以下、本発明の実施形態を、トラクタに適用した場合の図面に基づき、説明する。図１〜図４に示す如く、図中符号１０は、トラクタを示す。トラクタ１０は、走行機体１１と、走行機体１１の前部を支持する左右一対の前車輪１２と、前記走行機体１１の後部を支持する左右一対の後クローラ走行装置１３とを備えている。前記走行機体１１には、エンジン８を搭載すると共に、操縦座席９を設けている。
Hereinafter, embodiments of the present invention will be described with reference to the drawings when applied to a tractor. As shown in FIGS. 1-4, the code | symbol 10 in a figure shows a tractor. The tractor 10 includes a traveling machine body 11, a pair of left and right front wheels 12 that support the front part of the traveling machine body 11, and a pair of left and right rear crawler traveling devices 13 that support the rear part of the traveling machine body 11. The traveling body 11 is equipped with an engine 8 and a control seat 9.
図１〜図４に示す如く、前記走行機体１１の後部にミッションケース４０を搭載する。ミッションケース４０の左右両側に左右の後車軸ケース１４を設けている。走行機体１１に後車軸ケース１４を介して後クローラ走行装置１３を着脱可能に取付ける。図９に示す如く、後車軸ケース１４内に後車軸１５の一端側を軸支し、その後車軸１５の一端側に減速用ファイナルギヤ３７を軸支する。後車軸ケース１４から後車軸１５の他端側を突出させ、その後車軸１５の他端側に駆動輪体１６を取付けている。一方、前記後車軸ケース１４よりも下方に、前後方向に延設したトラックフレーム１７を配設する。前記後車軸ケース１４にフランジ部材１８を着脱可能に締結固定する。前記後車軸１５よりも前側に配設する前リンク部材１９と、前記後車軸１５よりも後側に配設する後リンク部材２０とを備える。フランジ部材１８に各リンク部材１９、２０を介してトラックフレーム１７を前後移動可能に連結している。
As shown in FIGS. 1 to 4, a transmission case 40 is mounted on the rear part of the traveling machine body 11. Left and right rear axle cases 14 are provided on both left and right sides of the mission case 40. A rear crawler traveling device 13 is detachably attached to the traveling machine body 11 via a rear axle case 14. As shown in FIG. 9, one end of the rear axle 15 is pivotally supported in the rear axle case 14, and then a reduction final gear 37 is pivotally supported on one end of the axle 15. The other end side of the rear axle 15 is protruded from the rear axle case 14, and then the driving wheel body 16 is attached to the other end side of the axle 15. On the other hand, a track frame 17 extending in the front-rear direction is disposed below the rear axle case 14. A flange member 18 is detachably fastened to the rear axle case 14. A front link member 19 disposed on the front side of the rear axle 15 and a rear link member 20 disposed on the rear side of the rear axle 15 are provided. The track frame 17 is connected to the flange member 18 via the link members 19 and 20 so as to be movable back and forth.
図１〜図４に示す如く、前記トラックフレーム１７の前端側にテンション調節機構２２を介して前従動輪体２１を取付ける。トラックフレーム１７の後端側に後従動輪体２３を支持軸２４にて取付ける。前記駆動輪体１６と、前記前従動輪体２１と、前記後従動輪体２３との三者には、履帯としての合成ゴム製の走行クローラ２５を、略三角形状に巻掛けしている。前記駆動輪体１６（後車軸１５）を適宜速度で正回転又は逆回転させて、走行クローラ２５を正回転又は逆回転駆動することによって、走行機体１１が前進走行又は後退走行するように構成している。
As shown in FIGS. 1 to 4, a front driven wheel body 21 is attached to the front end side of the track frame 17 via a tension adjusting mechanism 22. A rear driven wheel body 23 is attached to the rear end side of the track frame 17 by a support shaft 24. Synthetic rubber traveling crawlers 25 serving as crawler belts are wound around the drive wheel body 16, the front driven wheel body 21, and the rear driven wheel body 23 in a substantially triangular shape. The driving wheel body 16 (rear axle 15) is rotated forward or backward at an appropriate speed and the traveling crawler 25 is driven forward or backward to drive the traveling machine body 11 forward or backward. ing.
