JP3930505B2 - Mobile farm machine - Google Patents

Mobile farm machine Download PDF

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JP3930505B2
JP3930505B2 JP2004280490A JP2004280490A JP3930505B2 JP 3930505 B2 JP3930505 B2 JP 3930505B2 JP 2004280490 A JP2004280490 A JP 2004280490A JP 2004280490 A JP2004280490 A JP 2004280490A JP 3930505 B2 JP3930505 B2 JP 3930505B2
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steering
arm
pivot
speed change
shaft
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JP2005027676A (en
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茂實 日高
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Yanma Agricultural Equipment Co Ltd
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Yanma Agricultural Equipment Co Ltd
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Description

本発明は、コンバインなどの移動農機に関する。   The present invention relates to a mobile agricultural machine such as a combine.

従来、移動農機の一形態として、変速レバーでもって油圧走行機構を、また、操向ハンドルでもって油圧操向機構をそれぞれ別個に操作して機体の走行の変速や、機体の旋回を行うようにしたものがある(例えば、特許文献1参照)。
特公昭59−12505号公報
Conventionally, as a form of mobile farming machine, the hydraulic travel mechanism is operated with a shift lever, and the hydraulic steering mechanism is operated separately with a steering handle so as to shift the traveling of the aircraft and turn the aircraft. (For example, refer to Patent Document 1).
Japanese Examined Patent Publication No.59-12505

しかしなら、上記した移動農機の場合、常に2つの操作を必要にして作業が煩わしいものであった。   However, in the case of the mobile farm machine described above, two operations are always required and the work is troublesome.

そこで、本発明では、走行クローラ(2)と、当該走行クローラ(2)を駆動するミッションケース(22)とを備え、当該ミッションケース(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)とを備える移動農機であって、
前記走行用の油圧式無段変速機構(25)の操作に用いられる主変速レバー(68)と、
前記旋回用の油圧式無段変速機構(28)の操作に用いられる操向ハンドル(19)と、
前記主変速レバー(68)と前記操向ハンドル(19)とを連動させる変速及び旋回連動機構(69)と、当該連動機構(69)を前記無段変速機構(25)(28)の走行用及び操向用のコントロールレバー(72)(73)に連動連結させる走行変速及び操向リンク機構(70)(71)とを備え、前記操向ハンドル(19)の操向量を大とする程、前記走行用の油圧式無段変速機構(25)を減速操作して、走行速度を減速させるように構成したことを特徴とする移動農機を提供するものである。
Therefore, the present invention includes a traveling crawler (2) and a transmission case (22) that drives the traveling crawler (2), and the transmission case (22) includes a pair of first hydraulic pumps (23) and A traveling hydraulic continuously variable transmission mechanism (25), which is a main transmission mechanism composed of a first hydraulic motor (24), and a steering composed of a pair of second hydraulic pump (26) and second hydraulic motor (27). A mobile agricultural machine equipped with a hydraulic continuously variable transmission mechanism (28) for turning as a mechanism,
A main transmission lever (68) used for operating the traveling hydraulic continuously variable transmission mechanism (25);
A steering handle (19) used for operating the hydraulic continuously variable transmission mechanism (28) for turning;
Shifting and turning interlocking mechanism (69) for interlocking the main transmission lever (68) and the steering handle (19), and the interlocking mechanism (69) for running the continuously variable transmission mechanism (25) (28). And a steering gear link mechanism (70) (71) linked to the steering control levers (72) (73), and the larger the steering amount of the steering handle (19) , The present invention provides a mobile agricultural machine characterized in that the traveling speed is reduced by operating the hydraulic continuously variable transmission mechanism (25) for traveling.

