JP2006094870A - Device for operating combine harvester - Google Patents
Device for operating combine harvester Download PDFInfo
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- JP2006094870A JP2006094870A JP2005374890A JP2005374890A JP2006094870A JP 2006094870 A JP2006094870 A JP 2006094870A JP 2005374890 A JP2005374890 A JP 2005374890A JP 2005374890 A JP2005374890 A JP 2005374890A JP 2006094870 A JP2006094870 A JP 2006094870A
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- 230000005540 biological transmission Effects 0.000 description 46
- 230000007246 mechanism Effects 0.000 description 38
- 230000007935 neutral effect Effects 0.000 description 11
- 235000013339 cereals Nutrition 0.000 description 5
- 230000000452 restraining effect Effects 0.000 description 5
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000003306 harvesting Methods 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 239000010902 straw Substances 0.000 description 1
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Abstract
Description
本発明は、コンバインの操作装置に関する。 The present invention relates to a combine operating device.
従来、扱深さ調節用の扱深さスイッチや刈取昇降用の刈取昇降スイッチなど各種作業スイッチは、通常は主変速レバーや副変速レバーなど各種作業操作レバーの配設される運転席左側位置に設けられていて、左手でもってこれらの操作を行っている(例えば、特許文献1参照)。
ところが、操作頻度も多いためスイッチ操作に操作遅れが生じるなど、作業の対応性に欠ける不都合があった。 However, since the operation frequency is high, there is an inconvenience of lack of work compatibility such as an operation delay in the switch operation.
ここで、本発明では、運転席の左側のサイドコラムに主変速レバーを配設すると共に、運転席の前方の運転操作部に丸形の操向ハンドルを配設し、同操向ハンドルの丸形外周の右内側にスイッチ台を設け、同スイッチ台に、指先で操作可能なスイッチであって、条合わせのための進路方向の微調整を行う微調整用操向手段としてのスイッチを設けたことを特徴とするコンバインの操作装置を提供するものである。 Here, in the present invention, the main shift lever is disposed on the left side column of the driver's seat, and the round steering handle is disposed in the driving operation portion in front of the driver's seat, A switch base is provided on the right inner side of the outer periphery of the shape, and a switch that can be operated with a fingertip is provided on the switch base as a fine adjustment steering means for fine adjustment of the course direction for alignment. The present invention provides a combine operating device.
本発明によれば、例えば、右手で操向ハンドルを操作しながら操向ハンドルの丸形外周の右内側に設けたスイッチ台のスイッチを操作して条合わせのための進路方向の微調整を容易に行うことができるので、同スイッチにより容易に条合わせを行うことができ、作業性を向上させることができる。 According to the present invention, for example, while the steering handle is operated with the right hand, the switch of the switch base provided on the right inner side of the round outer periphery of the steering handle is operated to facilitate fine adjustment of the course direction for alignment. Therefore, alignment can be easily performed by the switch, and workability can be improved.
特に、レバーの設置数も多く操作頻度の多い左手側に対し、ハンドル操作のみの右手側に微調整用操向手段としてのスイッチを設けると共に、同スイッチを操向ハンドルの丸形外周の右内側に設けたスイッチ台に設けているため、頻繁に操作が行われるこの微調整用操向手段としてのスイッチの操作遅れなどのない迅速にして正確な操作を行うことができる。 In particular, on the left hand side where the number of levers is often set and the operation frequency is high, a switch as a steering means for fine adjustment is provided on the right hand side where only the handle is operated, and the switch is connected to the right inside of the round outer periphery of the steering handle Therefore, it is possible to perform a quick and accurate operation without a delay in the operation of the switch as the fine adjustment steering means that is frequently operated.
以下、本発明の実施例を図面に基づいて詳述する。図1は揺動選別部の側面説明図、図2はコンバインの全体側面図、図3は同平面図であり、図中(1)は走行クローラ(2)を装設するトラックフレーム、(3)は前記トラックフレーム(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(7)を内蔵している脱穀機である脱穀部、(8)は刈刃(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(8)を昇降させる油圧シリンダ、(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(16)を介して搬入する穀物タンク、(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)は運転操作部(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. FIG. 1 is an explanatory side view of the swing sorting portion, FIG. 2 is an overall side view of the combine, FIG. 3 is a plan view thereof, in which (1) is a track frame on which a traveling crawler (2) is installed; ) Is a machine base installed on the track frame (1), and (4) is a threshing machine that has a feed chain (5) stretched to the left and incorporates a handling cylinder (6) and a processing cylinder (7). (8) is a cutting part provided with a cutting blade (9) and a grain conveying mechanism (10), (11) is a hydraulic cylinder for raising and lowering the cutting part (8) via a cutting frame (12), (13 ) Is a waste processing section that faces the end of the waste chain (14), (15) is a grain tank that carries the grain from the threshing section (4) through the milling cylinder (16), A discharge auger for unloading the grain of the tank (15), (18) is a driving operation part (19) and a driver seat (20 Driving cabin comprising, it is configured to threshing harvests (21) the driver cabin (18) an engine provided below, continuously culms.
