JP2004278776A

JP2004278776A - Torque limiter

Info

Publication number: JP2004278776A
Application number: JP2003360250A
Authority: JP
Inventors: Shigemi Hidaka; 茂實日高; Yuichiro Yoshitake; 雄一郎吉武
Original assignee: Yanmar Agricultural Equipment Co Ltd
Current assignee: Yanmar Co Ltd
Priority date: 2003-02-25
Filing date: 2003-10-21
Publication date: 2004-10-07
Anticipated expiration: 2023-10-21
Also published as: JP4218829B2

Abstract

<P>PROBLEM TO BE SOLVED: To enhance durability of a torque limiter 126, to easily set the torque of the torque limiter 126 from the outside thereof, and to enhance handling property such as maintainability. <P>SOLUTION: A body side is provided inside a transmission case so as to be oil-bathed. A torque setting member is provided on the outer side of a pulley boss of a transmission pulley outside the transmission case, and the transmission pulley and the pulley boss are separately formed from each other. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は例えば左右一対の走行クローラを装設して移動するコンバインまたはトラクタまたは建設車輌などの作業車に用いるトルクリミッタに関する。 The present invention relates to a torque limiter used for a working vehicle such as a combine or tractor or a construction vehicle that moves by mounting a pair of left and right traveling crawlers.

従来、トルクリミッタとしてトルクローラを設ける技術がある。（例えば、特許文献１参照） Conventionally, there is a technique of providing a torque roller as a torque limiter. (For example, see Patent Document 1)

特開２００２−６１６６６号公報JP-A-2002-61666

前記従来技術は、例えば左右走行クローラを装設したコンバインにおいて、駆動速度を変更する油圧変速機構と、略定速で駆動する定速機構を備え、油圧変速機構と定速機構のいずれか一方によって走行部（走行クローラ）または作業部（刈取部）に駆動力を伝える場合、油圧変速機構と定速機構を切換えるときの車速差または駆動トルク差によってショックが発生し易いから、従来のようなトルクリミッタを設けてショックを緩和することが望ましい。しかし乍ら、伝動ケースにトルクリミッタを内設させることにより、トルクリミッタのトルクをセットするとき、伝動ケースを分解する必要があり、メンテナンスなどの取扱い性の向上を図り得ない等の問題がある。また、回転軸上で受板と押板を対向させ、複数組の内板とトルク板と外板を前記受板と押板の間に設け、内板を回転軸に係合させ、外板をアウタケースに係合させ、トルク板にトルクローラを設けると共に、回転軸に螺着させるトルクナットにバネ座板を係止させ、バネ座板と押板の間にバネを設けることにより、トルクリミッタのセットトルクを従来よりも大きくすることができる。しかし乍ら、受板または押板がセットトルクの押付け力によって撓み、トルクローラが不均一な面圧によって偏摩耗する等の耐久性及び精度上の問題がある。また、前記アウタケースをベアリングによって回転軸に軸支させる構造では、ベアリングのインナー部の径が小さいから、トルクローラの受圧用座金である受板を段付に形成する必要があり、受板の幅だけ取付スペースを確保する必要がある。 For example, in the prior art, for example, in a combine equipped with left and right traveling crawlers, a hydraulic speed change mechanism that changes the driving speed and a constant speed mechanism that drives at a substantially constant speed are provided, and one of the hydraulic speed change mechanism and the constant speed mechanism is used. When the driving force is transmitted to the traveling unit (traveling crawler) or the working unit (reaching unit), a shock is likely to occur due to a difference in vehicle speed or driving torque when switching between the hydraulic transmission mechanism and the constant speed mechanism. It is desirable to provide a limiter to mitigate the shock. However, when the torque of the torque limiter is set inside the transmission case, it is necessary to disassemble the transmission case when setting the torque of the torque limiter, and there is a problem that it is not possible to improve the handleability such as maintenance. . Further, the receiving plate and the pressing plate are opposed to each other on the rotating shaft, a plurality of sets of the inner plate, the torque plate and the outer plate are provided between the receiving plate and the pressing plate, the inner plate is engaged with the rotating shaft, and the outer plate is outer. The torque limiter set torque is provided by engaging the case with a torque roller on the torque plate, locking the spring seat plate on a torque nut screwed onto the rotating shaft, and providing a spring between the spring seat plate and the pressing plate. Can be made larger than before. However, there are problems in durability and accuracy such that the receiving plate or the pressing plate is bent by the pressing force of the set torque and the torque roller is unevenly worn due to uneven surface pressure. Further, in the structure in which the outer case is supported by the bearing on the rotating shaft, the diameter of the inner portion of the bearing is small. Therefore, it is necessary to form a stepped receiving plate as a pressure receiving washer of the torque roller. It is necessary to secure the mounting space by the width.

然るに、本発明は、請求項１の如く、本体側を伝動ケース内部に設けて油浴させると共に、伝動ケース外側の伝動プーリのプーリボス外側にトルクセット部材を設け、伝動プーリとプーリボスを別体で形成することを特徴とする。 Therefore, according to the present invention, the main body side is provided inside the transmission case for oil bathing, and a torque set member is provided outside the transmission pulley boss of the transmission pulley outside the transmission case, so that the transmission pulley and the pulley boss are separately provided. It is characterized by forming.

また、請求項２の如く、伝動プーリとプーリボスをボルト止め固定させると共に、車速同調入力の入切と、定速駆動入力の入切とを、同一のシフタによって行うことを特徴とする。 According to a second aspect of the present invention, the transmission pulley and the pulley boss are bolted and fixed, and the on / off of the vehicle speed tuning input and the on / off of the constant speed drive input are performed by the same shifter.

また、請求項３の如く、回転軸上で受板と押板を対向させ、複数組の内板とトルク板と外板を前記受板と押板の間に設け、内板を回転軸に係合させ、外板をアウタケースに係合させ、トルク板にトルクローラを設けると共に、回転軸に螺着させるトルクナットにバネ座板を係止させ、バネ座板と押板の間にバネを設けるトルクリミッタにおいて、トルク板に対向させる受板または押板の受圧面が、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、前記受圧面を略凹面形に形成することを特徴とする。 Further, as in claim 3, the receiving plate and the pressing plate are opposed to each other on the rotating shaft, a plurality of sets of inner plates, torque plates and outer plates are provided between the receiving plate and the pressing plate, and the inner plate is engaged with the rotating shaft. A torque limiter that engages the outer plate with the outer case, provides a torque roller on the torque plate, locks the spring seat plate on a torque nut screwed onto the rotating shaft, and provides a spring between the spring seat plate and the pressing plate. Wherein the pressure receiving surface of the pressure receiving plate or the pressing plate facing the torque plate is formed into a substantially concave shape so that the pressure receiving surface of the pressure receiving plate or the pressing plate is bent and flattened by the pressing force for generating the set torque.

また、請求項４の如く、ボス形のメタルを用いてアウタケースを回転軸に軸支させることを特徴とする。 According to a fourth aspect of the present invention, the outer case is supported on the rotating shaft by using a boss-shaped metal.

請求項１に係る発明は、トルクリミッタの本体側を油浴させることによって耐久性を向上させることができると共に、プーリボスの外側にトルクセット部材を設けるから、トルクリミッタのトルクセットを機外から容易に行うことができ、メンテナンスなど取扱い性の向上を容易に図ることができ、しかも伝動プーリとプーリボスを別体で形成し、プーリボスを取付けた状態で伝動プーリを取外すことができる。 According to the first aspect of the invention, the durability can be improved by making the main body side of the torque limiter oil bath, and the torque set member is provided outside the pulley boss, so that the torque limit of the torque limiter can be easily set from outside the machine. The transmission pulley and the pulley boss can be formed separately, and the transmission pulley can be removed with the pulley boss attached.