そして、前記主変速レバー(68)を操作して前進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が押されて、当該自在継手軸(88)に連結された変速アーム(84)により揺動軸(82)が次の位置、すなわち、前記操向ハンドル(19)を回動操作して前記連動機構(69)の操作部材(81)を第2枢軸(79)を中心として上に傾けると操向リンク機構(71)の自在継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行うその一方で下に傾けると継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行う位置に揺動し、前記主変速レバー(68)を操作して後進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が引っ張られて、当該自在継手軸(88)に連結された変速アーム(84)によって揺動軸(82)が次の位置、すなわち、後進切換えされた状態で操向ハンドル(19)を回動操作して操作部材(81)を第2枢軸(79)を中心として上に傾けると前記継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行うその一方で下に傾けると継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行う位置に揺動する請求項1に記載の移動農機を提供するものである。
また、前記連動機構(69)は、前記主変速レバー(68)を支持する回動板(75)と、当該回動板(75)を左右方向の第1枢軸(77)を介して前後回動自在に支持する固定取付板(78)と、前後方向に延伸する第2枢軸(79)を介して前記回動板(75)に連結されており当該第2枢軸(79)回りに回動自在に設けられた変速操作部材(80)と、前記第2枢軸(79)の軸回りに回動自在に連結された操向操作部材(81)とを備え、前記変速及び操向リンク機構(70)(71)は、連動機構(69)後方位置で本機フレーム(76)側に揺動軸(82)の外側の揺動筒軸(83)を介して支持される変速アーム(84)と、前記揺動軸(82)に基端を固設する操向アーム(85)と、前記変速操作部材(80)の出力部(80a)および前記操向操作部材(81)の出力部(81a)の各操作出力軸(86)(87)と各アーム(84)(85)間を連結する自在継手軸(88)(89)とを備え、前記第1枢軸(77)を中心として前記変速操作部材(80)が回動されると前記走行用のコントロールレバー(72)が操作されるように前記第1枢軸(77)と前記変速操作部材(80)とが連結されていると共に、前記第2枢軸(79)を中心として前記操向操作部材(81)が回動されると前記操向用のコントロールレバー(73)が操作されるように、前記第2枢軸(79)と前記操向操作部材(81)とが連結されており、前記主変速レバー(68)を前後進操作すると、前記変速操作部材(80)が前記第1枢軸(77)を中心として傾いて前記変速アーム(84)が動作し、これにより前記変速リンク機構(70)によって前後進の切換えが行われ、前記主変速レバー(68)をその中立以外の位置に位置させた状態で、前記操向ハンドル(19)を回動操作すると、前記操作部材(81)が前記第2枢軸(79)を中心として傾いて操向アーム(85)が動作し、これにより前記操向リンク機(71)によって機体の旋回が行われ、前記主変速レバー(68)が前後進操作されて前記変速操作部材(80)が俯角(α1)側に傾けられた状態で、前記操向ハンドル(19)をその中立位置から右或いは左旋回操作して前記操向ハンドル(19)の前記検出リンク(125)によって前記第1揺動アーム(127)を回動させて前記第2減速ロッド(133)を引張り状態にすると、前記自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が縮まって前記変速リンク機構(70)の前記変速アーム(84)が中立方向の低速側に変位し、また前記主変速レバー(68)が前後進操作されて前記変速操作部材(80)が仰角(α2)側に傾けられた状態で、前記操向ハンドル(19)をその中立位置から右或いは左旋回操作して前記操向ハンドル(19)の前記検出リンク(125)によって前記第1揺動アーム(127)を回動させて前記第2減速ロッド(133)を引張り状態にすると、前記自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が大きくなって前記変速リンク機構(70)の前記変速アーム(84)が中立方向の低速側に変位するようになっており、前記操向ハンドル(19)の旋回量に応じて、前記走行用の油圧式無段変速機構(25)の操作に用いられる前記変速リンク機構(70)の走行用のコントロールレバー(72)が動作して減速が行われる請求項1に記載の移動農機を提供するものである。
When the forward shift operation is performed by operating the main transmission lever (68), the universal joint shaft (88) of the transmission link mechanism (70) is pushed by the interlocking mechanism (69), and the universal joint shaft ( 88) the swinging shaft (82) is moved to the next position by the speed change arm (84), that is, the steering handle (19) is rotated to operate the operation member (81) of the interlocking mechanism (69). Is tilted upward with the second pivot (79) as the center, the universal joint shaft (89) of the steering link mechanism (71) is pushed, the steering arm (85) is operated, and the aircraft turns right. If the joint shaft (89) is tilted downward, the steering arm (85) is actuated to swing the machine body to the position where it turns counterclockwise, and the main speed change lever (68) is operated to perform the reverse switching operation. When this is done, the linkage mechanism is operated by the interlock mechanism (69). The universal joint shaft (88) of (70) is pulled, and the swinging shaft (82) is switched to the next position, that is, reversely moved by the transmission arm (84) connected to the universal joint shaft (88). When the steering handle (19) is rotated and the operating member (81) is tilted upward about the second pivot (79), the joint shaft (89) is pulled and the steering arm (85) operates. 2. The machine body according to claim 1, wherein when the machine body turns left, while tilting down, the joint shaft (89) is pushed and the steering arm (85) is operated to swing the machine body to a position where it turns right. A mobile agricultural machine is provided.
The front Symbol interlocking mechanism (69) includes a rotating plate (75) for supporting the main speed change lever (68), the rotary plate (75) before and after via the first pivot in the lateral direction (77) It is connected to the rotating plate (75) via a fixed mounting plate (78) that is rotatably supported and a second pivot (79) extending in the front-rear direction, and rotates around the second pivot (79). A shift operation member (80) provided movably and a steering operation member (81) rotatably connected about the axis of the second pivot (79), the shift and steering link mechanism (70) (71) is a speed change arm (84) supported on the frame (76) side of the interlocking mechanism (69) on the side of the machine frame (76) via a swinging cylindrical shaft (83) outside the swinging shaft (82). ), A steering arm (85) having a base end fixed to the swing shaft (82), and an output of the speed change operation member (80) (80a) and universal joint shafts (88) (89) connecting between the operation output shafts (86) (87) and the arms (84) (85) of the output portion (81a) of the steering operation member (81). ), And when the speed change operation member (80) is rotated about the first pivot (77), the travel control lever (72) is operated. And the speed change operation member (80) are connected, and when the steering operation member (81) is rotated about the second pivot (79), the steering control lever (73) The second pivot (79) and the steering operation member (81) are coupled so that the shift operation member (80) is operated when the main transmission lever (68) is moved forward and backward. Before tilting around the first pivot (77) Change arm (84) operates, which the shift link mechanism (70) reverse switching before by the is performed by the main speed change lever (68) in a state of being positioned in a position other than its neutral, the When the steering handle (19) is rotated, the operating member (81) is tilted about the second pivot (79) to operate the steering arm (85), thereby the steering link machine (71). ), The main speed change lever (68) is moved forward and backward, and the speed change operation member (80) is tilted toward the depression angle (α1), and the steering handle (19) is turned. By turning right or left from the neutral position, the first rocking arm (127) is rotated by the detection link (125) of the steering handle (19) to pull the second deceleration rod (133). When in the state The distance in the horizontal line (L1) direction between the joint portions (88a) and (88b) of the universal joint shaft (88) is shortened so that the speed change arm (84) of the speed change link mechanism (70) is moved to the low speed side in the neutral direction. The steering handle (19) is moved from its neutral position to the right while the main shift lever (68) is moved forward and backward and the shift operation member (80) is tilted to the elevation angle (α2) side. Alternatively, when the left swing rod (133) is pulled by rotating the first swing arm (127) by the detection link (125) of the steering handle (19) by turning left, the second deceleration rod (133) is pulled. The distance in the horizontal line (L1) direction between the joint portions (88a) and (88b) of the universal joint shaft (88) is increased, and the speed change arm (84) of the speed change link mechanism (70) is moved to the low speed side in the neutral direction. To be displaced The traveling control lever (70) of the shift link mechanism (70) used for the operation of the hydraulic continuously variable transmission mechanism (25) for traveling according to the turning amount of the steering handle (19). 72) The mobile agricultural machine according to claim 1, wherein deceleration is performed by operation.

(1)請求項1記載の本発明では、走行クローラ(2)と、当該走行クローラ(2)を駆動するミッションケース(22)とを備え、当該ミッションケース(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)とを備える移動農機であって、前記走行用の油圧式無段変速機構(25)の操作に用いられる主変速レバー(68)と、前記旋回用の油圧式無段変速機構(28)の操作に用いられる操向ハンドル(19)と、前記主変速レバー(68)と前記操向ハンドル(19)とを連動させる変速及び旋回連動機構(69)と、当該連動機構(69)を前記無段変速機構(25)(28)の走行用及び操向用のコントロールレバー(72)(73)に連動連結させる走行変速及び操向リンク機構(70)(71)とを備え、前記操向ハンドル(19)の操向量を大とする程、前記走行用の油圧式無段変速機構(25)を減速操作して、走行速度を減速させるように構成しているため、走行の変速や機体の旋回の作業の煩わしさが低減される。 (1) The present invention according to claim 1 includes a traveling crawler (2) and a mission case (22) for driving the traveling crawler (2), the mission case (22) being a pair of first A traveling hydraulic continuously variable transmission mechanism (25), which is a main transmission mechanism including a hydraulic pump (23) and a first hydraulic motor (24), a pair of second hydraulic pump (26) and a second hydraulic motor ( 27) is a mobile agricultural machine provided with a turning hydraulic continuously variable transmission mechanism (28) which is a steering mechanism consisting of 27), and is used for the operation of the traveling hydraulic continuously variable transmission mechanism (25). The lever (68), the steering handle (19) used for the operation of the hydraulic continuously variable transmission mechanism (28) for turning, and the main transmission lever (68) and the steering handle (19) are interlocked. Shift and turn interlocking mechanism (69), and Traveling transmission and steering link mechanism (70) (71) in which the moving mechanism (69) is interlocked and connected to the control levers (72) and (73) for traveling and steering of the continuously variable transmission mechanism (25) (28). The travel hydraulic speed continuously variable transmission mechanism (25) is decelerated and the travel speed is reduced as the steering amount of the steering handle (19) is increased. For this reason, the troublesome work of shifting gears and turning the body is reduced.

