤ１２８を内設させ、刈取入力軸１０２の左端側から刈取り動力を入力させ、前記ケース１０１右端側の刈取フレーム１２に内挿させる刈取伝動軸１３０を介して刈取部７の駆動を行わせる一方、支点軸１９９回りに機体左側に略水平に刈取部７を側方回動させ、機体内側の各ケース２２・２５付近のメンテナンス等を行う。
Further, as shown in FIGS. 1 to 4 and 9, a column controller 192 is provided in the cabin 18 on the rear side of the driver seat 20. A travel controller 194 is provided on the front plate 193 of the left and right support bases 23 and 24. An engine controller 195 is provided on the cabin frame 30 outside the engine room cover 31. In addition, a threshing controller 196 is provided in the frame of the threshing unit 4 on the rear side of the grain tank 15, and the controllers 192, 194, 195, and 196 are connected by CAN communication, and the upper surface of the machine base 3 on the lower side of the grain tank 15 is trimmed. A hydraulic valve set 197 is provided for raising and lowering the unit 7, for horizontal control of the machine body, and for moving the discharge auger 17. The engine room cover 31 is horizontally rotated around the outside air introduction cover 198 and the vertical discharge auger 16. The grain tank 15 to be rotated is provided so as to be pivotable to the side, and the storage case 200 of the gear 128 is provided on the left support base 23 via the fulcrum shaft 199 so as to be rotatable about the vertical axis. The left side of the supporting cutting input case 101 is fixed to the storage case 200 of the gear 128, and the gear 128 is inserted into the cutting input case 101. The cutting power is input from the left end side of the cutting input shaft 102, and the cutting unit 7 is driven via the cutting transmission shaft 130 inserted into the cutting frame 12 on the right end side of the case 101. Next, the mowing unit 7 is rotated sideways substantially horizontally on the left side of the machine body to perform maintenance etc. near the cases 22 and 25 inside the machine body.
さらに、図１３、図１５に示す如く、走行クローラ２を駆動するミッションケース２２と、刈取部７及び脱穀部４とに、カウンタケース２５を介してエンジン２１の動力を伝えるコンバインにおいて、前記刈取部７の駆動速度を変更する刈取変速機構１５０を設ける図１５の仕様と、刈取変速機構１５０を設けない図１３の仕様とを、同一形状のカウンタケース２５を用いて構成するもので、前記の異なる仕様にカウンタケース２５を兼用することができ、製造コストの低減などを図ることができる。また、略定速駆動によって流込み動作を行わせる刈取部７の回転数を、刈取変速機構１５０を設ける図１５の仕様と設けない図１３の仕様とで異ならせるもので、刈取変速を行わないときは刈取速度の高速側を制限する必要がないが、走行速度を早い変速段にしたとき、刈取回転が限界以上になる不具合があるから、流込み速度に切換えて刈取部７の駆動を行うから、刈取変速を行うときに比べて行わないときの流込み速度を早くし、早い走行速度に対応させて刈取部を駆動することができる。
Further, as shown in FIGS. 13 and 15, in the combine that transmits the power of the engine 21 to the transmission case 22 that drives the traveling crawler 2, the cutting unit 7 and the threshing unit 4 via the counter case 25, the cutting unit 15 in which the cutting speed change mechanism 150 for changing the driving speed of FIG. 7 is provided and the specification in FIG. 13 in which the cutting speed change mechanism 150 is not provided are configured using the counter case 25 having the same shape. The counter case 25 can also be used for the specification, and the manufacturing cost can be reduced. Further, the number of rotations of the cutting unit 7 that performs the pouring operation by the substantially constant speed drive is made different between the specification of FIG. 15 in which the cutting transmission mechanism 150 is provided and the specification of FIG. 13 in which the cutting transmission mechanism 150 is not provided. Sometimes, it is not necessary to limit the high speed side of the cutting speed, but when the traveling speed is set to a high gear position, there is a problem that the cutting rotation becomes more than the limit. Therefore, the cutting section 7 is driven by switching to the pouring speed. Thus, the cutting speed can be increased when the cutting speed is not changed compared to when the cutting speed is changed, and the cutting unit can be driven to correspond to the high traveling speed.