図4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対の第1油圧ポンプ(23)及び第1油圧モータ(24)からなる主変速機構である走行用の油圧式無段変速機構(25)と、1対の第2油圧ポンプ(26)及び第2油圧モータ(27)からなる操向機構である旋回用の油圧式無段変速機構(28)とを備え、前記エンジン(21)の出力軸(21a)に第1油圧ポンプ(23)の入力軸(23a)を伝達ベルト(29)を介し連動連結させると共に、第2油圧ポンプ(26)の入力軸(26a)を伝達ベルト(30)を介し前記第1油圧ポンプ(23)の入力軸(23a)に連動連結させている。 As shown in FIG. 4, the transmission case (22) for driving the travel crawler (2) is a main transmission mechanism comprising a pair of first hydraulic pump (23) and first hydraulic motor (24). A hydraulic continuously variable transmission mechanism (25) and a turning hydraulic continuously variable transmission mechanism (28) which is a steering mechanism including a pair of second hydraulic pump (26) and a second hydraulic motor (27). An input shaft (23a) of the first hydraulic pump (23) is linked to the output shaft (21a) of the engine (21) via a transmission belt (29), and the input shaft of the second hydraulic pump (26) (26a) is linked to the input shaft (23a) of the first hydraulic pump (23) via a transmission belt (30).
そして、前記第1油圧モータ(24)の出力軸(31)に、副変速機構(32)及び差動機構(33)を介し走行クローラ(2)の駆動輪(34)を連動連結させるもので、前記差動機構(33)は左右対称の1対の遊星ギヤ機構(35)(35)を有し、各遊星ギヤ機構(35)は1つのサンギヤ(36)と、該サンギヤ(36)の外周で噛合う3つのプラネタリギヤ(37)と、これらプラネタリギヤ(37)に噛合うリングギヤ(38)などで形成している。 The drive wheel (34) of the traveling crawler (2) is interlockedly connected to the output shaft (31) of the first hydraulic motor (24) via the subtransmission mechanism (32) and the differential mechanism (33). The differential mechanism (33) has a pair of symmetrical planetary gear mechanisms (35) and (35), each planetary gear mechanism (35) includes one sun gear (36) and the sun gear (36). It is formed by three planetary gears (37) meshing with the outer periphery and a ring gear (38) meshing with these planetary gears (37).
前記プラネタリギヤ(37)は、サンギヤ軸(39)と同軸線上とのキャリヤ軸(40)のキャリヤ(41)にそれぞれ回転自在に軸支させ、左右のサンギヤ(36)(36)を挾んで左右のキャリヤ(41)を対向配置させると共に、前記リングギヤ(38)は各プラネタリギヤ(37)に噛み合う内歯を有してサンギヤ軸(39)とは同一軸芯状に配置させ、サンギヤ軸(39)或いはキャリヤ軸(40)に回転自在に軸支させている。 The planetary gear (37) is rotatably supported by the carrier (41) of the carrier shaft (40) coaxial with the sun gear shaft (39), and the left and right sun gears (36) (36) are sandwiched between the left and right sun gears (36) (36). The ring gear (38) has inner teeth that mesh with the planetary gears (37) and is arranged on the same axis as the sun gear shaft (39). The carrier shaft (40) is rotatably supported.
また、走行用の油圧式無段変速機構(25)は第1油圧ポンプ(23)の回転斜板の角度変更調節により第1油圧モータ(24)の正逆回転と回転数の制御を行うもので、第1油圧モータ(24)の回転出力を出力軸(31)の伝達ギヤ(42)より副変速機構(32)を構成する各ギヤ(43)(44)(45)を介して、サンギヤ軸(39)に固定したセンタギヤ(46)に伝達してサンギヤ(41)を回転するように構成している。なお前記ギヤ(45)はブレーキ機構を有するブレーキ軸(47)に取付けられると共に、前記ギヤ(43)には作業機等に回転力を伝達するPTO軸(48)のPTO入力ギヤ(49)を噛合せている。 The traveling hydraulic continuously variable transmission mechanism (25) performs forward / reverse rotation and rotation speed control of the first hydraulic motor (24) by adjusting and changing the angle of the rotary swash plate of the first hydraulic pump (23). Thus, the rotational output of the first hydraulic motor (24) is transmitted from the transmission gear (42) of the output shaft (31) via the gears (43) (44) (45) constituting the auxiliary transmission mechanism (32) to the sun gear. The sun gear (41) is rotated by being transmitted to the center gear (46) fixed to the shaft (39). The gear (45) is attached to a brake shaft (47) having a brake mechanism, and a PTO input gear (49) of a PTO shaft (48) for transmitting rotational force to a work machine or the like is attached to the gear (43). Meshing.