また、請求項２に係る発明は、伝動プーリとプーリボスをボルト止め固定させるもので、トルクリミッタのセットトルクを一定に保った状態で伝動プーリを取外してベルト交換作業などを行うことができると共に、トルクリミッタ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、同一のシフタによって行うもので、トルクリミッタ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すことができる。 Further, the invention according to claim 2 is to fix the transmission pulley and the pulley boss by bolting, and it is possible to remove the transmission pulley while maintaining the set torque of the torque limiter at a constant level and perform a belt replacement operation and the like. The same shifter turns on and off the vehicle speed tuning input and the constant speed drive input to be transmitted to the torque limiter, eliminating the problem that the vehicle speed tuning input and the constant speed drive input to be transmitted to the torque limiter are turned on at the same time. be able to.

請求項３に係る発明は、トルク板に対向させる受板または押板の受圧面が、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、前記受圧面を略凹面形に形成するもので、セットトルクを発生するときの押付け力によって受板または押板が撓んで受圧面が略平面になるから、平滑化された面圧がトルクローラ面にかかり、トルクローラ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ことができる。また、受板または押板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ものである。 According to a third aspect of the present invention, the pressure receiving surface of the receiving plate or the pressing plate facing the torque plate is formed to have a substantially concave shape so that the pressure receiving surface of the receiving plate or the pressing plate is bent and flattened by a pressing force for generating the set torque. Since the receiving plate or the pressing plate bends due to the pressing force when generating the set torque and the pressure receiving surface becomes substantially flat, the smoothed surface pressure is applied to the torque roller surface, thereby reducing uneven wear of the torque roller. Thus, the durability can be improved, and the transmission accuracy of the set torque can be improved. Further, since the pressure receiving surface pressure can be smoothed without increasing the thickness of the receiving plate or the pressing plate so as not to be distorted by the set torque, it is possible to constitute a space-saving and compact unit.

また、請求項４に係る発明は、ボス形のメタルを用いてアウタケースを回転軸に軸支させるもので、アウタケースをベアリングによって軸支させる構造に比べ、受板を段付に形成する必要がなく、例えば受板とメタルを一体形成することも可能であり、セットトルクの押付け力によって撓むことのない厚みで受板を形成することができ、コンパクトな構造で精度と耐久性を向上させることができるものである。 Further, the invention according to claim 4 uses the boss-shaped metal to support the outer case on the rotating shaft. The receiving plate needs to be formed with a step compared to a structure in which the outer case is supported by bearings. For example, it is possible to integrally form the receiving plate and metal, and it is possible to form the receiving plate with a thickness that does not bend due to the pressing force of the set torque, improving accuracy and durability with a compact structure That can be done.

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斜視図、図２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。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a perspective view of the entire combine, and FIG. 2 is a right side view thereof. In FIG. 1, reference numeral 1 denotes a pair of left and right track frames on which a pair of left and right traveling crawlers 2 are mounted. 4 is a threshing unit which is a threshing machine that has a feed cylinder 5 stretched to the left and has a built-in handling cylinder 6 and a processing cylinder. Reference numeral 7 denotes a raising mechanism 8, a cutting blade 9, a grain culm transport mechanism 10, and the like. A harvesting unit, 11 is a hydraulic lifting cylinder that raises and lowers the cutting unit 7 via a cutting frame 12, 13 is a straw processing unit that faces the end of a straw chain 14, 15 is a grain-lifting cylinder for grain from the threshing unit 4. , A grain auger for carrying out the grains of the tank 15 out of the machine, a driving cabin 18 having a driving operation handle 19 and a driver's seat 20, 21 provided below the driving cabin 18. Engine Continuously harvests culms are configured to threshing.

さらに、図３乃至図７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. 3 to 7, a transmission case 22 is disposed between the left and right traveling crawlers 2 in front of the machine base 3, and the transmission case 22 and the engine 21 are provided substantially in front of and behind the transmission case 22. In addition to transmitting the driving force of the engine 21 to the traveling crawler 2 via the thruster 4, the left and right support stands 23 and 24 are erected on the upper surface of the machine 3 in front of the threshing unit 4, and the support stands 23 and 24 are harvested via the cutting frame 12. The part 7 is provided so as to be able to move up and down and to move horizontally. 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 cutting unit 7 via 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にフックレバー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に上載させてフックレバー３３により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 above the front frame 26 via the rotation fulcrum shaft 28. The cabin 18 is rotatably supported in the front, and the left support frame 29 is erected on the right support stand 24, and the gantry 3 between the right cabin frame 30 is erected on the machine 3. The engine 21 is provided on the upper surface, and the engine 21 is covered with the engine room cover 31. Further, the upper portions of the left and right rear frames 29 and 30 are connected to each other above the cover 31 by a cabin horizontal frame 32, a hook lever 33 is provided on the cabin horizontal frame 32, and the rear portion of the step frame 27 of the cabin 18 is mounted on the horizontal frame 32. And fixed by a hook lever 33 so as to be freely detachable, a horizontal connection frame 34 is fixed between the right support base 24 and the front frame 26, and an inclined connection frame 35 is fixed between the horizontal connection frame 34 and the horizontal frame 32. Then, the frame rigidity is secured by the connection frames 34 and 35. Further, an auger support 36 is connected to the left rear frame 29, and an auger rest 37 is provided on the upper side, and the discharge auger 17 provided to be able to move up and down and pivot is supported at the main body storage position of the auger rest 37.

さらに、図８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. 8 to 12, the transmission case 22 for driving the traveling crawler 2 includes a pair of hydraulic traveling pumps 38 and a hydraulic traveling motor 39 to provide a hydraulic continuously variable transmission mechanism for traveling main speed change. And a turning member 43 that forms a hydraulic stepless transmission mechanism for turning by providing a pair of a hydraulic turning pump 41 and a hydraulic turning motor 42, and the output shaft 44 of the engine 21. The pumps 38 and 41 are connected to each other via an input shaft 45 of the transmission case 22 to drive the pumps 38 and 41.

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。 The drive shaft 49 of the traveling motor 39 is connected to the driving wheels 49 of the left and right traveling crawlers 2 via a subtransmission mechanism 47 and a differential mechanism 48 in an interlocking manner. Each planetary gear mechanism 50 includes one sun gear 51, three planetary gears 52 meshing on the outer periphery of the sun gear 51, and a ring gear 53 meshing with the 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 shaft 54 of a sun gear 51 and a carrier 56 of an axle 55 on the same axis as the carrier, so that the left and right carriers 56 are opposed to each other with the left and right sun gears 51 interposed therebetween. Has internal teeth meshing with each planetary gear 52 and is rotatably supported on an axle 55. The axle 55 is extended and the drive wheel 49 is axially supported.