(2)請求項2記載の本発明では、前記主変速レバー(68)を操作して前進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が押されて、当該自在継手軸(88)に連結された変速アーム(84)により揺動軸(82)が次の位置、すなわち、前記操向ハンドル(19)を回動操作して前記連動機構(69)の操作部材(81)を第2枢軸(79)を中心として上に傾けると操向リンク機構(71)の自在継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行うその一方で下に傾けると継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行う位置に揺動し、前記主変速レバー(68)を操作して後進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が引っ張られて、当該自在継手軸(88)に連結された変速アーム(84)によって揺動軸(82)が次の位置、すなわち、後進切換えされた状態で操向ハンドル(19)を回動操作して操作部材(81)を第2枢軸(79)を中心として上に傾けると前記継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行うその一方で下に傾けると継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行う位置に揺動するようになっている。
(3)また、請求項3記載の本発明では、主変速レバー(68)を前後進操作すると、変速操作部材(80)が第1枢軸(77)を中心として傾いて変速アーム(84)が動作し、これにより変速リンク機構(70)によって走行速度の前後進の切換えが行われ、主変速レバー(68)をその中立以外の位置に位置させた状態で、操向ハンドル(19)を回動操作すると、操作部材(81)が第2枢軸(79)を中心として傾いて操向アーム(85)が動作し、これにより操向リンク機(71)によって機体の旋回が行われ、主変速レバー(68)が進操作されて変速操作部材(80)が俯角(α1)側に傾けられた状態で、操向ハンドル(19)をその中立位置から右或いは左旋回操作して操向ハンドル(19)の検出リンク(125)によって第1揺動アーム(127)を回動させて第2減速ロッド(133)を引張り状態にすると、自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が縮まって変速リンク機構(70)の変速アーム(84)が中立方向の低速側に変位し、また主変速レバー(68)が前後進操作されて変速操作部材(80)が仰角(α2)側に傾けられた状態で、操向ハンドル(19)をその中立位置から右或いは左旋回操作して操向ハンドル(19)の検出リンク(125)によって第1揺動アーム(127)を回動させて第2減速ロッド(133)を引張り状態にすると、自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が大きくなって変速リンク機構(70)の変速アーム(84)が中立方向の低速側に変位するようになっており、操向ハンドル(19)の旋回量に応じて、走行用の油圧式無段変速機構(25)の操作に用いられる変速リンク機構(70)の走行用のコントロールレバー(72)が動作して減速が行われるようになっている。したがって、操向操作を行うことなく車速を変更できる。これにより、たとえば、四輪自動車のアクセルペダルに近似した走行クローラの変速操作と旋回動作を容易に行わせることができ、走行クローラの車速制御及び操向制御機能の向上並びに変速操作及び操向操作の簡略化などを容易に図ることができる。
(2) According to the present invention, the universal joint shaft (88) of the transmission link mechanism (70) is operated by the interlocking mechanism (69) when the main transmission lever (68) is operated to perform the forward switching operation. Is pushed, and the rocking shaft (82) is rotated to the next position, that is, the steering handle (19) by the speed change arm (84) connected to the universal joint shaft (88). When the operating member (81) of the mechanism (69) is tilted upward about the second pivot (79), the universal joint shaft (89) of the steering link mechanism (71) is pushed and the steering arm (85) operates. When the aircraft turns right, while tilting downward, the joint shaft (89) is pulled and the steering arm (85) is operated to swing to the position where the aircraft turns left. 68) to perform the reverse switching operation, the interlocking mechanism (6 ) Pulls the universal joint shaft (88) of the transmission link mechanism (70), and the transmission arm (84) connected to the universal joint shaft (88) moves the swing shaft (82) to the next position, that is, When the steering handle (19) is rotated and the operating member (81) is tilted upward with the second pivot (79) as the center, the steering shaft (89) is pulled and the steering arm is turned. When (85) is operated and the aircraft turns left, while tilting down, the joint shaft (89) is pushed and the steering arm (85) is operated so that the aircraft swings to the right turning position. It has become.
(3) According to the third aspect of the present invention, when the main speed change lever (68) is moved forward and backward, the speed change operating member (80) is tilted about the first pivot (77), and the speed change arm (84) is moved. Thus, the forward / reverse travel speed is switched by the speed change link mechanism (70), and the steering handle (19) is turned with the main speed change lever (68) positioned at a position other than its neutral position. When the moving operation is performed, the operating member (81) is tilted about the second pivot (79) and the steering arm (85) is operated, whereby the steering link machine (71) rotates the body, and the main shift is performed. In a state where the lever (68) is advanced and the speed change operation member (80) is tilted to the depression (α1) side, the steering handle (19) is turned right or left from the neutral position to operate the steering handle ( 19) to the detection link (125) Then, when the first rocking arm (127) is rotated to bring the second deceleration rod (133) into a tension state, the horizontal line (L1) between the joint portions (88a) (88b) of the universal joint shaft (88). As the distance in the direction is reduced, the speed change arm (84) of the speed change link mechanism (70) is displaced toward the low speed side in the neutral direction, and the main speed change lever (68) is moved forward and backward to change the speed change operation member (80) to the elevation angle ( In the state tilted to the α2 side, the steering handle (19) is turned right or left from its neutral position, and the first swing arm (127) is moved by the detection link (125) of the steering handle (19). When the second decelerating rod (133) is pulled and rotated, the distance in the horizontal line (L1) direction between the joint portions (88a) and (88b) of the universal joint shaft (88) increases, and the speed change link mechanism ( 70) transmission arm (84) Is shifted to the low speed side in the neutral direction, and the speed change link mechanism (70 used for the operation of the hydraulic continuously variable speed change mechanism (25) for traveling according to the turning amount of the steering handle (19). The control lever (72) for traveling is operated to decelerate . Therefore , the vehicle speed can be changed without performing a steering operation. As a result, for example, the shifting operation and turning operation of the traveling crawler similar to the accelerator pedal of a four-wheeled vehicle can be easily performed, the vehicle speed control and steering control function of the traveling crawler can be improved, and the shifting operation and steering operation can be performed. Can be easily simplified.