そして、前記センタギヤ(46)を介しサンギヤ軸(39)に伝達された第1油圧モータ(24)からの駆動力を、左右の遊星ギヤ機構(35)を介しキャリヤ軸(40)に伝達させると共に、該キャリヤ軸(40)に伝達された回転を左右各一対の減速ギヤ(50)(51)を介し左右の駆動輪(34)の左右輪軸(34a)にそれぞれ伝えるように構成している。 The driving force from the first hydraulic motor (24) transmitted to the sun gear shaft (39) via the center gear (46) is transmitted to the carrier shaft (40) via the left and right planetary gear mechanisms (35). The rotation transmitted to the carrier shaft (40) is transmitted to the left and right wheel shafts (34a) of the left and right drive wheels (34) via a pair of left and right reduction gears (50) and (51), respectively.
さらに、旋回用の油圧式無段変速機構(28)は第2油圧ポンプ(26)の回転斜板の角度変更調節により第2油圧モータ(27)の正逆回転と回転数の制御を行うもので、第2油圧モータ(27)から出力軸(52)の伝達ギヤ(52a)(52b)に伝達される回転出力を、左側のリングギヤ(38)の外歯を対しては直接的に、また右側のリングギヤ(38)の外歯に対しては逆転軸(53)の逆転ギヤ(53a)を介し伝えて、第2油圧モータ(27)の正転時に左右のリングギヤ(38)を左右同一回転数で左ギヤ(38)を逆転、右ギヤ(38)を正転とさせるように構成している。 Further, the turning hydraulic continuously variable transmission mechanism (28) controls the forward and reverse rotation of the second hydraulic motor (27) and the rotational speed by adjusting the angle change of the rotary swash plate of the second hydraulic pump (26). Thus, the rotational output transmitted from the second hydraulic motor (27) to the transmission gears (52a) and (52b) of the output shaft (52) can be directly applied to the outer teeth of the left ring gear (38) and The external gear of the right ring gear (38) is transmitted via the reverse gear (53a) of the reverse shaft (53), and the left and right ring gears (38) rotate in the same direction when the second hydraulic motor (27) rotates forward. The left gear (38) is reversely rotated by the number, and the right gear (38) is normally rotated.
而して、旋回用の第2油圧ポンプ(26)の駆動を停止させ左右リングギヤ(38)を静止固定させた状態で、走行用の第1油圧ポンプ(23)の駆動を行うと、第1油圧モータ(24)からの回転出力はセンタギヤ(47)から左右のサンギヤ(36)に同一回転数で伝達され、左右遊星ギヤ機構(35)のプラネタリギヤ(37)・キャリヤ(41)及び減速ギヤ(50)(51)を介し左右の輪軸(34a)に左右同回転方向の同一回転数で伝達されて、機体の前後直進走行が行われる。一方、走行用の第1油圧ポンプ(23)の駆動を停止させ左右のサンギヤ(36)を静止固定させた状態で、旋回用の第2油圧ポンプ(26)を正逆回転駆動すると、左側の遊星ギヤ機構(35)が逆或いは正回転、また右側の遊星ギヤ機構が正或いは逆回転して、左右走行クローラ(2)の駆動方向を前後逆方向とさせて機体を左或いは右にその場でスピンターンさせるものである。 Thus, when the driving of the first hydraulic pump (23) for driving is performed in a state where the driving of the second hydraulic pump (26) for turning is stopped and the left and right ring gears (38) are stationary and fixed, The rotational output from the hydraulic motor (24) is transmitted from the center gear (47) to the left and right sun gears (36) at the same rotational speed, and the planetary gear (37), carrier (41) and reduction gear ( 50), the left and right wheel shafts (34a) are transmitted to the left and right wheel shafts (34a) at the same rotational speed in the same direction of left and right, and the vehicle body travels straight forward and backward. On the other hand, when the second hydraulic pump (26) for rotation is driven to rotate in the forward and reverse directions with the driving of the first hydraulic pump (23) for traveling stopped and the left and right sun gears (36) stationary and fixed, The planetary gear mechanism (35) rotates in the reverse or forward direction, and the right planetary gear mechanism rotates in the forward or reverse direction so that the driving direction of the left and right traveling crawler (2) is reversed in the front-rear direction. This is what makes you spin-turn.
また、走行用の第1油圧ポンプ(23)を駆動させながら、旋回用の第2油圧ポンプ(26)を駆動して機体を左右に旋回させる場合には旋回半径の大きい旋回を可能にできるもので、その旋回半径は左右走行クローラ(2)の速度に応じ決定される。 In addition, when the first hydraulic pump (23) for driving is driven and the second hydraulic pump (26) for turning is driven to turn the body left and right, turning with a large turning radius can be enabled. Thus, the turning radius is determined according to the speed of the left and right traveling crawler (2).