さらに、走行クローラ２を駆動するミッションケース２２と、刈取部７及び脱穀部４とに、カウンタケース２５を介してエンジン２１の動力を伝えるコンバインにおいて、前記刈取部７の駆動速度を変更する刈取変速機構１５０を設ける図１５の仕様のときに、流込み機構である流込みギヤ１２３と高速カット機構である高速カットギヤ１５６をカウンタケース２５に設けると共に、刈取変速機構１５０を設けない図１３の仕様のときに、刈取変速機構１５０を設ける図１５の仕様よりも流込みギヤ１２３の速度を早くし、高速カットギヤ１５６を省くもので、流込みギヤ１２３と軸１５４を変換するだけで刈取変速機構１５０を設ける図１５の仕様と設けない図１３の仕様を構成でき、製造コストの低減などを図ることができる。また、刈取部７の側方回動によって開放される位置に、刈取変速機構１５０及び流込みギヤ１２３などの変速コントローラである走行コントローラ１９４を設けるもので、エンジン２１から離れた機体内側で、保守作業を行い易い位置で、カウンタケース２５に近い位置に走行コントローラ１９４を設置でき、該コントローラ１９４とカウンタケース２５の間のハーネス張設距離を短縮でき、組立性及び取扱い性の向上並びに製造コストの低減などを図ることができる。
Further, in a combine that transmits the power of the engine 21 to the mission case 22 that drives the traveling crawler 2, and the cutting unit 7 and the threshing unit 4 via the counter case 25, the cutting shift that changes the driving speed of the cutting unit 7. In the specification of FIG. 15 in which the mechanism 150 is provided, the counter case 25 is provided with the inflow gear 123 that is an inflow mechanism and the high speed cut gear 156 that is a high speed cut mechanism, and the cutting speed change mechanism 150 is not provided. In some cases, the speed of the pour gear 123 is made faster than the specification of FIG. 15 where the pruning speed change mechanism 150 is provided, and the high speed cut gear 156 is omitted, and the pruning speed change mechanism 150 is changed only by converting the pour gear 123 and the shaft 154. The specification of FIG. 15 provided and the specification of FIG. 13 not provided can be configured, and the manufacturing cost can be reduced. In addition, a travel controller 194 that is a speed change controller such as the mowing transmission mechanism 150 and the pouring gear 123 is provided at a position opened by the lateral rotation of the mowing section 7, and maintenance is performed on the inner side of the machine body away from the engine 21. The travel controller 194 can be installed at a position where the work is easy to be performed and close to the counter case 25, and the harness extension distance between the controller 194 and the counter case 25 can be shortened. Reduction can be achieved.