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 the forward / reverse rotation and the rotation speed of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. The traveling speed change member 40 controls the rotation of the traveling motor 39 by the motor shaft 46 and the auxiliary transmission mechanism 47. Are transmitted to the left and right ring gears 53 via the low and high speed gears 57 and 58, the brake shaft 59 and the branch shaft 60 to rotate the left and right carriers 56. A parking brake 61 is provided on the brake shaft 59, and a mowing drive pulley 62 for transmitting torque to the mowing unit 7 is provided on the motor shaft 46, and the mowing unit 7 is driven at a vehicle speed tuning 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. To the left and right drive wheels 49 to drive the left and right traveling crawlers 2 in the same direction 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, a turning member 43 formed by a hydraulic stepless speed change mechanism for turning controls the forward / reverse rotation of the turning motor 42 and the rotation speed by changing the swash plate angle of the turning pump 41, and controls the steering output brake. 63, a clutch shaft 66 for providing a steering output clutch 65, and left and right input gears 67 and 68 which are always meshed with the left and right sun gears 51. A clutch shaft 66 is connected via a steering output clutch 65, and left and right input gears 67 and 68 are connected to the clutch shaft 66 via a forward rotation gear 69 and a reverse rotation gear 70. When 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 rotation motor 42 rotates forward (reverse rotation). The left sun gear 51 is rotated in the reverse direction (forward rotation) and the right sun gear 51 is rotated in the forward direction (reverse rotation) at the same left and right rotation speeds, and the left and right traveling crawlers 2 are driven in the opposite directions 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 in which 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 speed, and the left and right planetary gears are rotated. The right and left traveling crawlers 2 are driven at the same rotational speed in the same rotational direction on the left and right via the carrier 56 of the mechanism 50, and the body travels straight in the front-rear direction. On the other hand, when the traveling motor 39 is stopped and the left and right ring gears 53 are stationary and the swing motor 42 is driven forward and reverse, 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 crawlers 2 in the reverse direction, and turns the machine body to the left or right. Further, by driving the turning motor 42 while driving the traveling motor 39, the body turns left and right to correct the course, and the turning radius of the body 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 water cooling of the engine 21 is driven by the fan shaft 71. The fan shaft 71 is connected through a gear group 75, the input shaft 45 is connected to each of the pumps 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 a vehicle speed constant speed clutch. A constant speed shaft 77 is provided for connection via the constant speed shaft 76, and when the vehicle speed constant speed clutch 76 is engaged, 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 provided. Instead, the rotation of the input shaft 45 is transmitted to the auxiliary transmission mechanism 47, the left and right traveling crawlers 2 are driven by the constant speed rotation of the engine 21, and the vehicle travels at a substantially constant vehicle speed for harvesting. To perform the like. Note that a charge pump 78 is provided on the swivel 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 for adjusting the output by changing the angle of the swash plate 79 of the traveling pump 38, a transmission valve 82 for switching by connecting the main transmission lever 81 and the steering handle 19, and a traveling pump A valve 83 for decelerating the output 38 by a fixed 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 to change the angle of the swash plate 79 of the traveling pump 38 to change the rotation speed of the motor shaft 46 of the traveling motor 39 in a stepless manner or to perform a traveling speed change operation of reverse rotation. The swash plate 7 is adjusted in proportion to the amount of operation of the main shift lever 81 by performing a feedback operation in which the shift valve 82 returns to neutral 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, an auxiliary 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 auxiliary transmission cylinder 85 is hydraulically connected to the charge pump 78 via an electromagnetic auxiliary transmission valve 86. Is neutral, the sub transmission cylinder 85 is short-circuited to the transmission case 22 as an oil tank, the swash plate 84 angle of the traveling motor 39 is changed by the main circuit oil pressure, and the swash plate 84 angle is changed by switching the sub transmission valve 86. The output is forcibly changed to change the output of the traveling motor 39 to high speed or low speed.

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 swing cylinder 88 for adjusting the output by changing the angle of the swash plate 87 of the swing pump 41 is provided. The swing cylinder 89 is connected to the steering handle 19 and the main shift lever 81 for switching, and a solenoid automatic steering valve 90 is provided. The charge pump 78 is hydraulically connected to the swivel cylinder 88, the swivel valve 89 is switched by the steering handle 19, and the swivel cylinder 88 is operated to change the angle of the swash plate 87 of the swivel pump 41. A left-right turning operation for continuously changing or reversing the rotation speed is performed, and a feedback operation for returning the turning valve 89 to neutral by the angle adjusting 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。 When the main shift lever 81 is operated to a position other than the neutral position and the steering handle 19 is operated to a position other than the straight traveling, the hydraulic output of the traveling pump 38 is adjusted in proportion to the operation direction and the operation amount of the main shift lever 81. In addition to changing the forward / backward speed or the speed of the hydraulic motor 39 to change the forward / backward speed (vehicle speed), the output of the swing pump 41 is changed in proportion to the operation amount of the main shift lever 81. The turning radius is automatically reduced, and the turning radius is automatically increased by the low speed running speed change. The turning radius of the left and right running crawlers 2 is maintained substantially constant by the constant operation of the steering wheel 19 regardless of the running speed. Then, the work traveling speed is changed, and the course is adjusted so that the aircraft follows the uncut culm row. On the other hand, when the turning radius (steering angle) is reduced (increased) by changing the output of the turning pump 41 and the output of the traveling pump 38 by controlling the valves 82 and 89 in proportion to the operation amount of the steering handle 19, the traveling speed is reduced. (Vehicle speed) is reduced in proportion to the speed difference between the left and right traveling crawlers 2 and the vehicle is turned left and right. The driving speed of the left and right traveling crawlers 2 is changed to correct the alignment path and to make a headland. The direction change by the spin turn in, and the harvesting work of cutting and threshing the stalk continuously. When the main shift lever 81 is neutral, the turning valve 89 is maintained neutral regardless of the operation of the steering handle 19, the hydraulic output of the turning pump 41 is maintained at substantially zero, and the turning motor 42 is stopped.

さらに、図１１乃至図１８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. 11 to 18, the output shaft 44 of the engine 21 is protruded forward and rearward, and the input shaft 45 is connected to the front 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 unit 4 on the left side of the engine 21, and an input pulley 92, a vehicle speed tuning pulley 93, a threshing pulley 94, a cutting pulley 95, and a sorting pulley 96 are countered. The input pulley 92 on the rear side of the case 25 is connected to the work output pulley 91 via a tension threshing clutch 97 via a belt 98, and the driving force of the engine 21 is transmitted to the counter case 25. Also, the vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected to the mowing drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support stand 24 with the belt 100, and is erected on the front upper surface of the machine base 3. The cutting input case 101 is rotatably supported on the support bases 23 and 24, the 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, and the cutting pulley 95 on the left side of the counter case 25 is connected to the cutting input pulley 103 by the belt 104, and the driving force is transmitted to each section of the cutting section 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。 A threshing pulley 94 on the front side of the counter case 25 is connected to a belt 106 to a drive input pulley 105 of the handling cylinder 6, and a driving force is transmitted from a sorting pulley 96 to a sorting machine and a swing sorting mechanism below the handling cylinder 6 to thresh. 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 a drive sprocket 108 of the feed chain 5 which can move outward. Further, a discharge drive pulley 109 is provided in front of the grain tank 15, and the pulley 109 is connected to the work output pulley 91 by a belt via a discharge clutch 110, and the output of the engine 21 is transmitted to the discharge auger 17 to transmit the grain of the tank 15. Let the grains drain.

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 handle case input shaft 111 is pivotally supported on the counter case 25, the shaft 111 is extended in the front-rear direction, and a threshing pulley 94 is provided on the front side of the shaft 111 outside the front 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 handle input shaft 111 to rotate the engine 21 at a constant speed. A tuning input shaft 112 is supported on the right side of the counter case 25, and a vehicle speed tuning pulley 93 is provided on the right side of the shaft 112 on the right outside of the counter case 25, and a belt is provided between the pulleys 62 and 93 via an idle pulley 99. 100 is tensed, and vehicle speed tuning power is input from the transmission 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, a constant speed shaft 114, which is a counter shaft or a sorting input shaft for connecting the right side of the handle cylinder input shaft 111 to the bevel gear 113, and a vehicle speed tuning shaft 115 provided substantially in front of the shaft 114, are mounted on the counter case 25. A one-way clutch 120 is provided on the tuning input shaft 112 for supporting and transmitting the vehicle speed tuning rotational force of the tuning input shaft 112, and the gear 117 and the reaping clutch 118 for transmitting the power from the vehicle speed tuning pulley 93 by the one-way clutch 120. The configuration is such that the vehicle speed tuning shaft 115 is rotated via the motor.

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 constant cutting speed clutch 122 forming a constant cutting speed mechanism 121 and a high-speed cut gear 123 are provided between the shafts 114 and 115, and the respective gear clutches are switched by a switching shifter 124 for tuning the cutting unit 7 to a vehicle speed or high-speed cutting drive. 118 and 122 are selectively engaged to drive the reaper 7 in synchronization with the vehicle speed to drive the reaper 7 at a speed linked to the traveling speed, while driving the reaper 7 in high-speed cut drive to achieve the highest speed of vehicle speed synchronization. The cutting unit 7 is driven at a higher constant rotation speed to cut the lodging culm.