図5乃至図8に示す如く、走行用の油圧式無段変速機構(25)に連結する主変速レバー(54)と、主クラッチペダル(55)とを主変速中立復帰機構(56)を介し連動連結させるもので、前記主変速レバー(54)は基端ボス(57)に変速操作板(58)を固設させ、該操作板(58)をレバー軸(59)を中心に回動自在に設けると共に、該操作板(58)に固定する2本の前進及び後進用ワイヤ(60)(61)を出力変換手段である変速及び旋回操作機構(62)を介して前記無段変速機構(25)に連動連結させている。 As shown in FIGS. 5 to 8, a main transmission lever (54) connected to a traveling hydraulic continuously variable transmission mechanism (25) and a main clutch pedal (55) are connected via a main transmission neutral return mechanism (56). The main transmission lever (54) has a transmission operation plate (58) fixed to a base end boss (57), and the operation plate (58) is rotatable about a lever shaft (59). And the two forward and reverse wires (60) and (61) fixed to the operation plate (58) are connected to the continuously variable transmission mechanism (62) via the shift and turning operation mechanism (62) as output conversion means. 25).
そして、前記操作板(58)にL形状の規制ピン(63)を固設させ、該規制ピン(63)の先端部を前記中立復帰機構(56)を構成する二枚一組の上下拘束板(64a)(64b)によって拘束するもので、上下拘束板(64a)(64b)は基端を枢支軸(65)に回動自在に支持して、上下拘束板(64a)(64b)の対向内側面間に一定の開ぎ角(α)を有するとき、主変速レバー(54)の前進高速操作時から後進高速操作時におけるピン(63)の上下移動を許容するように構成している。 Then, an L-shaped restricting pin (63) is fixed to the operation plate (58), and a pair of upper and lower restricting plates constituting the neutral return mechanism (56) is formed at the tip of the restricting pin (63). The upper and lower restraint plates (64a) and (64b) are supported by the pivot shaft (65) so as to be rotatable, and the upper and lower restraint plates (64a) and (64b) When there is a constant opening angle (α) between the opposed inner side surfaces, the pin (63) is allowed to move up and down during the forward high-speed operation from the high-speed forward operation of the main transmission lever (54). .
また、上下拘束板(64a)(64b)の対向内側面には半円状の中立位置決め用切欠き(66)と前記ピン(63)に係合する切欠き長溝(67)を形成し、上下拘束板(64a)(64b)の開き角(α)を略0°に閉動作させるとき、前記ピン(63)を中央位置に戻して主変速レバー(54)を中立復帰させるように構成している。 Further, a semicircular neutral positioning notch (66) and a notch long groove (67) engaged with the pin (63) are formed on the opposing inner side surfaces of the upper and lower restraining plates (64a) (64b). When the opening angle (α) of the restraint plates (64a) and (64b) is closed to approximately 0 °, the pin (63) is returned to the center position, and the main transmission lever (54) is returned to the neutral position. Yes.
さらに、前記主クラッチペダル(55)を駐車ブレーキ機構(68)にワイヤ代(68a)を介し連動連結させ、該主クラッチペダル(55)のクラッチアーム(69)と前記上拘束板(64a)間を中立復帰ワイヤ(70)で連結させるもので、上拘束板(64a)にワイヤ(70)の一端側を連結させ、ワイヤ(70)の他端側をバネ(71)を介してクラッチアーム(69)に連結させると共に、前記ワイヤ(70)のアウタチューブ(70a)一端のアウタ受け(72)を下拘束板(64b)に、またアウタチューブ(70a)他端のアウタ受け(73)を、ペダル(55)のペダル受け台(74)に取付けて、ペダル(55)の踏み込み操作時(主クラッチの切時)に上下拘束板(64a)(64b)の開き角(α)を略0°とするように構成している。 Further, the main clutch pedal (55) is linked to the parking brake mechanism (68) via a wire allowance (68a), and the clutch arm (69) of the main clutch pedal (55) and the upper restraining plate (64a) are connected. Are connected by a neutral return wire (70), one end side of the wire (70) is connected to the upper restraining plate (64a), and the other end side of the wire (70) is connected to the clutch arm (71) via a spring (71). 69), the outer receiver (72) at one end of the outer tube (70a) of the wire (70) is connected to the lower restraint plate (64b), and the outer receiver (73) at the other end of the outer tube (70a) is connected. Attached to the pedal pedestal (74) of the pedal (55), when the pedal (55) is depressed (when the main clutch is disengaged), the opening angle (α) of the upper and lower restraint plates (64a) (64b) is approximately 0 °. To It is configured as follows.