さらに、図５、図６、図９に示す如く、カウンタケース２５に締結座２０１を一体形成し、機台３上面と支持台２３とに受台２０２・２０３を設け、締結座２０１を受台２０２・２０３にボルト２０４止め固定させ、機台３と支持台２３とにカウンタケース２５を固定させると共に、支持台２３の開口２０５から出入自在にバッテリ２０６を支持台２３の内側に設けるもので、走行クローラ２を駆動するミッションケース２２と、刈取部７及び脱穀部４とに、カウンタケース２５を介してエンジン２１の動力を伝えるコンバインにおいて、前記刈取部７を昇降可能並びに側方回動可能に支持させる刈取架台である支持台２３にバッテリ２０６を設け、支持台２３に前記カウンタケース２５を固定させ、刈取部７の側方回動によりバッテリ２０６をメンテナンスし易い場所に設置でき、支持台２３及びカウンタケース２５を設ける脱穀部４前側の機台３を前方に拡張する必要がなく、機台３の有効利用並びにメンテナンス作業の簡略化などを図ることができる。
Further, as shown in FIGS. 5, 6, and 9, the fastening seat 201 is integrally formed on the counter case 25, and the receiving bases 202 and 203 are provided on the upper surface of the machine base 3 and the support base 23. 202 and 203 are fixed with bolts 204, the counter case 25 is fixed to the machine base 3 and the support base 23, and a battery 206 is provided inside the support base 23 so as to be freely accessible through the opening 205 of the support base 23. In the combine that transmits the power of the engine 21 to the mission case 22 that drives the traveling crawler 2, the cutting unit 7 and the threshing unit 4 through the counter case 25, the cutting unit 7 can be moved up and down and can be turned sideways. A battery 206 is provided on a support base 23 which is a cutting stand to be supported, the counter case 25 is fixed to the support base 23, and the battery 20 is rotated by a side rotation of the cutting part 7. Can be installed in a place where maintenance is easy to perform, and it is not necessary to expand the machine base 3 on the front side of the threshing section 4 where the support base 23 and the counter case 25 are provided, to effectively use the machine base 3 and simplify the maintenance work. be able to.
また、側方回動可能に機台３上に配置させる穀物タンク１５下面の機台３に、刈取部７の昇降並びに機体の水平制御用の油圧バルブセット１９７を設け、穀物タンク１５の側方回動により前記油圧バルブセット１９７をメンテナンスし易い場所に設置でき、機台３の有効利用並びにメンテナンス作業の簡略化などを図ると共に、機台３前側のカウンタケース２５と機台３後側の燃料タンク２０７の間で、脱穀部４の下側に、エンジン２１の排気管２０８を設け、バッテリ２０６及び油圧バルブセット１９７などに対して排気管２０８を離間させて設置でき、機台３の有効利用並びにメンテナンス作業の簡略化などを図ることができる。
Further, a hydraulic valve set 197 for raising and lowering the cutting unit 7 and leveling the machine body is provided on the machine base 3 on the lower surface of the grain tank 15 that is disposed on the machine base 3 so as to be pivotable to the side. The hydraulic valve set 197 can be installed in a place where it can be easily maintained by turning, and the machine base 3 can be effectively used, the maintenance work can be simplified, the counter case 25 on the front side of the base 3 and the fuel on the rear side of the base 3 The exhaust pipe 208 of the engine 21 is provided below the threshing unit 4 between the tanks 207, and the exhaust pipe 208 can be installed separately from the battery 206, the hydraulic valve set 197, etc. In addition, the maintenance work can be simplified.
さらに、図６、図８に示す如く、走行クローラ２を駆動するミッションケース２２と、刈取部７及び脱穀部４とに、カウンタケース２５を介してエンジン２１の動力を伝えるコンバインにおいて、前記刈取部７を支持させる左右の支持台２３・２４と脱穀部４の間にカウンタケース２５を設け、左右の支持台２３・２４を連結する支持フレーム２０９をカウンタケース２５の上方に横架させるもので、左右の支持台２３・２４を支持フレーム２０９によって連結させることにより、ハーネス２１０取付け部材または機外側の支持台２３の補強部材として支持フレーム２０９を活用でき、カウンタケース２５周辺構造の簡略化並びに剛性向上などを図ることができる。
Further, as shown in FIGS. 6 and 8, in the combine that transmits the power of the engine 21 to the transmission case 22 that drives the traveling crawler 2, the cutting unit 7 and the threshing unit 4 through the counter case 25, the cutting unit 7 is provided between the left and right support bases 23 and 24 and the threshing portion 4, and the support frame 209 connecting the left and right support bases 23 and 24 is horizontally placed above the counter case 25. By connecting the left and right support bases 23 and 24 with the support frame 209, the support frame 209 can be used as a harness 210 attachment member or a reinforcement member of the support base 23 on the outside of the machine, and the structure around the counter case 25 is simplified and the rigidity is improved. Etc.