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１２９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 projected to the lower rear side on the left side of the counter case 25, and the selection pulley 96 is pivotally supported at the left end of the shaft 114. Further, a mowing transmission shaft 125 is axially supported on the lower front side on the left side of the counter case 25, and the right side of the shaft 125 is connected to a vehicle speed tuning shaft 115 via a torque limiter 126 so that the shaft 125 protrudes to the left side of the counter case 25. A cutting pulley 95 is pivotally supported on the left end, a cutting drive shaft 127 is connected to the cutting input shaft 102 by a gear 128, and the cutting input pulley 103 is pivotally supported by the cutting drive shaft 127, and transmitted to a torque limiter 126. The turning on and off of the vehicle speed tuning input and the turning on and off of the constant speed driving input are performed by the same shifter 124, eliminating 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 control of transmission switching is not required to improve handling. Further, a case of the gear 128 is provided on the left support stand 23 via a fulcrum shaft 129 so as to be rotatable around the vertical axis, and the left side of the cutting input case 101 is fixed to the case of the gear 128. A gear 128 is provided inside, a mowing power is input from the left end side of the mowing input shaft 102, and the mowing unit 7 is driven via a mowing transmission shaft 130 inserted into the mowing 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 to the left of the machine body, and maintenance and the like near the respective cases 22 and 25 inside the machine body are 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 supported on the upper left side of the counter case 25, and the input shaft 107 is connected to a feed chain drive shaft 132 provided with a feed chain clutch 131 by a chain 133. Is provided by a feed chain transmission mechanism 134 for transmitting the gears by changing the rotation speed of the vehicle speed tuning shaft 115, and the mechanism 134 is formed to be continuously variable by a planetary gear mechanism 138 including a sun gear 135, a planetary gear 136, and a ring gear 137. A sun gear 135 is engaged with the constant speed shaft 114, and a ring gear 137 that idles and supports the constant speed shaft 114 is connected to the vehicle speed tuning shaft 115 with a gear 139, and a bearing body 140 that idles and supports the planetary gear 136 is fixed. The idler is supported by the speed shaft 114, A gear 141 is connected to the feed chain drive shaft 132 through a clutch 131 to form a gear 141, and the feed chain 5 speed is changed from a constant low speed to a high speed while maintaining the minimum rotation required for conveying the grain. It is configured to be synchronized and changeable.

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 harvesting constant speed cylinder 143 for operating the switching shifter 124 and a hydraulic threshing cylinder 144 for engaging the threshing clutch 97 are fixed to an oil passage base 145 which is an upper cover of the counter case 25 and the vehicle speed constant. A vehicle speed constant speed valve 147 for operating the vehicle speed constant speed cylinder 146 for turning on the speed clutch 76, a cutting constant speed valve 149 for operating the cutting constant speed cylinder 143, and a threshing valve 150 for operating the threshing cylinder 144, A hydraulic connection is made to the charge pump 78 in parallel.

さらに、図１９、図２０に示す如く、前記脱穀クラッチ９７をテンションアーム１５１に軸支させ、カウンタケース２５の支軸１５２にテンションアーム１５１を回転自在に軸支させ、折曲自在な２本のリンク１５３・１５４を介して脱穀シリンダ１４４のピストンロッド１５５をテンションアーム１５１に連結させ、ピストンロッド１５５の押し（進出）動作により、脱穀クラッチ９７を入動作させてベルト９８を緊張させる一方、ピストンロッド１５５の引き（退入）動作により、脱穀クラッチ９７を切動作させてベルト９８を弛める。また、脱穀クラッチ９７を切り側に弾圧させるバネ１５６をリンク１５４に連結させる。 Further, as shown in FIGS. 19 and 20, the threshing clutch 97 is rotatably supported by a tension arm 151, and the tension arm 151 is rotatably supported by a support shaft 152 of the counter case 25. While the piston rod 155 of the threshing cylinder 144 is connected to the tension arm 151 via the links 153 and 154, the thrusting clutch 97 is engaged by the pushing (advancing) operation of the piston rod 155 to tension the belt 98, while the piston rod By the pulling (retreating) operation of 155, the threshing clutch 97 is disengaged to loosen the belt 98. Further, a spring 156 for urging the threshing clutch 97 toward the disengagement side is connected to the link 154.

さらに、図１７、図１８に示す如く、前記カウンタケース２５に形成する締結座１８５を機台３にボルト１８６止め固定させると共に、カウンタケース２５の機外側に分離ケース１８７を着脱自在にボルト１８８止め固定させ、カウンタケース２５の一部を分離ケース１８７によって形成し、分離ケース１８７の脱着によってカウンタケース２５の機外側面を開閉自在に形成するもので、カウンタケース２５と分離ケース１８７とに、前記各軸１０７・１１４・１１５・１２５・１３２を軸支させ、カウンタケース２５上面の油路ベース１４５開口に比べ、分離ケース１８７を外したときのケース２５機外側面の開口面積を大きくし、各軸１０７・１１４・１１５・１２５・１３２の脱着及びギヤ交換などを行えるように構成している。 Further, as shown in FIGS. 17 and 18, a fastening seat 185 formed in the counter case 25 is fixedly fastened to the machine base 3 by a bolt 186, and a separation case 187 is detachably fastened to the machine case 3 outside the counter case 25 by a bolt 188. The counter case 25 is fixed, a part of the counter case 25 is formed by the separation case 187, and the outer surface of the counter case 25 is formed to be openable and closable by attaching and detaching the separation case 187. Each of the shafts 107, 114, 115, 125, and 132 is pivotally supported, and the opening area of the outer surface of the case 25 when the separation case 187 is removed is increased as compared with the opening of the oil passage base 145 on the upper surface of the counter case 25. The shafts 107, 114, 115, 125, and 132 are configured to be removable and gears can be replaced.

さらに、図２１に示す如く、作業レバー１８９の脱穀操作を検出する脱穀スイッチ１９０と、作業レバー１８９の刈取操作を検出する刈取スイッチ１９１と、主変速レバー８１の高速前進及び後進の切換を検出する高速運転スイッチ１９３及び後進スイッチ１９４と、低速・高速の副変速切換を行う副変速スイッチ１９７とを、マイクロコンピュータで構成する作業コントローラ１９８に接続させる。 Further, as shown in FIG. 21, a threshing switch 190 for detecting a threshing operation of the work lever 189, a reaper switch 191 for detecting a reaping operation of the work lever 189, and detection of switching between a high speed forward movement and a reverse movement of the main shift lever 81. The high-speed operation switch 193 and the reverse switch 194, and the sub-transmission switch 197 for switching between low-speed and high-speed sub-transmission are connected to a work controller 198 composed of a microcomputer.

また、エンジン２１の一定回転出力によって刈取部７を駆動する動作に手動で切換える直接駆動スイッチ１９９と、該スイッチ１９９の手動入力を入切する自動スイッチ２００と、左右の走行クローラ２の速度（車速）を検出する左及び右車速センサ２０１・２０２と、刈取部７の搬送穀稈の有無を検出する穀稈センサ２０３と、刈取部７に車速同調の駆動力を入力する同調入力軸１１２の入力回転数を低速ギヤ１１７を介して検出する刈取入力センサ２０４と、フィードチェンクラッチ１３１を切にするようにフィードチェンクラッチシリンダを作動させるフィードチェンソレノイド１９１と、定速シリンダ１４３により切換シフタ１２４を高速カットギヤ１２３係合動作させる高速カットソレノイド２０９と、刈取クラッチ１１８を入にする刈取クラッチソレノイド２１０とを、作業コントローラ１９８に接続させ、図２２のフローチャートのように、刈取部７を、高速カット速度または車速同調速度で作動させる。 Further, a direct drive switch 199 for manually switching to an operation for driving the mowing unit 7 by a constant rotation output of the engine 21, an automatic switch 200 for turning on / off the manual input of the switch 199, a speed of the left and right traveling crawlers 2 (vehicle speed) ), Right and left vehicle speed sensors 201 and 202, a cereal stalk sensor 203 for detecting the presence or absence of a transported cereal culm of the mowing unit 7, and an input of a tuning input shaft 112 for inputting a driving force of vehicle speed tuning to the mowing unit 7. The switching shifter 124 is driven at a high speed by a cutting input sensor 204 for detecting the number of revolutions via the low-speed gear 117, a feed chain solenoid 191 for operating the feed chain clutch cylinder so as to disconnect the feed chain clutch 131, and a constant speed cylinder 143. The high-speed cut solenoid 209 for engaging the cut gear 123 and the cutting clutch 118 are turned on. A clutch solenoid 210 reaper that, is connected to the work controller 198, as shown in the flowchart of FIG. 22, the reaper 7 is operated at a high speed cutting speed or the vehicle speed synchronization speed.