なお、このような上下拘束板(64a)(64b)の閉じ動作時にあっては、本機側フレームに連結する中立位置決めピン(75)と、前記切欠き(66)との係合によって、上下拘束板(64a)(64b)の間で閉じ動作や閉じ量に差があっても確実に中立位置に戻すことを可能とさせるものである。また(76)は自動走行制御用の変速モータである。 During the closing operation of the upper and lower restraining plates (64a) and (64b), the neutral positioning pin (75) connected to the machine side frame and the notch (66) are engaged to move the upper and lower restraint plates (64a) and (64b). Even if there is a difference in the closing operation or the closing amount between the restraining plates (64a) and (64b), it is possible to reliably return to the neutral position. Reference numeral (76) denotes a transmission motor for automatic travel control.
図9乃至図13にも示す如く、単一のコンポーネントに形成する前記操作機構(62)には前記主変速レバー(54)と機体の旋回操作を行う丸形操向ハンドル(77)からの操作出力が入力され、それぞれ必要な動きに変換され、2つのポンプ(23)(26)・2つのモータ(24)(27)で構成する強制デフ式ミッションケース(22)に出力させて走行と旋回の制御を行うようにしたもので、主変速レバー(54)及び操向ハンドル(77)と、走行及び旋回用無段変速機構(25)(28)のコントロールレバー(78)(79)との間に前記操作機構(62)を介設したものである。 As shown in FIGS. 9 to 13, the operation mechanism (62) formed as a single component is operated from the main steering lever (54) and a round steering handle (77) for turning the fuselage. The output is input, converted into the necessary movements, and output to the forced differential transmission case (22) composed of two pumps (23) (26) and two motors (24) (27). The main transmission lever (54) and the steering handle (77) and the control levers (78) and (79) of the continuously variable transmission mechanisms (25) and (28) for turning and turning are provided. The operation mechanism (62) is interposed therebetween.
前記操作機構(62)は、本機側のフレーム(80)の上部に固設するコンポーネントケース(81)と、該ケース(81)に左右両端の支軸(82)を回動自在に支持させる門形のベース部材であるベース(83)と、ケース(81)外側の支軸(82)に固設して主変速レバー(54)からの前記ワイヤ(60)(61)を上下に連結させる主変速入力アーム(84)と、前記ベース(83)の左右両側に固設する縦カム軸(85)(86)にそれぞれ回動自在に支持させるカム部材である主変速及び旋回カム(87)(88)と、前記ベース(83)の略中央に固設する入力アーム軸(89)に回動自在に支持させるステアリング操作入力アーム(90)と、該入力アーム(90)に固設して前記ハンドル(77)のステアリングアーム(91)からの左右旋回ワイヤ(92)を連結させる入力アームピン(93)と、前記入力アーム(90)に固設して主変速及び旋回カム(87)(88)の固定ギヤ(94)(95)に噛合せる旋回ギヤ(96a)(96b)と、前記フレーム(80)の下部に回動自在に枢支する横軸(97)に基端ボス(98a)を揺動自在に支持させる主変速用従動カム(98)と、前記横軸(97)に基端ボス(99a)を一体連結させる旋回用従動カム(99)と、前記主変速及び旋回カム(87)(88)と従動カム(98)(99)とにそれぞれ上下両端を自在継手(100)を介し連結させる変速及び旋回カムロッド(101)(102)と、前記ミッションケース(22)上部の軸受台(103)に固設する筒軸(104)に回動自在に支持させる操作伝達軸(105)と、前記ボス(98a)に右端を固設する揺動アーム(106)と伝達軸(105)に基端ボス(107a)を固設する揺動アーム(107)の各先端間を自在継手(100)を介し連結させる変速第1ロッド(108)と、前記横軸(97)に基端を固設する揺動アーム(109)と前記伝達軸(105)に基端ボス(110a)を回動自在に取付ける揺動アーム(110)の各先端間を自在継手(100)を介し連結させる旋回第1ロッド(111)と、前記伝達軸(105)に基端を固設する揺動アーム(112)と前記コントロールレバー(78)の各先端間を自在継手(100)を介し連結させる変速第2ロッド(113)と、前記ボス(110a)に基端を固設する揺動アーム(114)と前記コントロールレバー(79)の各先端間を自在継手(100)を介し連結させる旋回第2ロッド(115)とを備え、前記主変速レバー(54)及び操向ハンド(77)の各操作力を操作機構(62)でそれぞれ必要な動きに変換して各コントロールレバー(78)(79)に伝えるように構成している。 The operating mechanism (62) includes a component case (81) fixed to the upper part of the frame (80) on the machine side, and the case (81) rotatably supporting the left and right support shafts (82). A base (83), which is a gate-shaped base member, and a support shaft (82) outside the case (81) are fixed to connect the wires (60) (61) from the main transmission lever (54) up and down. A main shift and swing cam (87) which is a cam member rotatably supported by a main shift input arm (84) and vertical cam shafts (85) and (86) fixed to the left and right sides of the base (83). (88), a steering operation input arm (90) that is rotatably supported by an input arm shaft (89) fixed at substantially the center of the base (83), and fixed to the input arm (90). Steering arm of the handle (77) An input arm pin (93) for connecting the left and right swirl wires (92) from (91), and a fixed gear (94) for main shift and swiveling cams (87) (88) fixed to the input arm (90) ( 95) The swivel gears (96a) (96b) meshed with the main body boss (98a) and the horizontal shaft (97) pivotably supported at the lower part of the frame (80) are supported in a swingable manner. A shift driven cam (98), a swivel driven cam (99) in which a base boss (99a) is integrally connected to the horizontal shaft (97), the