また、カウンタケース２５上面に設ける油圧機器である変速バルブ２１１のハーネス２１０を支持フレーム２０９に支持させ、支持台２３の補強部材として共用可能な支持フレーム２０９を利用してハーネス２１０を簡単に附設でき、刈取部７の側方回動による開放部に設けるカウンタケース２５の周辺構造の簡略化などを図る。また、支持台２３・２４に変速バルブ２１１のコントローラ１９４を設けると共に、刈取部７を側方回動させる支点１９９を一方の支持台２３に設け、側方に回動させる刈取部７の開放部でのメンテナンスし易い場所に支持台２３・２４を利用して前記コントローラ１９４を設置でき、カウンタケース２５とこのコントローラ１９４を近接させてカウンタケース２５の周辺構造の簡略化などを図ることができる。
Further, the harness 210 of the speed change valve 211, which is a hydraulic device provided on the upper surface of the counter case 25, is supported by the support frame 209, and the harness 210 can be easily attached using the support frame 209 that can be shared as a reinforcing member of the support base 23. Further, the peripheral structure of the counter case 25 provided in the open part by the side rotation of the cutting part 7 is simplified. Further, the support bases 23 and 24 are provided with a controller 194 for the speed change valve 211, and a fulcrum 199 for rotating the mowing unit 7 to the side is provided on one of the support bases 23, and the opening part of the mowing unit 7 for rotating sideways. The controller 194 can be installed using the support bases 23 and 24 in a place where maintenance is easy, and the counter case 25 and the controller 194 can be brought close to each other to simplify the peripheral structure of the counter case 25.
さらに、図４、図７、図８に示す如く、エンジン２１の動力を伝えるミッションケース２２と、刈取部７と、脱穀部４を設けるコンバインにおいて、刈取部７を支える支持台２４と、該支持台２４よりも前方に突設させる機台３前部のキャビンフレーム２６とに連結フレーム３４を固定させ、連結フレーム３４中間に固定させるブラケット２１２をミッションケース２２の前側に設け、ミッションケース２２に対する連結フレーム３４の取付高さ、またはミッションケース２２の上面に設ける附設部品の高さなどの制限を緩和でき、ミッションケース２２構造及び機体構成の簡略化並びに剛性向上などを図ることができると共に、ミッションケース２２の上面にドレン口２１３を設け、該ドレン口２１３にエア抜パイプ２１４を連結させ、ミッションケース２２の上面で略最高位置にドレン口２１３を設置でき、エア抜パイプ２１４の連結によってミッションケース２２のドレン構造の簡略化などを図ることができる。
Further, as shown in FIGS. 4, 7, and 8, in the combine that provides the transmission case 22 for transmitting the power of the engine 21, the cutting unit 7, and the threshing unit 4, the support base 24 that supports the cutting unit 7, and the support The connecting frame 34 is fixed to the cabin frame 26 at the front part of the machine base 3 that protrudes forward from the base 24, and a bracket 212 that is fixed in the middle of the connecting frame 34 is provided on the front side of the transmission case 22. It is possible to relax restrictions such as the mounting height of the frame 34 or the height of the accessory parts provided on the upper surface of the mission case 22, simplify the structure of the mission case 22 and the structure of the aircraft, improve rigidity, and the like. 22 is provided with a drain port 213, and an air vent pipe 214 is connected to the drain port 213 to In the upper surface of the Deployment casing 22 can be installed drain port 213 in a substantially uppermost position, and the like can be achieved simplification of the drain structure of the transmission case 22 by a connecting air disconnect pipe 214.