以下、本発明の実施例を図面に基づいて詳述する。図1は走行変速及び操向操作部の説明図、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)は丸形操向ハンドル(19)及び運転席(20)など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 view of a traveling speed change and steering operation unit, FIG. 2 is an overall side view of the combine, FIG. 3 is a plan view thereof, and (1) is a track frame for mounting a traveling crawler (2), (3) is a machine base installed on the track frame (1), (4) is a threshing machine with a feed chain (5) stretched to the left and a handling cylinder (6) and a processing cylinder (7) built in. A threshing unit, (8) a cutting unit including a cutting blade (9) and a culm transport mechanism (10), and (11) a hydraulic cylinder that moves the cutting unit (8) up and down 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 milled cylinder (16), (17) Is a discharge auger for unloading the grain of the tank (15), (18) is a round steering handle (19) and Driver's seat (20) operating cabin comprising etc., are 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変速部材としての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操向部材としての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) that drives the traveling crawler (2) is a traveling transmission member that is a main transmission mechanism including a pair of first hydraulic pump (23) and first hydraulic motor (24). As a steering member which is a steering mechanism comprising a hydraulic continuously variable transmission mechanism (25) for traveling as a pair, a second hydraulic pump (26) and a second hydraulic motor (27). And an input shaft (23a) of the first hydraulic pump (23) to the output shaft (21a) of the engine (21) via a transmission belt (29). The input shaft (26a) of the second hydraulic pump (26) is interlocked and connected to the input shaft (23a) of the first hydraulic pump (23) via the 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、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 internal teeth that mesh with the planetary gears (37) and is arranged on the same axis as the sun gear shaft (39). It is pivotally 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)より各ギヤ(43)(44)(45)及び副変速機構(32)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(36)を回転するように構成している。   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) through the gears (43) (44) (45) and the auxiliary transmission mechanism (32) to the sun gear shaft ( The sun gear (36) is rotated by being transmitted to the center gear (46) fixed to 39).

前記副変速機構(32)は、前記ギヤ(45)を有する副変速軸(47)と、前記センタギヤ(46)に噛合うギヤ(48)を有する車速センサ軸(49)とを備え、副変速軸(47)とセンサ軸(49)間に各1対の低速用ギヤ(50)(48)・中速用ギヤ(51)(52)・高速用ギヤ(53)(54)を設けて、中央位置のギヤ(51)のスライド操作によってこれら低速・中速・高速の切換えを可能とさせるように構成している。   The auxiliary transmission mechanism (32) includes an auxiliary transmission shaft (47) having the gear (45) and a vehicle speed sensor shaft (49) having a gear (48) meshing with the center gear (46). A pair of low speed gears (50) (48), medium speed gears (51) (52), and high speed gears (53) (54) are provided between the shaft (47) and the sensor shaft (49). Switching between the low speed, the medium speed, and the high speed is made possible by the sliding operation of the gear (51) at the center position.

また、前記センサ軸(49)には車速検出ギヤ(55)を設けると共に、該ギヤ(55)の回転数より車速を検出する車速センサ(56)を設けている。なお、作業機などに回転力を伝達するPTO軸(57)のPTO入力ギヤ(58)に、PTO伝達ギヤ機構(59)を介し前記出力軸(31)を連動連結させている。   The sensor shaft (49) is provided with a vehicle speed detection gear (55) and a vehicle speed sensor (56) for detecting the vehicle speed from the rotational speed of the gear (55). Note that the output shaft (31) is interlocked and connected to a PTO input gear (58) of a PTO shaft (57) that transmits rotational force to a work machine or the like via a PTO transmission gear mechanism (59).

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(60)(61)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 (60) and (61), 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)の出力軸(62)の出力ギヤからギヤ伝達機構(63)を介し旋回入力軸(64)の入力ギヤ(65a)(65b)に回転出力を伝達し、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(66)の逆転ギヤ(67)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) performs forward / reverse rotation and rotation speed control of the second hydraulic motor (27) by adjusting the angle change of the rotary swash plate of the second hydraulic pump (26). The rotational output is transmitted from the output gear of the output shaft (62) of the second hydraulic motor (27) to the input gears (65a) and (65b) of the swing input shaft (64) through the gear transmission mechanism (63). The second hydraulic pressure is transmitted directly to the external teeth of the left ring gear (38) and to the external teeth of the right ring gear (38) via the reverse gear (67) of the reverse shaft (66). At the time of forward rotation of the motor (27), the left and right ring gears (38) are configured to rotate the left gear (38) in the reverse direction and the right gear (38) in the normal direction at the same left and right rotational speed.

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(46)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(60)(61)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(35)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 (46) to the left and right sun gears (36) at the same rotational speed, and the planetary gear (37), carrier (41) and reduction gear ( 60) (61) is transmitted to the left and right wheel shafts (34a) at the same rotational speed in the same direction of left and right, and the machine 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) is reverse or forward rotation, and the right planetary gear mechanism (35) is forward or reverse rotation, so that the left and right traveling crawler (2) is driven backward and forward, and the aircraft is left or right. Spin-turn on the spot.

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1、図5乃至図12に示す如く、前記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(68)と、旋回用の油圧式無段変速機構(28)に連結する操向ハンドル(19)とを、連動手段である変速及び旋回連動機構(69)に連動連結させると共に、該連動機構(69)を走行変速及び操向リンク機構(70)(71)介し走行及び操向用の無段変速機構(25)(28)のコントロールレバー(72)(73)に連動連結させている。   As shown in FIGS. 1 and 5 to 12, the main transmission lever (68) connected to the traveling hydraulic continuously variable transmission mechanism (25) and the turning hydraulic continuously variable transmission mechanism (28) are connected. The steering handle (19) to be linked is linked to the shift and turn interlocking mechanism (69) which is the interlocking means, and the interlocking mechanism (69) is traveled via the travel shift and steering link mechanisms (70) (71). In addition, the steering continuously variable transmission mechanisms (25) and (28) are linked to control levers (72) and (73).