また、前記の自動スイッチ２００がオンの状態下で高速運転スイッチ１９３がオンになったときに定速クラッチ７６を入にする高速運転ソレノイド２１１と、前記の副変速スイッチ１９７の切換によって副変速シリンダ８５を作動させて走行モータ３９を低速または高速出力にする副変速用低速及び高速ソレノイド２１２・２１３と、前記脱穀スイッチ１９０のオンによって脱穀クラッチ９７を入にする脱穀クラッチソレノイド２１４とを、作業コントローラ１９８に接続させる。 A high-speed operation solenoid 211 that turns on the constant-speed clutch 76 when the high-speed operation switch 193 is turned on while the automatic switch 200 is on, and a sub-transmission cylinder by switching the sub-transmission switch 197. The operation controller includes a low-speed and high-speed solenoids 212 and 213 for sub-transmission for operating the traveling motor 39 at low speed or high-speed output, and a threshing clutch solenoid 214 for turning on the threshing clutch 97 by turning on the threshing switch 190. 198.

さらに、図２２のフローチャートに示す如く、作業レバー１８９の操作により脱穀スイッチ１９０がオンになると、フィードチェンソレノイド２０７をオフにしてフィードチェンクラッチ１３１を入にし、フィードチェン５の駆動を開始し、かつ脱穀クラッチソレノイド２１４を作動させて脱穀クラッチ９７を入にし、脱穀部４とフィードチェン５を駆動する。また、作業レバー１８９の操作により刈取スイッチ１９１がオンになると、刈取クラッチ１１８が入になり、車速同調プーリ９３を介して主変速駆動力が刈取部７に伝達される。 Further, as shown in the flowchart of FIG. 22, when the threshing switch 190 is turned on by operating the work lever 189, the feed chain solenoid 207 is turned off, the feed chain clutch 131 is turned on, and the drive of the feed chain 5 is started, and The threshing clutch solenoid 214 is operated to turn on the threshing clutch 97 and drive the threshing unit 4 and the feed chain 5. Further, when the cutting switch 191 is turned on by operating the work lever 189, the cutting clutch 118 is turned on, and the main transmission driving force is transmitted to the cutting unit 7 via the vehicle speed tuning pulley 93.

また、後進スイッチ１９４がオフのときで、車速センサ２０１・２０２によって検出する車軸５５が駆動されていると、走行モータ３９の副変速出力が低速のときで、刈取入力センサ２０４が検出する刈取部７の車速同調の入力回転が高速カットギヤ１２３による回転設定以上のとき、高速カットソレノイド２０９を作動させ、高速カットギヤ１２３を介して刈取部７を最高速で定速駆動する高速カット動作を行わせる。 Also, when the reverse switch 194 is off and the axle 55 detected by the vehicle speed sensors 201 and 202 is driven, the mowing unit detected by the mowing input sensor 204 when the sub-shift output of the traveling motor 39 is low. When the input rotation of the vehicle speed synchronization of 7 is equal to or greater than the rotation setting by the high-speed cut gear 123, the high-speed cut solenoid 209 is operated to perform a high-speed cutting operation for driving the reaping unit 7 at a constant speed at the highest speed via the high-speed cut gear 123.

また、走行モータ３９の副変速出力が低速のときで、刈取部７の入力回転が設定以下のときで、自動スイッチ２００がオンのとき、直接駆動スイッチ１９９がオン操作されると、高速運転ソレノイド２１１を作動させて車速定速クラッチ７６を入にし、走行変速部材４０を介することなく、エンジン２１の駆動力を定速クラッチ７６から副変速機構４７に直接伝達させ、高速運転動作させる。 Also, when the sub-shift output of the traveling motor 39 is low, the input rotation of the mowing unit 7 is lower than a set value, the automatic switch 200 is on, and the direct drive switch 199 is directly turned on, the high-speed operation solenoid By operating the 211, the vehicle speed constant speed clutch 76 is turned on, and the driving force of the engine 21 is directly transmitted from the constant speed clutch 76 to the subtransmission mechanism 47 without going through the traveling speed change member 40, thereby performing a high-speed driving operation.

さらに、図１３、図１４、図２３乃至図２８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１８７にトルクリミッタ取付け孔２１９を開設させ、前記取付け孔２１９に軸受蓋２２０を外側から嵌合させて着脱自在にボルト２２１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２２０に刈取伝動軸１２５の中間をベアリング軸受２２２により回転自在に軸支させる。 Further, as shown in FIGS. 13, 14, and 23 to 28, a torque limiter 126 is provided on the mowing transmission shaft 125, and a detachable separation case 187 forming a part of the side wall of the counter case 25 is provided. A torque limiter mounting hole 219 is opened, a bearing cover 220 is fitted into the mounting hole 219 from the outside, and the bolt 221 is detachably fixed and fixed. The middle of the transmission shaft 125 is rotatably supported by a bearing 222.

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、軸受段部２２４と、スプライン２２５と、ネジ２２６を形成し、平ギヤ形のリミッタ伝動ギヤ２２７を軸受段部２２４にベアリング軸受２２８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２２０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２２０及びボルト２２１の着脱を行うと共に、前記ギヤ２２７の外径を取付け孔２１９よりも小さく形成し、ギヤ２２７を軸１２５に取付けた状態で、取付け孔２１９に軸１２５と軸受蓋２２０の嵌合部を出入させるもので、前記ギヤ２２７を噛合させる平ギヤ２２９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２２７を連結させる。 Further, a cutting pulley 95 is key-fitted and fixed to one end of a cutting transmission shaft 125 protruding outside the counter case 25, and a bearing step is mounted on the other end of the cutting transmission shaft 125 to be inserted inside the counter case 25. A part 224, a spline 225, and a screw 226 are formed, and a flat gear type limiter transmission gear 227 is rotatably supported on the bearing step part 224 via a bearing 228. The outer diameter of the pulley 95 is made larger than the outer diameter of the bearing lid 220, and the bearing lid 220 and the bolt 221 are attached and detached while the pulley 95 is removed from the shaft 125, and the outer diameter of the gear 227 is attached. The flat gear 229 is formed smaller than the hole 219 so that the fitting portion between the shaft 125 and the bearing lid 220 enters and exits the mounting hole 219 in a state where the gear 227 is mounted on the shaft 125. The vehicle speed tuning shaft 115 is engaged and supported, and the limiter transmission gear 227 is connected to the vehicle speed tuning shaft 115.

さらに、前記リミッタ伝動ギヤ２２７の側面に一体形成する円筒形のアウタケース２３０と、刈取伝動軸１２５上で対向させるドーナツ板形の受板２３１及び押板２３２と、同一円周上に複数のトルクローラ２３３を略等間隔に配列させるドーナツ板形のトルク板２３４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２３４のトルクローラ２３３を挾持させるドーナツ平板形の内板２３５及び外板２３６と、前記ネジ２２６に螺着させて押板２３２に圧接させる着脱自在なナット２２３及び座金１８１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２３０などを配設させて油浴させる。 Further, a cylindrical outer case 230 integrally formed on the side surface of the limiter transmission gear 227, a donut plate-shaped receiving plate 231 and a push plate 232 opposed on the cutting transmission shaft 125, and a plurality of torques on the same circumference. A donut plate-shaped torque plate 234 in which the rollers 233 are arranged at substantially equal intervals; a donut plate-shaped inner plate 235 for clamping the torque roller 233 of the torque plate 234 from both sides of the cutting power transmission shaft 125 facing each other in the axial direction; An outer plate 236 and a detachable nut 223 and a washer 181 screwed to the screw 226 and pressed against the push plate 232 are provided in the torque limiter 126, and the outer case of the torque limiter 126 body side is provided inside the counter case 25. 230 and so on to be oil bathed.