さらに、走行クローラ２を駆動するミッションケース２２と、エンジン２１及びラジエータ２１５を設けると共に、運転席２０を設けるキャビン１８を機台３に四角パイプ形のキャビンフレーム３２を介して支持させるコンバインにおいて、ミッションケース２２のエア抜パイプ２１４をキャビンフレーム３２に連結させるもので、別途にキャッチタンクを設ける必要がなく、ミッションケース２２に対して高位置に設けるキャビンフレーム３２の一部をエア抜パイプとして形成でき、ドレン構造の簡略化並びにコスト低減などを行うことができる。また、キャビンフレーム３２に連結させる補強フレームである連結フレーム３５にエア抜パイプ２１４の中間を支持させ、エア抜パイプ２１４の中間を変形し易い軟質ゴムホースによって形成でき、エア抜パイプ２１４構造の簡略化並びにコスト低減などを行うと共に、図２１に示す如く、ラジエータ２１５の給水ホース２１６及び給水キャップ２１７をキャビンフレーム３０にブラケット２１８を介して支持させ、エンジン２１に対して高位置に設けるキャビンフレーム３０のブラケット２１８を給水キャップ２１７の支持部材として形成でき、給水キャップ２１７支持構造の簡略化並びにコスト低減などを行うことができる。
Further, in a combine that provides a mission case 22 for driving the traveling crawler 2, an engine 21 and a radiator 215, and that supports a cabin 18 that provides a driver's seat 20 on a machine base 3 via a square pipe-shaped cabin frame 32. Since the air vent pipe 214 of the case 22 is connected to the cabin frame 32, there is no need to provide a separate catch tank, and a part of the cabin frame 32 provided at a high position with respect to the transmission case 22 can be formed as an air vent pipe. The drain structure can be simplified and the cost can be reduced. Further, the middle of the air vent pipe 214 is supported by the connecting frame 35 that is a reinforcing frame to be connected to the cabin frame 32, and the middle of the air vent pipe 214 can be formed by a soft rubber hose that is easily deformed, and the structure of the air vent pipe 214 is simplified. Further, as shown in FIG. 21, the water supply hose 216 and the water supply cap 217 of the radiator 215 are supported on the cabin frame 30 via the bracket 218 and the cabin frame 30 provided at a high position with respect to the engine 21 is provided. The bracket 218 can be formed as a support member for the water supply cap 217, and the structure for supporting the water supply cap 217 can be simplified and the cost can be reduced.
さらに、図２２、図２３に示す如く、エンジンルームカバー３１の内部にエンジン２１を設けると共に、エンジンルームカバー３１の外側で前方にラジエータ２１５を設け、エンジンルームカバー３１及びラジエータ２１５の一側に外気導入カバー１９８を後支点２１９で側方に回動自在に設けるコンバインにおいて、ラジエータ２１５のラジエータダクト２２０にオイルクーラ２２１を内設させ、オイルクーラ２２１を出入させるラジエータダクト２２０一側の開口２２２を保守カバー２２３によって閉塞し、オイルクーラ２２１のホース２２４を保守カバー２２３に挿通させ、ボルト２２５止め固定の前記保守カバー２２３を外すことによってオイルクーラ２２１を外してラジエータ２１５及びダクト２２０等のメンテナンスを行うことができ、前記ホース２２４を外す必要がなく、メンテナンス作業性の向上などを図ることができると共に、ラジエータ２１５に外気を取入れる側でラジエータ２１５に対してオイルクーラ２２１を可及的に離反させて設け、ラジエータ２１５の放熱面に充分な冷却風を均等に供給でき、ラジエータ２１５の放熱効率を向上させることができ、熱容量の大きいサイズのラジエータ２１５を設置できる。なお、ヒンジ２２６及びボルト２２７によってオイルクーラ２２１を側方に回動自在に固定させ、ボルト２２７を外してヒンジ２２６回りにオイルクーラ２２１を側方回動させてダクト２２０内部を掃除すると共に、ヒンジ２２６及びボルト２２７を外し、かつ保守カバー２２３を外し、オイルクーラ２２１をダクト２２０前側の開口２２２から出入させる。