前記連動機構(69)は、主変速レバー(68)の基端折曲部(68a)を筒軸(74)に左右揺動自在に支持する回動板(75)と、機体側の本機フレーム(76)に固設して前記回動板(75)を左右方向の第1枢軸(77)を介し前後回動自在に支持する固定取付板(78)と、前記枢軸(77)とは直交する前後方向の第2枢軸(79)を介して回動板(75)に連結させて該軸(79)回りに回動自在に設ける変速操作部材(80)と、前記第2枢軸(79)の軸回りに回動自在に連結させる操向操作部材(81)とを備え、変速及び操向操作部材(80)(81)の第2枢軸(79)とは偏心位置の各操作出力部(80a)(81a)を変速及び操向リンク機構(70)(71)に連動連結させている。   The interlocking mechanism (69) includes a rotating plate (75) for supporting the base end bent portion (68a) of the main transmission lever (68) on the cylindrical shaft (74) so as to be swingable in the left-right direction, and the main body side machine. A fixed mounting plate (78) fixed to a frame (76) and supporting the rotating plate (75) through a first pivot (77) in the left-right direction so as to be capable of pivoting back and forth, and the pivot (77). A speed change operation member (80) that is connected to a rotating plate (75) through a second pivot (79) in the front-rear direction orthogonal to the shaft (79) and is rotatable about the shaft (79), and the second pivot (79) ) And a steering operation member (81) that is pivotally connected around the axis of the gear, and the second pivot (79) of the speed change and steering operation members (80) and (81) is each operation output portion at an eccentric position. (80a) (81a) are interlockingly connected to the speed change and steering link mechanism (70) (71).

前記変速及び操向リンク機構(70)(71)は、連動機構(69)後方位置で本機フレーム(76)側に揺動軸(82)外側の揺動筒軸(83)を介し支持する変速アーム(84)と、前記揺動軸(82)に基端を固設する操向アーム(85)と、前記出力部(80a)(81a)の各操作出力軸(86)(87)と各アーム(84)(85)間を連結する自在継手軸(88)(89)と、前記筒軸(83)及び揺動軸(82)の右端に固設する変速及び操向出力アーム(90)(91)と、前記運転キャビン(18)の回動支点軸(92)の支点軸受(93)に取付ける中間軸(94)に回転自在に設ける変速及び操向用第1揺動アーム(95)(96)と、前記出力アーム(90)(91)と第1揺動アーム(95)(96)の各先端間をそれぞれ連結する変速及び操向用自在継手形第1ロッド(97)(98)と、前記中間軸(94)に設けて第1揺動アーム(95)(96)に一体連結する変速及び操向用第2揺動アーム(99)(100)と、前記ミッションケース(22)上部の軸受板(101)に取付ける支軸(102)に回動自在に支持させる変速及び操向用筒軸(103)(104)と、該筒軸(103)(104)に基端を固設する第1揺動アーム(105)(106)と前記第2揺動アーム(99)(100)の各先端間を連結する変速及び操向用自在継手形第2ロッド(107)(108)と、前記筒軸(103)(104)に基端を固設する第2揺動アーム(109)(110)と前記コントロールレバー(72)(73)の各先端間を連結させる変速及び操向用自在継手形第3ロッド(111)(112)とを備え、前記第1枢軸(77)を中心とした走行操作部材(80)の回動によって走行用のコントロールレバー(72)を、また走行中の第2枢軸(79)を中心とした操向操作部材(81)の回動によって操向用のコントロールレバー(73)を操作して変速及び操向制御を行うように構成している。   The shift and steering link mechanisms (70) (71) are supported on the frame (76) side of the machine mechanism (69) via the swinging cylinder shaft (83) outside the swinging shaft (82) at the rear position of the interlocking mechanism (69). A transmission arm (84), a steering arm (85) having a base end fixed to the swing shaft (82), and each operation output shaft (86) (87) of the output sections (80a) (81a) Universal joint shafts (88) and (89) for connecting the arms (84) and (85), and a shift and steering output arm (90) fixed to the right ends of the cylindrical shaft (83) and the swing shaft (82). ) (91) and a first swing arm (95) for shifting and steering provided rotatably on an intermediate shaft (94) attached to a fulcrum bearing (93) of the pivot fulcrum shaft (92) of the operating cabin (18). ) (96), and tips of the output arms (90) (91) and the first swing arms (95) (96) And a universal joint-type first rod (97) (98) for shifting and steering, and a shift and steering gear connected to the first swing arm (95) (96) provided on the intermediate shaft (94). Shifting and steering cylinder shaft (100) that is rotatably supported by a second pivot arm (99) (100) for direction and a support shaft (102) attached to the bearing plate (101) above the transmission case (22). 103) (104), and the distal ends of the first swing arm (105) (106) and the second swing arm (99) (100), the base end of which is fixed to the cylindrical shaft (103) (104). Universal joint-type second rods (107) (108) for shifting and steering, and second swing arms (109) (110) having base ends fixed to the cylindrical shafts (103) (104) And control levers (72) and (73) are connected to each tip. And a steering universal joint type third rod (111) (112), and a travel control member (80) is rotated by a travel operation member (80) about the first pivot (77). Further, the steering control member (81) is operated by the rotation of the steering operation member (81) around the second pivot (79) during traveling to perform the shift and steering control. ing.

一方、前記操向ハンドル(19)下端のハンドル操作軸(113)にギヤ(114)を設けて、この後方の回転軸(115)に取付けるセクタギヤ(116)に前記ギヤ(114)を噛合せると共に、前記主変速レバー(68)位置下方に配設する操向軸(117)の第1揺動アーム(118)と、前記回転軸(115)に基端を固設する出力アーム(119)との各先端間を操向リンク機構である自在継手形操向第1ロッド(120)を介して連結させ、操向軸(117)の第1揺動アーム(118)と一体の第2揺動アーム(121)を、前記自在継手軸(89)の前端に自在継手形操向第2ロッド(122)を介して連結させ、前記ハンドル(19)の回動操作によって前記第2枢軸(79)を中心として操向操作部材(81)を回動するように構成している。   On the other hand, a gear (114) is provided on the handle operating shaft (113) at the lower end of the steering handle (19), and the gear (114) is engaged with a sector gear (116) attached to the rear rotating shaft (115). A first swing arm (118) of a steering shaft (117) disposed below the position of the main transmission lever (68), and an output arm (119) having a base end fixed to the rotating shaft (115). Are connected to each other via a universal joint type steering first rod (120) which is a steering link mechanism, and a second swinging integral with the first swinging arm (118) of the steering shaft (117). An arm (121) is connected to the front end of the universal joint shaft (89) via a universal joint-type steering second rod (122), and the second pivot (79) is operated by rotating the handle (19). Rotate the steering operation member (81) around It is configured to so that.