そして、軸受蓋２２０に刈取伝動軸１２５を軸支させ、該軸１２５の軸受段部２２４にリミッタ伝動ギヤ２２７を抜出し自在に軸支させ、アウタケース２３０の内孔２４０に受板２３１を内挿させ、複数組の内板２３５とトルク板２３４と外板２３６をアウタケース２３０に内挿させ、刈取伝動軸１２５のスプライン２２５に内板２３５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２３０のキー溝２４１に外板２３６外周の突起形キー２４２を係合させる。また、トルクバネ２３９を支持させた座板２３８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のネジ１８２にトルクナット２３７を螺着させ、トルクリミッタ１２６を軸受蓋２２０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２３７を締付けてトルクバネ２３９力を調節し、トルクローラ２３３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１８３とを各別に形成し、プーリ９５とボス１８３を着脱自在にボルト１８４止め固定させ、プーリボス１８３を刈取伝動軸１２５にキー嵌合させ、プーリボス１８３の機外側面にトルクバネ２３９を圧接させ、カウンタケース２５の外側にトルクナット２３７及びバネ２３９を設ける。 The cutting cover transmission shaft 125 is supported by the bearing cover 220, and the limiter transmission gear 227 is supported by the bearing step portion 224 of the shaft 125 so that the limiter transmission gear 227 can be pulled out, and the receiving plate 231 is inserted into the inner hole 240 of the outer case 230. Then, a plurality of sets of the inner plate 235, the torque plate 234, and the outer plate 236 are inserted into the outer case 230, and the spline 225 of the cutting power transmission shaft 125 is engaged with the inner hole of the inner plate 235 at an interval of approximately 120 degrees. Is engaged with the key 241 of the outer case 230 provided on the outer case 236. Further, a seat plate 238 supporting a torque spring 239 is rotatably supported on an outer end of the mowing transmission shaft 125, a torque nut 237 is screwed on a screw 182 of the shaft 125, and the torque limiter 126 is fixed to a bearing cover. It is assembled in a unit structure with 220 and the mowing transmission shaft 125, and tightens the torque nut 237 to adjust the force of the torque spring 239 to set the transmission torque of the torque roller 233. Further, the cutting pulley 95 and the pulley boss 183 are separately formed, the pulley 95 and the boss 183 are detachably fixed with bolts 184, and the pulley boss 183 is key-fitted to the cutting transmission shaft 125. A torque spring 239 is pressed against the side surface, and a torque nut 237 and a spring 239 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２４３を形成し、油穴２４３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２４３の他端側を刈取伝動軸１２５のスプライン２２５形成部の周面に開口させると共に、スプライン２２５に嵌合させる内板２３５の内孔に油通し用の切欠２４４を形成し、多層形の各トルク板２３４のトルクローラ２３３に、油穴２４３及び切欠２４４を介し、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２４３からトルクローラ２３３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２３３に油を送って強制潤滑する。 Further, an L-shaped oil hole 243 is formed in the shaft core of the cutting power transmission shaft 125, one end of the oil hole 243 is opened inside the counter case 25 at the end surface of the shaft 125, and the other end of the oil hole 243 is cut. An opening is formed on the peripheral surface of the spline 225 forming portion of the transmission shaft 125, and a cutout 244 for passing oil is formed in an inner hole of the inner plate 235 fitted to the spline 225, and the torque roller 233 of each of the multi-layered torque plates 234 is formed. The oil in the case 25 is moved from the oil hole 243 toward the torque roller 233 by the centrifugal force generated by the rotation of the mowing transmission shaft 125 through the oil hole 243 and the notch 244, and the centrifugal force forces the oil to the torque roller 233. To forcibly lubricate.

さらに、前記トルクローラ２３３の円柱形に対して平面視で相似する長方形の支持孔２４５をトルク板２３４に形成し、トルクローラ２３３を支持孔２４５に回転自在に内挿させると共に、支持孔２４５の対向する長辺側の開口縁に一対の舌片２４６を対向させて設け、トルクローラ２３３の外周に舌片２４６を摺接させる。また、トルク板２３４の外周に形成する折曲げ縁２４７と同一方向に舌片２４６を突設させ、トルク板２３４の軸芯方向の幅をトルクローラ２３３の外径よりも小さく形成し、トルク板２３４の両側面にトルクローラ２３３の外周側を突出させて内板２３５と外板２３６に摺接させると共に、ホルダを形成する一対の舌片２４６の先端側をトルクローラ２３３の円周方向に折曲げ、トルクローラ２３３の外周を一対の舌片２４６によって回転自在に挾持させる。 Further, a rectangular support hole 245 which is similar to the cylindrical shape of the torque roller 233 in a plan view is formed in the torque plate 234, and the torque roller 233 is rotatably inserted into the support hole 245. A pair of tongue pieces 246 are provided so as to be opposed to the opening edges on the long sides facing each other, and the tongue pieces 246 are slid on the outer periphery of the torque roller 233. A tongue piece 246 projects in the same direction as the bent edge 247 formed on the outer periphery of the torque plate 234, and the width of the torque plate 234 in the axial direction is smaller than the outer diameter of the torque roller 233. The outer peripheral side of the torque roller 233 protrudes from both side surfaces of the torque roller 233 so as to be in sliding contact with the inner plate 235 and the outer plate 236, and the distal ends of a pair of tongue pieces 246 forming a holder are bent in the circumferential direction of the torque roller 233. The outer periphery of the bending and torque roller 233 is rotatably clamped by a pair of tongue pieces 246.

さらに、前記トルク板２３４の回転中心２４７を通過する放射線２４８に対してトルクローラ２３３の軸芯線２４９をトルク板２３４の回転下手側に一定の傾斜角度θで傾斜させるもので、転動軸芯線２４９がトルク板２３４の回転中心を含む平面（放射線２４８）に対して角度θだけ傾斜するようにトルクローラ２３３を配置させる構成において、車速同調軸１１４の平ギヤ２２９を介してアウタケース２３０を回転駆動させると、各トルクローラ２３３が内板２３５と外板２３６に接しながら転動してトルク板２３４も回転する。このとき、各トルクローラ２３３は、外板２３６の回転軌道に対して前記角度θだけ傾斜した方向に転動しようとするのを、トルク板２３４で規制されながら外板２３６の回転軌道の方向に移動するため、前記トルクバネ２３９圧に比例した摩擦抵抗が発生し、しかも、各トルクローラ２３３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２２９側の入力速度の変更によりアウタケース２３０の回転速度が高速側に急変したとき、内板２３５と外板２３６の各回転トルク差が増大してトルクローラ２３３の摩擦抵抗力よりも大きくなることにより、内板２３５と外板２３６がトルクローラ２３３に対して摺動して伝達動力が遮断される。 Further, the axis 249 of the axis of the torque roller 233 is inclined toward the lower side of the rotation of the torque plate 234 at a constant inclination angle θ with respect to the radiation 248 passing through the rotation center 247 of the torque plate 234. Is arranged so that the torque roller 233 is inclined by an angle θ with respect to a plane (radiation 248) including the rotation center of the torque plate 234, and the outer case 230 is rotationally driven via the spur gear 229 of the vehicle speed tuning shaft 114. Then, the torque rollers 233 roll while contacting the inner plate 235 and the outer plate 236, and the torque plate 234 also rotates. At this time, each of the torque rollers 233 attempts to roll in the direction inclined by the angle θ with respect to the rotational path of the outer plate 236 in the direction of the rotational path of the outer plate 236 while being regulated by the torque plate 234. As a result, a frictional resistance proportional to the pressure of the torque spring 239 is generated, and the respective torque rollers 233 generate sliding friction while rolling, so that static friction is not generated, and a stable frictional resistance due to dynamic friction is always generated. can get. Also, when the mowing drive load on the mowing transmission shaft 125 increases, or when the rotation speed of the outer case 230 suddenly changes to a high speed side due to a change in the input speed on the spur gear 229 side, each of the inner plate 235 and the outer plate 236 When the rotational torque difference increases and becomes larger than the frictional resistance of the torque roller 233, the inner plate 235 and the outer plate 236 slide with respect to the torque roller 233, 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を設けるもので、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、前記の各機構４０・１２１を切換えるときのショックを低減させ、取扱い性を向上させると共に、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するもので、トルクリミッタ１２６に対して充分に潤滑を行わせ、耐久性を向上させ、安定したトルクを得る。 As described above, one of the hydraulic transmission mechanism 40 and the constant speed mechanism 121 transmits the driving force to the reaping unit 7 which is a working unit, and the torque limiter 126 is attached to the reaping transmission shaft 125 for rotating the reaping unit 7 at a constant speed. The torque limiter 126 absorbs a shock caused by a difference in driving torque when switching between the hydraulic transmission mechanism 40 and the constant speed mechanism 121, and reduces the shock when switching between the mechanisms 40 and 121, thereby improving handling. In addition, the hydraulic oil level inside the counter case 25 in which the torque limiter 126 is installed is made higher than the position where the shaft 125 of the torque limiter 126 is installed. Performance and obtain stable torque.