Further, as shown in FIGS. 22 and 23, the engine 21 is provided inside the engine room cover 31, and a radiator 215 is provided in front of the engine room cover 31, and outside air is provided on one side of the engine room cover 31 and the radiator 215. In a combine in which the introduction cover 198 is provided so as to be pivotable to the side at the rear fulcrum 219, an oil cooler 221 is provided in the radiator duct 220 of the radiator 215, and an opening 222 on one side of the radiator duct 220 through which the oil cooler 221 enters and exits is maintained. Covering with the cover 223, inserting the hose 224 of the oil cooler 221 into the maintenance cover 223, and removing the maintenance cover 223 fixed with bolts 225 to remove the oil cooler 221 to perform maintenance of the radiator 215, the duct 220, and the like. The hose 224 is not required to be removed, the maintenance workability can be improved, and the oil cooler 221 is provided as far away as possible from the radiator 215 on the side where the outside air is taken into the radiator 215. Sufficient cooling air can be uniformly supplied to the heat radiation surface of the radiator 215, the heat radiation efficiency of the radiator 215 can be improved, and the radiator 215 having a large heat capacity can be installed. The oil cooler 221 is pivotally fixed to the side by the hinge 226 and the bolt 227, the bolt 227 is removed, the oil cooler 221 is turned to the side around the hinge 226, and the inside of the duct 220 is cleaned. 226 and the bolt 227 are removed, and the maintenance cover 223 is removed, and the oil cooler 221 is made to enter and exit from the opening 222 on the front side of the duct 220.
また、外気導入カバー１９８の側方回動によって開放されるエンジンルームカバー３１の側部に工具箱２２８を出入自在に設け、外気導入カバー１９８を工具箱２２８の収納蓋として仕様できると共に、工具箱２２８を収穫作業を行う運転席２０周辺場所から離して保管でき、しかも工具箱２２８を取出すとき、外気導入カバー１９８を開けるから、該カバー１９８内部のメンテナンス回数を増やして塵詰りを未然に防止できると共に、エンジン２１と外気導入カバー１９８の間にインタークーラ２２９を設け、エンジン２１とインタークーラ２２９の間に冷却ファン２３０を設け、エンジン２１に設けるターボチャージャー２３１の冷却を行うインタークーラ２２９をエンジン２１の近くでコンパクトに設置でき、ラジエータ２１５及びインタークーラ２２９のメンテナンス作業を、外気導入カバー１９８を開けて行うことができる。
In addition, a tool box 228 is provided in a side portion of the engine room cover 31 that is opened by the lateral rotation of the outside air introduction cover 198 so that the tool box 228 can freely enter and exit, and the outside air introduction cover 198 can be used as a storage lid for the tool box 228. Since the outside air introduction cover 198 is opened when the tool box 228 is taken out, the number of maintenance inside the cover 198 can be increased to prevent dust clogging. In addition, an intercooler 229 is provided between the engine 21 and the outside air introduction cover 198, a cooling fan 230 is provided between the engine 21 and the intercooler 229, and an intercooler 229 that cools the turbocharger 231 provided in the engine 21 is provided in the engine 21. Can be installed compactly near the radiator 215 and The maintenance work of Takura 229, can be performed by opening the outside air introduction cover 198.