main shift and swivel cams (87) (88), and a driven cam (98) and (99) are fixedly mounted on a shift and swivel cam rod (101) (102) and upper bearing case (103) on the upper side of the transmission case (22). Can be rotated to the cylinder axis (104) An operation transmission shaft (105) to be supported, a swing arm (106) having a right end fixed to the boss (98a), and a swing arm (107) having a proximal end boss (107a) fixed to the transmission shaft (105). A variable speed first rod (108) for connecting the distal ends of each of the first and second ends via a universal joint (100), a swing arm (109) having a base end fixed to the horizontal shaft (97), and a transmission shaft (105). A pivoting first rod (111) for connecting the distal ends of a swing arm (110) to which a proximal boss (110a) is rotatably attached via a universal joint (100), and a proximal end to the transmission shaft (105) The rocking arm (112) for fixing the shaft and the distal end of the control lever (78) are connected to each other through the universal joint (100), and the base end is fixed to the boss (110a). The swing arm (114) to be installed and the A turning second rod (115) for connecting the tip ends of the control lever (79) via a universal joint (100), and operating each operating force of the main transmission lever (54) and the steering hand (77). The mechanism (62) is configured to convert the movement into necessary movements and transmit it to the control levers (78) and (79).
前記主変速レバー(54)の操作に応じて支軸(82)を中心として傾斜角を変化させるベース(83)は、主変速の中立位置のとき一定角度前低後高状に傾斜(a)させ、該ベース(83)に直交させる縦カム軸(85)(86)の軸芯(b)下方延長線上に各従動カム(98)(99)とカムロッド(101)(102)との自在継手(100)の中心を配置させると共に、前記主変速アーム(87)のカムロッド(101)を連結するロッド操作アーム(87a)を、支軸(82)の軸芯(c)に直交させて前方に突設させるのに対し、旋回カム(88)のカムロッド(102)に連結するロッド操作アーム(88a)を、支軸(82)の軸芯(c)方向に突設させて該アーム(88a)とロッド(102)との自在継手(100)の中心を支軸(82)の軸芯(c)に一致させ、主変速の中立位置でハンドル(77)操作により各カム軸(85)(86)を中心としてカム(87)(88)を回動させるとき、これらカム(87)(88)と従動カム(98)(99)間の距離を一定状態に保って、コントロールレバー(78)(79)の中立を保持させる。 The base (83) that changes the inclination angle around the support shaft (82) in accordance with the operation of the main transmission lever (54) is inclined at a certain angle before, after and at a predetermined angle when the main transmission is in the neutral position (a). Universal joints of the driven cams (98) (99) and the cam rods (101) (102) on the axis (b) downward extension line of the vertical cam shafts (85) (86) perpendicular to the base (83) (100) is disposed at the center, and the rod operating arm (87a) for connecting the cam rod (101) of the main transmission arm (87) is moved forward at right angles to the axis (c) of the support shaft (82). On the other hand, the rod operating arm (88a) connected to the cam rod (102) of the swiveling cam (88) is projected in the direction of the axis (c) of the support shaft (82). And universal joint (100) of rod (102) Align the center with the axis (c) of the support shaft (82), and rotate the cams (87) and (88) around the cam shafts (85) and (86) by operating the handle (77) at the neutral position of the main transmission. When moving, the distance between the cams (87) (88) and the driven cams (98) (99) is kept constant, and the neutrality of the control levers (78) (79) is maintained.
一方、主変速レバー(54)の操作によって支軸(82)を中心としてベース(83)を上下方向に回動させるとき、旋回カム(88)とカムロッド(102)との自在継手(100)中心と支軸(82)の軸芯とが一致するため旋回用従動カム(79)は動作せず、主変速カム(87)の傾きの変化によって主変速カム(87)が動作して主変速コントロールレバー(78)のみが操作されて前進及び後進・低速及び高速の変速が行われる。 On the other hand, when the base (83) is turned up and down around the support shaft (82) by the operation of the main speed change lever (54), the center of the universal joint (100) of the turning cam (88) and the cam rod (102) And the shaft of the support shaft (82) coincide with each other, so that the swivel driven cam (79) does not operate, and the main transmission cam (87) operates by the change in the inclination of the main transmission cam (87), and the main transmission control Only the lever (78) is operated to shift forward, reverse, low speed and high speed.