上記のように、トルクリミッタ１２６の本体側を伝動ケースであるカウンタケース２５内部に設けて油浴させると共に、カウンタケース２５外側の伝動プーリである刈取プーリ９５のプーリボス１８３外側にトルクリミッタ１２６のトルクセット部材であるトルクナット２３７及びトルクバネ２３９を設け、トルクリミッタ１２６の本体側を油浴させることによって耐久性を向上させると共に、プーリボス１８３の外側にトルクナット２３７及びトルクバネ２３９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１８３を別体で形成し、刈取プーリ９５とプーリボス１８３をボルト１８４止め固定させ、プーリボス１８３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い、取扱い性の向上などを図る。 As described above, the main body side of the torque limiter 126 is provided inside the counter case 25 which is a transmission case to allow an oil bath, and the torque of the torque limiter 126 is provided outside the pulley boss 183 of the cutting pulley 95 which is a transmission pulley outside the counter case 25. A torque nut 237 and a torque spring 239, which are set members, are provided to improve durability by oil bathing the main body side of the torque limiter 126, and a torque nut 237 and a torque spring 239 are provided outside the pulley boss 183 to provide a torque limiter 126. Torque setting is performed from outside the machine to improve handling such as maintenance. Also, the cutting pulley 95 and the pulley boss 183 are formed separately, the cutting pulley 95 and the pulley boss 183 are fixed by bolts 184, and the pulley boss 183 is mounted. Mowing pooh Remove the 95, remove the pulleys 95 cutting while maintaining the set torque of the torque limiter 126 fixed perform a belt replacement, achieving such improvement in handling property.

また、伝動軸１２５にベアリング軸受２２８を介して伝動ギヤ２２７を回転自在に軸支させ、前記伝動ギヤ２２７の一側にアウタケース２３０を一体形成するもので、トルクリミッタ１２６の構成部品数の削減並びにコンパクト化を行い、かつ伝動軸１２５に対してトルクリミッタ１２６の本体側をユニット構成して組立性及びメンテナンス性などを向上させる。また、伝動軸１２５の中間を伝動ケースである軸受蓋２２０に軸受２２２を介して軸支させ、軸受蓋２２０の内部に突設させる伝動軸１２５の一端側にトルクリミッタ１２６の本体側を設け、軸受蓋２２０の外部に突設させる伝動軸１２５の他端側に伝動輪であるプーリ９５とトルクナット２３７などのトルクセット部材とを設けるもので、例えば分離自在な軸受蓋２２０に伝動軸１２５を軸支させることにより、分離する側の軸受蓋２２０と一体的にトルクリミッタ１２６を着脱させる一方、カウンタケース２５にトルクリミッタ１２６及びプーリボス１８３を設けて状態でプーリ９５だけを取外すことが可能で、組立性及びメンテナンス性などを向上させる。 Further, the transmission gear 227 is rotatably supported on the transmission shaft 125 via a bearing 228, and the outer case 230 is integrally formed on one side of the transmission gear 227, so that the number of components of the torque limiter 126 is reduced. In addition, the size of the main body of the torque limiter 126 with respect to the transmission shaft 125 is reduced as a unit, so that assemblability and maintainability are improved. Further, a body of the torque limiter 126 is provided at one end of the transmission shaft 125 which is supported by a bearing lid 220 serving as a transmission case via a bearing 222 at an intermediate portion of the transmission shaft 125 and protrudes inside the bearing lid 220, A pulley 95 serving as a transmission wheel and a torque setting member such as a torque nut 237 are provided on the other end side of the transmission shaft 125 protruding outside the bearing cover 220. For example, the transmission shaft 125 is mounted on the separable bearing cover 220. By supporting the shaft, the torque limiter 126 can be attached and detached integrally with the bearing cover 220 on the side to be separated, while the torque limiter 126 and the pulley boss 183 are provided on the counter case 25, and only the pulley 95 can be removed in a state. Improves ease of assembly and maintenance.

さらに、図２９、図３０に示す如く、回転軸１２５上で受板２３１と押板２３２を対向させ、複数組の内板２３５とトルク板２３４と外板２３６を前記受板２３１と押板２３２の間に設け、内板２３５を回転軸１２５に係合させ、外板２３６をアウタケース２３０に係合させ、トルク板２３４にトルクローラ２３３を設けると共に、回転軸１２５に螺着させるトルクナット２３７にバネ座板２３８を係止させ、バネ座板２３８と押板２３２の間にバネ２３９を設けるトルクリミッタにおいて、トルク板２３４に対向させる受板２３１または押板２３２の受圧面２３１ａ、２３２ａ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２３１ａ、２３２ａを略凹面形に形成するもので、受板２３１及び押板２３２の各受圧面２３１ａ、２３２ａを、傾斜角Ａ１、Ａ２をなすテーパこ構造にし、各板２３１、２３２の外周側が内板２３５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２３１ａ、２３２ａ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２３１または押板２３２が撓んで受圧面２３１ａ、２３２ａが略平面になり、平滑化された面圧がトルクローラ２３３面にかかり、トルクローラ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ことができる。また、受板２３１または押板２３２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２３１ａ、２３２ａ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。 29 and 30, the receiving plate 231 and the pressing plate 232 are opposed to each other on the rotating shaft 125, and a plurality of sets of the inner plate 235, the torque plate 234, and the outer plate 236 are connected to the receiving plate 231 and the pressing plate 232. , The inner plate 235 is engaged with the rotating shaft 125, the outer plate 236 is engaged with the outer case 230, the torque roller 233 is provided on the torque plate 234, and the torque nut 237 is screwed onto the rotating shaft 125. In a torque limiter that locks the spring seat plate 238 and the spring 239 between the spring seat plate 238 and the pressing plate 232, the pressure receiving surfaces 231a and 232a of the receiving plate 231 or the pressing plate 232 facing the torque plate 234 The pressure receiving surfaces 231a and 232a are formed in a substantially concave shape so that the pressure receiving surfaces 231a and 232a are bent to be flat by a pressing force for generating a set torque. The pressure receiving surfaces 231a, 232a are formed into a tapered sawing structure having the inclination angles A1, A2, and the pressure receiving surfaces 231a, 232a is formed. Then, the receiving plate 231 or the pressing plate 232 is bent by the pressing force when the set torque is generated, the pressure receiving surfaces 231a and 232a become substantially flat, and the smoothed surface pressure is applied to the torque roller 233 surface, The uneven wear can be reduced, the durability can be improved, and the transmission accuracy of the set torque can be improved. Further, even if the thickness of the receiving plate 231 or the pressing plate 232 is not increased so as not to be distorted by the set torque, the pressure of the pressure receiving surfaces 231a and 232a can be smoothed, so that a space-saving and compact unit can be configured. .