また、前記ハンドル操作軸(113)のギヤ(114)下方に中立位置決め板(123)を設けていて、該位置決め板(123)下面の突出軸(124)に操向検出リンク(125)の一端を連結させ、前記回転軸(115)の右側に配設する減速アーム軸(126)の第1揺動アーム(127)と前記検出リンク(125)の他端長孔(125a)とを軸(128)を介し連結させると共に、前記操向軸(117)の減速アーム(129)と減速アーム軸(126)の第2揺動アーム(130)との各先端間を減速リンク機構である自在継手形第1減速ロッド(131)で連結させ、前記変速操作部材(80)の最右端の減速伝達軸(132)と第2揺動アーム(130)の他端間を自在継手形第2減速ロッド(133)で連結させて、走行状態で前記ハンドル(19)の操向量を大とする程第2減速ロッド(133)を下方に引張って走行速度を減速させるように構成している。   Further, a neutral positioning plate (123) is provided below the gear (114) of the handle operating shaft (113), and one end of the steering detection link (125) is attached to the protruding shaft (124) on the lower surface of the positioning plate (123). And the first swing arm (127) of the reduction arm shaft (126) disposed on the right side of the rotation shaft (115) and the other end long hole (125a) of the detection link (125) are connected to the shaft ( 128), and a universal joint which is a speed reduction link mechanism between the tips of the speed reduction arm (129) of the steering shaft (117) and the second swing arm (130) of the speed reduction arm axis (126). The first speed reduction rod (131) is connected, and the rightmost speed reduction transmission shaft (132) of the speed change operation member (80) and the other end of the second swing arm (130) are connected with a universal joint type second speed reduction rod. Connect at (133) and run State is configured so as to decelerate the steering amount to pull the second reduction rod enough to a large (133) below the running speed of the handle (19).

ところで、前記変速及び操向操作部材(80)(81)を軸回りに回動可能とさせる第2枢軸(79)と、操向アーム(85)と継手軸(89)との自在継手部(89a)とを前後方向の水平ライン(L1)上に位置させ、また前記操作出力軸(86)(87)と自在継手軸(88)(89)との自在継手部(88b)(89b)と、第1枢軸(77)とを前記ライン(L1)に直交させる左右水平ライン(L2)上に位置させ、さらに前記変速アーム(84)と継手軸(88)との自在継手部(88a)と前記継手部(89a)とを前記ライン(L2)と平行な左右水平ライン(L3)上に位置させ、且つ継手部(89a)に継手部(88a)を可及的に接近(最大限近い位置)させて、主変速レバー(68)及び操向ハンドル(19)の中立保持時に、操向ハンドル(19)が操作されても、操向操作部材(81)を第2枢軸(79)の軸回りに回動させるのみとさせて、自在継手軸(89)には操作力を作用させないものである。   By the way, a universal joint portion (a second pivot (79) that allows the shift and steering operation members (80) and (81) to rotate about an axis, and a steering arm (85) and a joint shaft (89) ( 89a) is positioned on the horizontal line (L1) in the front-rear direction, and the universal joint portions (88b) (89b) of the operation output shafts (86) (87) and the universal joint shafts (88) (89) The first pivot (77) is positioned on a horizontal horizontal line (L2) orthogonal to the line (L1), and a universal joint (88a) between the transmission arm (84) and the joint shaft (88) The joint part (89a) is positioned on the horizontal horizontal line (L3) parallel to the line (L2), and the joint part (88a) is as close as possible to the joint part (89a) (position closest to the maximum). ) Of the main transmission lever (68) and the steering handle (19). Even when the steering handle (19) is operated at the time of standing, the steering operating member (81) is merely rotated around the axis of the second pivot (79), and the universal joint shaft (89) The operating force is not applied.

そして、図8にも示す如く、主変速レバー(68)の前後進操作で、第1枢軸(77)を中心として操作部材(80)を前後に角度(α1)(α2)傾けるとき前記継手軸(88)を引張って或いは押して変速アーム(84)を動作させて走行速度の前後進の切換えを行うと共に、図9に示す如くこの状態中(主変速レバー(68)が中立以外のとき)に操向ハンドル(19)の回動操作で第2枢軸(79)を中心として操作部材(81)を上下に角度(β1)(β2)傾けるとき継手軸(89)を引張って或いは押して操向アーム(85)を動作させて機体の左及び右旋回を行うものである。(主変速の中立時に旋回操作を行っても継手軸(89)はライン(L1)を中心とした円錐面上にも移動する状態となって継手部(89a)(89b)間の距離は変化しない。)
また、図11にも示す如く、前記操向ハンドル(19)に設ける検出リンク(125)は中立位置より右或いは左旋回操作の何れにおいても第1揺動アーム(127)を同一方向に角度(θ)の範囲で回動させて第2減速ロッド(133)を常に引張る状態とさせて、前進操作時の操作部材(80)が角度(α1)側に傾いてるときには、継手部(88a)(88b)間の距離を縮め、また後進操作時の操作部材(80)が角度(α2)側に傾いているときには、継手部(88a)(88b)間の距離を大きくして、変速アーム(84)をそれぞれ中立方向の低速側に変位させて、その旋回量に応じた減速を行うものである。
As shown in FIG. 8, when the main transmission lever (68) is moved forward and backward, the joint shaft is tilted when the operation member (80) is tilted back and forth by an angle (α1) (α2) about the first pivot (77). Pull or push (88) to operate the speed change arm (84) to switch the travel speed forward and backward, and during this state (when the main speed change lever (68) is other than neutral) as shown in FIG. When the operating member (81) is tilted up and down by an angle (β1) (β2) about the second pivot (79) by rotating the steering handle (19), the steering shaft (89) is pulled or pushed to operate the steering arm (85) is operated to turn the aircraft left and right. (Even when the turning operation is performed at the neutral position of the main speed, the joint shaft (89) also moves on the conical surface centered on the line (L1), and the distance between the joint portions (89a) and (89b) changes. do not do.)
Further, as shown in FIG. 11, the detection link (125) provided on the steering handle (19) has the first swing arm (127) angled in the same direction in either the right or left turn operation from the neutral position. When the operating member (80) during forward operation is inclined to the angle (α1) side by rotating in the range of θ) so that the second deceleration rod (133) is always pulled, the joint portion (88a) ( 88b) is shortened, and when the operation member (80) during reverse operation is inclined to the angle (α2) side, the distance between the joint portions (88a) (88b) is increased, and the speed change arm (84 ) Are respectively displaced toward the low speed side in the neutral direction, and the speed is reduced according to the turning amount.