さらに、図４、図２４に示す如く、防振ゴムを有する前側の支点軸２８によって前側を支えるステップフレーム２７の後側に防振ゴムを有する取付台２３２を設け、取付台２３２を係止台２３３に軸２３４を介して設けると共に、前記台ブラケット３３の上面３３ａと側部テーパ面３３ｂとに係止台２３３下面側を当接させ、各面３３ａ・３３ｂに係止台２３３をボルト２３５・２３６止め固定させ、キャビン１８後側をキャビンフレーム３２に着脱自在にボルト２３５・２３６止め固定させ、ボルト２３５・２３６を外してキャビン１８を支点軸２８回りに前方に回動させ、キャビン１８下方側のメンテナンス作業を行う。また、前方回動姿勢のキャビン１８を固定位置に戻すとき、前側支点軸２８の防振ゴムによってキャビン１８が左右に振れて位置がずれても、テーパ面３３ｂと係止台２３３の当接によってキャビン１８の位置を修正し、ボルト２３５・２３６によって固定できる。さらに、図２４の構造では、左右の台ブラケット３３の同じ右側面にテーパ面３３ｂを形成したが、図２５のように、左右の台ブラケット３３の外側の側面にテーパ面３３ｂを左右対称に形成することにより、キャビン１８の左右いずれの方向の振れに対しても、左右対称のテーパ面３３ｂと左右の係止台２３３によってキャビン１８の位置ずれが修正されると共に、左右の台ブラケット３３左右の係止台２３３の当接によってキャビン１８の左右方向の位置ずれが防止され、例えば図２４の構造では２本のボルト２３５・２３６を用いたのに対し、図２５の構造では１本のボルト２３５でもキャビン１８を適正に固定させることができる。
Further, as shown in FIGS. 4 and 24, a mounting base 232 having anti-vibration rubber is provided on the rear side of the step frame 27 that supports the front side by a front fulcrum shaft 28 having anti-vibration rubber, and the mounting base 232 is fixed to the locking base. 233 is provided through a shaft 234, and the lower surface side of the locking table 233 is brought into contact with the upper surface 33a and the side taper surface 33b of the base bracket 33, and the locking table 233 is attached to each surface 33a and 33b with a bolt 235. 236 is fixed, the rear side of the cabin 18 is detachably fixed to the cabin frame 32, the bolts 235 and 236 are fixed and removed, the bolts 235 and 236 are removed, the cabin 18 is rotated forward around the fulcrum shaft 28, and the cabin 18 lower side Perform maintenance work. Further, when the cabin 18 in the forward rotation posture is returned to the fixed position, even if the cabin 18 is swung to the left and right by the anti-vibration rubber of the front fulcrum shaft 28 and the position is shifted, the contact between the tapered surface 33b and the locking base 233 is caused. The position of the cabin 18 can be corrected and fixed by bolts 235 and 236. Furthermore, in the structure of FIG. 24, the tapered surface 33b is formed on the same right side surface of the left and right base brackets 33, but the tapered surface 33b is formed symmetrically on the outer side surfaces of the left and right base brackets 33 as shown in FIG. As a result, the displacement of the cabin 18 is corrected by the symmetrically tapered surfaces 33b and the right and left locking bases 233, and the left and right base brackets 33 The lateral displacement of the cabin 18 is prevented by the contact of the locking base 233. For example, in the structure of FIG. 24, the two bolts 235 and 236 are used, whereas in the structure of FIG. However, the cabin 18 can be properly fixed.
図１９、図２０において、受板１６５及び押板１６６の受圧面１８５，１８６をテーパ構造にしたが、図２６に示すように、受圧面１８５，１８６の軸穴側（内周側）を窪ませるように段部を設けて受板１６５及び押板１６６と対向する内板１６９との間に隙間Ｓを形成し、内板１６９外周側からトルクナット１７８の押圧力がトルクローラ１６７に直接作用するように構成し、トルクローラ１６７の外開きをなくして安定したトルク値を保持できるものである。
19 and 20, the pressure receiving surfaces 185 and 186 of the receiving plate 165 and the pressing plate 166 are tapered, but as shown in FIG. 26, the shaft hole side (inner peripheral side) of the pressure receiving surfaces 185 and 186 is recessed. A step S is provided so that a clearance S is formed between the receiving plate 165 and the inner plate 169 facing the pressing plate 166, and the pressing force of the torque nut 178 directly acts on the torque roller 167 from the outer peripheral side of the inner plate 169. Thus, the torque roller 167 can be kept open and a stable torque value can be maintained.