また、図２９、図３１に示す如く、受板２３１に段部２３１ｂを設け、該段部２３１ｂをベアリング軸受２２８のインナー部２２８ａに当接させてセットトルクを受圧させると共に、押板２３２に段部２３２ｂを設け、該段部２３２ｂを座金１８１に当接させ、ナット２２３によって固定させる座金１８１と押板２３２の間で押板２３２の円周側に空間Ｂを形成し、ナット２３３の締付力が座金１８１を介して段部２３２ｂから押板２３２に直線的に作用するように構成している。 Further, as shown in FIGS. 29 and 31, a step portion 231b is provided on the receiving plate 231. The step portion 231b is brought into contact with the inner portion 228a of the bearing 228 so as to receive the set torque. A space B is formed on the circumferential side of the push plate 232 between the washer 181 and the push plate 232, which are provided with a step 232 b and the step portion 232 b is brought into contact with the washer 181 and fixed by the nut 223, and the nut 233 is tightened. The force is linearly applied to the push plate 232 from the step portion 232 b via the washer 181.

さらに、図３１に示す如く、図２９のベアリング軸受２２８に代えてボス形の受圧メタル５００を設け、アウタケース２３０を回転軸１２５に前記受圧メタル５００を介して軸支させ、前記受板２３１を受圧メタル５００に一体形成させると共に、ベアリング軸受２２２側の軸受メタル５０１に前記のボス形の受圧メタル５００を当接させるもので、ボス形のメタル５００を用いてアウタケース２３０を回転軸１２５に軸支させ、アウタケース２３０をベアリング２２８によって軸支させる構造に比べ、受板２３１を段付に形成する必要がなく、例えば受板２３１とメタル５００を一体形成することが可能であり、セットトルクの押付け力によって撓むことのない厚みで受板２３１を形成することができ、コンパクトな構造で精度と耐久性を向上させることができる。 Further, as shown in FIG. 31, a boss-shaped pressure receiving metal 500 is provided instead of the bearing 228 of FIG. 29, the outer case 230 is supported by the rotating shaft 125 via the pressure receiving metal 500, and the receiving plate 231 is The boss-shaped pressure-receiving metal 500 is formed integrally with the pressure-receiving metal 500, and the boss-shaped pressure-receiving metal 500 is brought into contact with the bearing metal 501 on the bearing bearing 222 side. It is not necessary to form the receiving plate 231 in a stepped manner as compared with a structure in which the outer case 230 is supported by the bearing 228, and for example, the receiving plate 231 and the metal 500 can be integrally formed. The receiving plate 231 can be formed with a thickness that does not bend due to the pressing force, and the accuracy and durability are reduced by a compact structure. It is possible to above.

また、図３１の如く、プーリボス１８３にビス５０２止め固定させる合成樹脂製の軸カバー５０３を設け、トルクバネ２３９及びトルクナット２３７などを前記軸カバー５０３に内設させ、軸カバー５０３を外した状態でカウンタケース２５外側でトルクナット２３７を操作し、トルクリミッタ１２６のセットトルクを調節する。なお、複数の内板２３５の間の夫々に向けて回転軸１２５の外周の複数個所に油穴２４３を夫々開口させ、油穴２４３からアウタケース２３０のキー溝２４１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２３３の強制潤滑が行われるように構成している。 As shown in FIG. 31, a shaft cover 503 made of a synthetic resin for fixing and fixing the screw 502 to the pulley boss 183 is provided, a torque spring 239 and a torque nut 237 are provided inside the shaft cover 503, and the shaft cover 503 is removed. By operating the torque nut 237 outside the counter case 25, the set torque of the torque limiter 126 is adjusted. Oil holes 243 are respectively opened at a plurality of locations on the outer periphery of the rotating shaft 125 toward each of the plurality of inner plates 235, and oil is centrifuged to the outside from the oil holes 243 via the key grooves 241 of the outer case 230. It is configured to move by force and to perform forced lubrication of the torque roller 233.

コンバインの斜視図。The perspective view of a combine. 同側面図。FIG. 前部機体の側面説明図。FIG. 4 is an explanatory side view of the front body. 同正面説明図。FIG. 駆動部の側面説明図。FIG. 同正面説明図。FIG. 同平面説明図。FIG. 同ミッションケースの駆動系統図。Drive system diagram of the transmission case. 同断面背面図。FIG. 前図の拡大図。The enlarged view of the previous figure. エンジン出力系統図。Engine output system diagram. 油圧回路図。Hydraulic circuit diagram. カウンタケースの駆動系統図。The drive system diagram of a counter case. 同断面平面図。FIG. 同拡大図。FIG. 同外観正面図。FIG. 同平面図。FIG. 同側面図。FIG. 脱穀クラッチ部の平面図。The top view of the threshing clutch part. 同背面図。FIG. 制御回路図。Control circuit diagram. 前図のフローチャート。The flowchart of a previous figure. トルクリミッタ取付説明図。FIG. 同拡大説明図。FIG. 同分解説明図。FIG. 同展開説明図。FIG. 図２５の拡大説明図。FIG. 26 is an enlarged explanatory view of FIG. 25. 刈取プーリの分解説明図。Exploded explanatory view of a cutting pulley. 受板及び押板の説明図。Explanatory drawing of a receiving plate and a pressing plate. 同拡大図。FIG. 受板の他の実施例を示す説明図。Explanatory drawing which shows the other example of a receiving plate.

Explanation of reference numerals

２５カウンタケース（伝動ケース）
９５刈取プーリ（伝動プーリ）
１２４切換シフタ
１２５回転軸
１２６トルクリミッタ
１８３プーリボス
１８４ボルト
２３０アウタケース
２３１受板
２３２押板
２３３トルクローラ
２３４トルク板
２３５内板
２３６外板
２３７トルクナット（トルクセット部材）
２３８バネ座板
２３９トルクバネ（トルクセット部材） 25 Counter case (transmission case)
95 Cutting pulley (transmission pulley)
124 Switching shifter 125 Rotating shaft 126 Torque limiter 183 Pulley boss 184 Bolt 230 Outer case 231 Receiving plate 232 Push plate 233 Torque roller 234 Torque plate 235 Inner plate 236 Outer plate 237 Torque nut (torque setting member)
238 Spring seat plate 239 Torque spring (torque set member)

Claims

A torque limiter comprising: a main body side provided inside a transmission case for oil bath; a torque set member provided outside a transmission pulley boss of a transmission pulley outside the transmission case; and a transmission pulley and a pulley boss formed separately.

The torque limiter according to claim 1, wherein the transmission pulley and the pulley boss are bolted and fixed, and the on / off of the vehicle speed tuning input and the on / off of the constant speed drive input are performed by the same shifter.

The receiving plate and the pressing plate are opposed to each other on the rotating shaft, a plurality of sets of inner plates, torque plates and outer plates are provided between the receiving plate and the pressing plate, the inner plate is engaged with the rotating shaft, and the outer plate is attached to the outer case. The torque plate is provided with a torque roller, and the spring nut is screwed onto the rotating shaft.The spring nut is engaged with the spring seat plate, and a spring is provided between the spring seat plate and the pressing plate. The torque limiter according to claim 1, wherein the pressure receiving surface of the plate is formed to be substantially concave so that the pressure receiving surface is bent by a pressing force that generates a set torque and becomes flat.

The torque limiter according to claim 1, wherein the outer case is supported on the rotation shaft by using a boss-shaped metal.