さらに、変速及び操向の操作力を伝達する前記第1ロッド(97)(98)と揺動アーム(95)(96)の自在継手部(97a)(98a)の中心を、運転キャビン(18)の回動支点軸(92)位置に一致させて、変速及び操向の中立保持においてはこれらの操作系を取外すことなく運転キャビン(18)の前方向への回動を可能とさせるように構成している。   Further, the center of the universal joints (97a) and (98a) of the first rods (97) and (98) and the swing arms (95) and (96) for transmitting the operating force for shifting and steering are arranged in the driving cabin (18 ) To coincide with the position of the pivot fulcrum shaft (92) so that the driving cabin (18) can be rotated in the forward direction without removing these operating systems in the neutral holding of shifting and steering. It is composed.

走行変速及び操向操作部の説明図である。It is explanatory drawing of a driving | running | working transmission and steering operation part. コンバインの全体側面図である。It is a whole side view of a combine. コンバインの全体平面図である。It is a whole top view of a combine. ミッション駆動系の説明図である。It is explanatory drawing of a mission drive system. 操作部の正面説明図である。It is front explanatory drawing of an operation part. 操作部の平面説明図である。It is plane explanatory drawing of an operation part. 操作部の側面説明図である。It is side surface explanatory drawing of an operation part. 操作部材の側面説明図である。It is side surface explanatory drawing of an operation member. 操作部材の正面説明図である。It is front explanatory drawing of an operation member. 操作部材の平面説明図である。It is a plane explanatory view of an operation member. 操向ハンドル部の平面説明図である。It is a plane explanatory view of a steering handle part. リンク機構部の平面説明図である。It is plane explanatory drawing of a link mechanism part.

符号の説明Explanation of symbols

(19) 操向ハンドル
(25) 油圧変速機構
(28) 油圧操向機構
(68) 変速レバー
(70)(71) リンク機構
(77)(79) 枢軸
(80)(81) 操作部材
(120) ロッド(リンク機構)
(19) Steering handle (25) Hydraulic transmission mechanism (28) Hydraulic steering mechanism (68) Shift lever (70) (71) Link mechanism (77) (79) Pivot (80) (81) Operating member (120) Rod (link mechanism)

Claims (3)