また、斯る主変速の操作条件下でハンドル(77)により旋回操作が行われるときには、旋回カム(88)の回動による旋回カム(88)とカムロッド(102)との自在継手(100)中心と、支軸(82)の軸芯の位置ズレでもって従動カム(99)が動作し、旋回用コントロールレバー(79)が操作されて機体の左及び右旋回が行われるもので、またこの際ギヤ(94)(96a)の噛合せによる主変速カム(87)の回動によって走行速度が低速側(ハンドル(77)の直進位置のとき主変速にあってはそのレバー(54)操作位置での常に最高速位置にあって、ハンドル(77)の操舵角を大とする程主変速カム(87)は低速側に制御される)に減速されて安全旋回が行われる。さらに、この場合機体の前後進時の旋回方向も一致させることができて、従来の如く切換機構なども要することなく至便なものである。 Further, when the turning operation is performed by the handle (77) under the operation condition of the main speed change, the center of the universal joint (100) between the turning cam (88) and the cam rod (102) by the turning of the turning cam (88). Then, the driven cam (99) is operated by the misalignment of the axis of the support shaft (82), and the turning control lever (79) is operated to turn the aircraft left and right. When the main speed change cam (87) is rotated by the engagement of the gears (94) and (96a), the travel speed is low (when the main speed is the straight position of the handle (77), the lever (54) is operated. The main speed change cam (87) is controlled to the lower speed side as the steering angle of the handle (77) is increased, and a safe turning is performed. Further, in this case, the direction of turning when the aircraft is moving forward and backward can be made coincident, which is convenient without requiring a switching mechanism or the like as in the prior art.
ところで、図13乃至図14に示す如く、前記運転キャビン(18)内の運転席(20)左側のサイドコラムには、前記主変速レバー(54)・副変速レバー(116)・刈取クラッチレバー(117)・脱穀クラッチレバー(118)を配設すると共に、運転席(20)前方の運転操作部(19)に前記操向ハンドル(77)を配設している。 By the way, as shown in FIG. 13 to FIG. 14, the side column on the left side of the driver's seat (20) in the driving cabin (18) has the main transmission lever (54), the auxiliary transmission lever (116), the cutting clutch lever ( 117) The threshing clutch lever (118) is disposed, and the steering handle (77) is disposed in the driving operation portion (19) in front of the driver seat (20).
前記操向ハンドル(77)の丸形外周の右内側にスイッチ台(119)を固設して、脱穀部に挿入する穀稈の扱深さを調節する扱深さ調節機構の扱深さ調節スイッチ(120)を前記スイッチ台(119)に設けて、右手で操向ハンドル(77)を回動操作しながら扱深さ調節も同時に可能とさせるように構成している。而して該構成の場合レバー(54)(116)(117)(118)の設置数も多く操作頻度の多い左手側に対し、ハンドル(77)操作のみの右手側に扱深さ調節スイッチ(120)を設けて、その操作性を向上させることができるものである。 The switch base (119) is fixed to the right inner side of the round outer periphery of the steering handle (77), and the handle depth adjustment of the handle depth adjusting mechanism that adjusts the handle depth of the cereal to be inserted into the threshing portion is adjusted. A switch (120) is provided on the switch base (119) so that the steering depth can be adjusted simultaneously while the steering handle (77) is rotated with the right hand. Thus, in the case of this configuration, the levers (54), (116), (117), and (118) are installed in large numbers, and the handle depth adjustment switch ( 120) can be provided to improve the operability.
また、図15乃至図16は、操向ハンドル(77)に刈取部(8)を昇降操作する刈取昇降スイッチ(121)を設ける構成例を示すもので、前述の扱深さ調節スイッチ(120)に換え、ハンドル(77)のスイッチ台(119)に刈取昇降スイッチ(121)を設けて、頻繁に操作が行われるこの刈取昇降スイッチ(121)の操作遅れなどのない迅速にして正確な昇降操作を可能とさせるように構成したものである。 15 to 16 show a configuration example in which the steering handle (77) is provided with a cutting lift switch (121) for raising and lowering the cutting part (8), and the above-described handling depth adjustment switch (120) is shown. Instead, a cutting / lifting switch (121) is provided on the switch base (119) of the handle (77), and the lifting / lowering switch (121), which is frequently operated, is operated quickly and accurately without any delay in operation. Is configured to be possible.
さらに、図17は、指先だけで進路方向の微調整を行うフィットステアリングスイッチ(122)を操向ハンドル(77)右側のスイッチ台(119)に設ける構成例を示すもので、右手をその都度持ち換える必要もなく、ハンドル(77)の操作を行いながら条合わせなどにおいて方向の微調整を容易に可能とさせて、この作業性を向上させるように構成したものである。 Further, FIG. 17 shows a configuration example in which a fitting steering switch (122) for performing fine adjustment in the course direction only with the fingertip is provided on the switch base (119) on the right side of the steering handle (77), and the right hand is held each time. There is no need to change the direction of the handle (77), and it is possible to easily finely adjust the direction in the alignment or the like, thereby improving the workability.