走行クローラ(2)と、当該走行クローラ(2)を駆動するミッションケース(22)とを備え、当該ミッションケース(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)とを備える移動農機であって、
前記走行用の油圧式無段変速機構(25)の操作に用いられる主変速レバー(68)と、
前記旋回用の油圧式無段変速機構(28)の操作に用いられる操向ハンドル(19)と、
前記主変速レバー(68)と前記操向ハンドル(19)とを連動させる変速及び旋回連動機構(69)と、
当該連動機構(69)を前記無段変速機構(25)(28)の走行用及び操向用のコントロールレバー(72)(73)に連動連結させる走行変速及び操向リンク機構(70)(71)とを備え、
前記操向ハンドル(19)の操向量を大とする程、前記走行用の油圧式無段変速機構(25)を減速操作して、走行速度を減速させるように構成したことを特徴とする移動農機。
A traveling crawler (2) and a transmission case (22) for driving the traveling crawler (2) are provided. The transmission case (22) includes a pair of a first hydraulic pump (23) and a first hydraulic motor (24). ) A hydraulic continuously variable transmission mechanism (25) for traveling which is a main transmission mechanism, and a steering mechanism which is a steering mechanism consisting of a pair of second hydraulic pump (26) and a second hydraulic motor (27). A mobile agricultural machine comprising a hydraulic continuously variable transmission mechanism (28),
A main transmission lever (68) used for operating the traveling hydraulic continuously variable transmission mechanism (25);
A steering handle (19) used for operating the hydraulic continuously variable transmission mechanism (28) for turning;
A shifting and turning interlocking mechanism (69) for interlocking the main transmission lever (68) and the steering handle (19);
Traveling shift and steering link mechanism (70) (71) in which the interlocking mechanism (69) is interlocked and connected to the control levers (72) and (73) for driving and steering of the continuously variable transmission mechanism (25) (28). )
The movement characterized in that the traveling speed is reduced by decelerating the traveling hydraulic continuously variable transmission mechanism (25) as the steering amount of the steering handle (19) increases. Agricultural machinery.
前記主変速レバー(68)を操作して前進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が押されて、当該自在継手軸(88)に連結された変速アーム(84)により揺動軸(82)が次の位置、すなわち、前記操向ハンドル(19)を回動操作して前記連動機構(69)の操作部材(81)を第2枢軸(79)を中心として上に傾けると操向リンク機構(71)の自在継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行うその一方で下に傾けると継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行う位置に揺動し、前記主変速レバー(68)を操作して後進切換え操作を行うと、前記連動機構(69)によって変速リンク機構(70)の自在継手軸(88)が引っ張られて、当該自在継手軸(88)に連結された変速アーム(84)によって揺動軸(82)が次の位置、すなわち、後進切換えされた状態で操向ハンドル(19)を回動操作して操作部材(81)を第2枢軸(79)を中心として上に傾けると前記継手軸(89)が引っ張られて操向アーム(85)が動作され機体が左旋回を行うその一方で下に傾けると継手軸(89)が押されて操向アーム(85)が動作され機体が右旋回を行う位置に揺動する請求項1に記載の移動農機。 When the main transmission lever (68) is operated to perform forward switching operation, the interlocking mechanism (69) pushes the universal joint shaft (88) of the transmission link mechanism (70), and the universal joint shaft (88). The swing arm (82) is rotated to the next position, that is, the steering handle (19) is rotated by the speed change arm (84) connected to the operation member (81) of the interlock mechanism (69). When the two pivots (79) are tilted upward, the universal joint shaft (89) of the steering link mechanism (71) is pushed to operate the steering arm (85), while the aircraft turns right, while When the joint shaft (89) is pulled, the steering arm (85) is operated to swing the machine body to the left-turning position. When the main speed change lever (68) is operated, the reverse switching operation is performed. , The link mechanism (70) by the interlock mechanism (69). The universal joint shaft (88) is pulled, and the swinging shaft (82) is steered in the next position, that is, reversely switched by the speed change arm (84) connected to the universal joint shaft (88). When the handle (19) is rotated and the operating member (81) is tilted upward about the second pivot (79), the joint shaft (89) is pulled, and the steering arm (85) is operated to move the fuselage. 2. The mobile agricultural machine according to claim 1, wherein when the vehicle is turned counterclockwise, the joint shaft (89) is pushed, the steering arm (85) is operated, and the machine body swings to a position where it turns right . 記連動機構(69)は、前記主変速レバー(68)を支持する回動板(75)と、当該回動板(75)を左右方向の第1枢軸(77)を介して前後回動自在に支持する固定取付板(78)と、前後方向に延伸する第2枢軸(79)を介して前記回動板(75)に連結されており当該第2枢軸(79)回りに回動自在に設けられた変速操作部材(80)と、前記第2枢軸(79)の軸回りに回動自在に連結された操向操作部材(81)とを備え、
前記変速及び操向リンク機構(70)(71)は、連動機構(69)後方位置で本機フレーム(76)側に揺動軸(82)の外側の揺動筒軸(83)を介して支持される変速アーム(84)と、前記揺動軸(82)に基端を固設する操向アーム(85)と、前記変速操作部材(80)の出力部(80a)および前記操向操作部材(81)の出力部(81a)の各操作出力軸(86)(87)と各アーム(84)(85)間を連結する自在継手軸(88)(89)とを備え、
前記第1枢軸(77)を中心として前記変速操作部材(80)が回動されると前記走行用のコントロールレバー(72)が操作されるように前記第1枢軸(77)と前記変速操作部材(80)とが連結されていると共に、前記第2枢軸(79)を中心として前記操向操作部材(81)が回動されると前記操向用のコントロールレバー(73)が操作されるように、前記第2枢軸(79)と前記操向操作部材(81)とが連結されており、
前記主変速レバー(68)を前後進操作すると、前記変速操作部材(80)が前記第1枢軸(77)を中心として傾いて前記変速アーム(84)が動作し、これにより前記変速リンク機構(70)によって前後進の切換えが行われ、
前記主変速レバー(68)をその中立以外の位置に位置させた状態で、前記操向ハンドル(19)を回動操作すると、前記操作部材(81)が前記第2枢軸(79)を中心として傾いて操向アーム(85)が動作し、これにより前記操向リンク機(71)によって機体の旋回が行われ、
前記主変速レバー(68)が前後進操作されて前記変速操作部材(80)が俯角(α1)側に傾けられた状態で、前記操向ハンドル(19)をその中立位置から右或いは左旋回操作して前記操向ハンドル(19)の前記検出リンク(125)によって前記第1揺動アーム(127)を回動させて前記第2減速ロッド(133)を引張り状態にすると、前記自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が縮まって前記変速リンク機構(70)の前記変速アーム(84)が中立方向の低速側に変位し、また前記主変速レバー(68)が前後進操作されて前記変速操作部材(80)が仰角(α2)側に傾けられた状態で、前記操向ハンドル(19)をその中立位置から右或いは左旋回操作して前記操向ハンドル(19)の前記検出リンク(125)によって前記第1揺動アーム(127)を回動させて前記第2減速ロッド(133)を引張り状態にすると、前記自在継手軸(88)の継手部(88a)(88b)間の水平ライン(L1)方向の距離が大きくなって前記変速リンク機構(70)の前記変速アーム(84)が中立方向の低速側に変位するようになっており、前記操向ハンドル(19)の旋回量に応じて、前記走行用の油圧式無段変速機構(25)の操作に用いられる前記変速リンク機構(70)の走行用のコントロールレバー(72)が動作して減速が行われる請求項1に記載の移動農機。
Before SL interlocking mechanism (69), said main pivot plate for supporting the shift lever (68) and (75), back-and-forth rotation the rotating plate (75) via a first pivot in the lateral direction (77) A fixed mounting plate (78) that is freely supported and a second pivot (79) extending in the front-rear direction are connected to the pivot plate (75) and are rotatable about the second pivot (79). A shift operation member (80) provided on the second pivot shaft (79), and a steering operation member (81) rotatably connected around the axis of the second pivot (79).
The speed change and steering link mechanisms (70) (71) are arranged at the rear position of the interlocking mechanism (69) via the swinging cylinder shaft (83) outside the swinging shaft (82) on the machine frame (76) side. A shift arm (84) to be supported, a steering arm (85) having a base end fixed to the swing shaft (82), an output portion (80a) of the shift operation member (80), and the steering operation Universal operation shafts (88) and (89) for connecting the operation output shafts (86) and (87) of the output portion (81a) of the member (81) and the arms (84) and (85),
The first pivot (77) and the speed change operation member so that the travel control lever (72) is operated when the speed change operation member (80) is rotated about the first pivot (77). (80), and when the steering operation member (81) is rotated about the second pivot (79), the steering control lever (73) is operated. The second pivot (79) and the steering operation member (81) are connected to each other,
When the main speed change lever (68) is operated forward and backward, the speed change operating member (80) is tilted about the first pivot (77) to operate the speed change arm (84), whereby the speed change link mechanism ( reverse switching before by the 70) is performed,
When the steering handle (19) is rotated with the main transmission lever (68) positioned at a position other than its neutral position, the operating member (81) is centered on the second pivot (79). The steering arm (85) is tilted and the aircraft is turned by the steering link machine (71).
The steering handle (19) is turned right or left from its neutral position in a state where the main transmission lever (68) is moved forward and backward and the transmission operation member (80) is tilted to the depression (α1) side. Then, when the first rocking arm (127) is rotated by the detection link (125) of the steering handle (19) to bring the second deceleration rod (133) into a tension state, the universal joint shaft ( 88), the distance in the horizontal line (L1) direction between the joint portions (88a) and (88b) is reduced, and the transmission arm (84) of the transmission link mechanism (70) is displaced toward the low speed side in the neutral direction. With the main speed change lever (68) moved forward and backward and the speed change operation member (80) tilted to the elevation angle (α2) side, the steering handle (19) is turned right or left from its neutral position. The steering hand When the first rocking arm (127) is rotated by the detection link (125) of the rod (19) to bring the second deceleration rod (133) into a tensioned state, the joint portion of the universal joint shaft (88) The distance in the horizontal line (L1) direction between (88a) and (88b) is increased so that the speed change arm (84) of the speed change link mechanism (70) is displaced toward the low speed side in the neutral direction. In accordance with the turning amount of the steering handle (19), the traveling control lever (72) of the transmission link mechanism (70) used for the operation of the traveling hydraulic continuously variable transmission mechanism (25) operates. The mobile agricultural machine according to claim 1, wherein deceleration is performed.
JP2004280490A 2004-09-27 2004-09-27 Mobile farm machine Expired - Lifetime JP3930505B2 (en)

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JP18546096A Division JP3708634B2 (en) 1996-06-25 1996-06-25 Combine operating device

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