またさらに、図18及び図19は、刈取部(8)を高速で一定回転駆動する刈取一定回転機構(123)を備え、該回転機構(123)を操作する押ボタン式の高速一定回転スイッチ(124)をハンドル(77)右側のスイッチ台(119)に設ける構成例を示すもので、前記スイッチ(124)は押している間だけオンとなって刈取部(8)を高速で一定回転させ、例えば倒伏稈場所ではスイッチ(124)をオンして刈取部(8)を高速回転させ、倒伏稈場所を過ぎるとスイッチ(124)から指を離して通常の刈取回転に戻して刈取作業の作業性を向上させるように構成したものである。またこの場合刈り終り時に稈を脱穀部に流し込む作業も、スイッチ(124)のワンタッチ操作で容易に可能となる。 18 and 19 are each provided with a constant cutting rotation mechanism (123) that drives the cutting part (8) at a constant speed at a high speed, and a push button type high-speed constant rotation switch (123) that operates the rotation mechanism (123). 124) is provided on the switch base (119) on the right side of the handle (77). The switch (124) is turned on only while it is pressed, and the cutting part (8) is rotated at a constant speed at a high speed. Turn the switch (124) on and turn the cutting part (8) at high speed at the lodging position, and release the switch (124) to return to the normal cutting rotation after passing the lying position to improve the workability of the cutting work. It is configured to improve. Also, in this case, the work of pouring the straw into the threshing portion at the end of cutting can be easily performed by a one-touch operation of the switch (124).
前記刈取一定回転機構(123)は、カウンタケース(125)の刈取出力軸(126)に備えるもので、前記高速一定回転スイッチ(124)によってオンにする刈取高速クラッチ(127)と、刈取低速クラッチ(128)を設け、刈取出力軸(126)に一方向クラッチ(129)及び伝達ベルト(130)を介して刈取入力1軸(131)を連動連結させると共に、ミッションケース(22)の車速同調出力軸(132)に一方向クラッチ(133)及び伝達ベルト(134)及び刈取テンションクラッチ(135)を介して刈取入力1軸(131)を連動連結させ、刈取テンションクラッチ(135)切のとき、刈取出力軸(125)の低高速出力により1軸(131)を駆動すると共に、テンションクラッチ(135)入によって、低速走行状態で車速同調出力軸(132)回転数が刈取出力軸(126)回転数よりも低いとき、刈取出力軸(126)によって1軸(131)を駆動する一方、高速走行状態で車速同調出力軸(132)回転数が刈取出力軸(126)回転数よりも高いとき、車速同調出力軸(132)によって1軸(131)を駆動し、走行速度に比例した速度で刈取部(8)を駆動するように構成している。 The mowing constant rotation mechanism (123) is provided on the mowing output shaft (126) of the counter case (125). The mowing high speed clutch (127) is turned on by the high speed constant rotation switch (124), and the mowing low speed clutch. (128) is provided, and the cutting output shaft (126) is coupled to the cutting input shaft (131) via the one-way clutch (129) and the transmission belt (130), and the vehicle speed tuning output of the transmission case (22) is provided. When the cutting tension clutch (135) is cut off, the cutting input clutch (135) is cut off by linking the shaft (132) to the cutting input clutch (135) via the one-way clutch (133), the transmission belt (134) and the cutting tension clutch (135). One shaft (131) is driven by the low-speed output of the output shaft (125) and the tension clutch (135) is engaged. When the rotational speed of the vehicle speed tuning output shaft (132) is lower than the rotational speed of the cutting output shaft (126) in the low speed traveling state, the one shaft (131) is driven by the cutting output shaft (126), while the vehicle speed in the high speed traveling state is When the rotation speed of the tuning output shaft (132) is higher than the rotation speed of the cutting output shaft (126), one shaft (131) is driven by the vehicle speed tuning output shaft (132), and the cutting portion (8) is driven at a speed proportional to the traveling speed. ) Is driven.
なお、前述実施例にあっては、各作業スイッチ(120)(121)(122)(124)をハンドル(77)に直接的に取付ける構成を示したが、ハンドル(77)にハンドル操作用ノブを設置して、該ノブにこれらスイッチ(120)(121)(122)(123)を設けても良い。 In the above-described embodiment, the configuration is shown in which each work switch (120) (121) (122) (124) is directly attached to the handle (77). These switches (120) (121) (122) (123) may be provided on the knob.
(77) 操向ハンドル
(120)(121)(122)(124) スイッチ
(77) Steering handle (120) (121) (122) (124) Switch
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