なお、複数の転動輪２６及びクローラガイド体４１を備える。前記トラックフレーム１７に前記複数の転動輪２６を回転自在に設けている。トラックフレーム１７にクローラガイド体４１を締結固定している。前記走行クローラ２５の内周面のうち、前従動輪体２１と後従動輪体２３との間の内周面（走行クローラ２５の接地側の内周面）に、複数の転動輪２６及びクローラガイド体４１を接触させる。複数の転動輪２６とクローラガイド体４１によって、走行クローラ２５の接地側を着地支持するように構成している。
A plurality of rolling wheels 26 and a crawler guide body 41 are provided. The plurality of rolling wheels 26 are rotatably provided on the track frame 17. A crawler guide body 41 is fastened and fixed to the track frame 17. Of the inner peripheral surface of the traveling crawler 25, an inner peripheral surface between the front driven wheel body 21 and the rear driven wheel body 23 (an inner peripheral surface on the grounding side of the traveling crawler 25) is provided with a plurality of rolling wheels 26 and crawlers. The guide body 41 is brought into contact. The plurality of rolling wheels 26 and the crawler guide body 41 are configured to land and support the grounding side of the traveling crawler 25.
図３、図４に示す如く、前記フランジ部材１８に前後の上端枢着軸２７，２８を設ける。前記後車軸１５と平行に前後の上端枢着軸２７，２８を延設する。前後の上端枢着軸２７，２８に、前リンク部材１９及び後リンク部材２０の上端側ボス部を回転自在に軸支する。前記トラックフレーム１７に前後の下端枢着軸３０，３１を設ける。前リンク部材１９は、その下端が前記トラックフレーム１７に前下端枢着軸３０にて回転自在に連結されている。前上端枢着軸２７よりも前下端枢着軸３０を前側に位置させ、前リンク部材１９を前向きに傾斜させて支持している。
As shown in FIGS. 3 and 4, front and rear upper pivot shafts 27 and 28 are provided on the flange member 18. Front and rear upper end pivot shafts 27 and 28 are extended in parallel with the rear axle 15. The upper end side boss portions of the front link member 19 and the rear link member 20 are rotatably supported by the front and rear upper end pivot shafts 27 and 28. The track frame 17 is provided with front and rear lower pivot shafts 30 and 31. The lower end of the front link member 19 is rotatably connected to the track frame 17 by a front lower end pivot shaft 30. The front lower end pivot shaft 30 is positioned on the front side of the front upper pivot shaft 27, and the front link member 19 is tilted forward and supported.
また、図３、図４に示す如く、後リンク部材２０は、その下端が前記トラックフレーム１７に後下端枢着軸３１にて回転自在に連結されている。後上端枢着軸２８よりも後下端枢着軸３１を後側に位置させ、後リンク部材２０を後ろ向きに傾斜させて支持している。これにより、前後のリンク部材１９，２０は、前記トラクタ１０における側面視（図３、図４）において、互いに下広がりのハ字状の配設になっている。なお、走行クローラ２５は、前記トラクタ１０における側面視（図３、図４）において、前記後車軸１５を通る鉛直線から前従動輪体２１までの距離が、前記鉛直線から後従動輪体２３までの距離よりも大きい略三角形状に張設される。
As shown in FIGS. 3 and 4, the rear link member 20 has a lower end rotatably connected to the track frame 17 by a rear lower end pivot shaft 31. The rear lower end pivot shaft 31 is positioned rearward of the rear upper pivot shaft 28, and the rear link member 20 is tilted backward and supported. As a result, the front and rear link members 19 and 20 are arranged in a C shape spreading downward from each other in a side view of the tractor 10 (FIGS. 3 and 4). The travel crawler 25 has a distance from the vertical line passing through the rear axle 15 to the front driven wheel body 21 in the side view of the tractor 10 (FIGS. 3 and 4). It is stretched in a substantially triangular shape larger than the distance up to.
上記の構成により、トラクタ１０を前進走行させた場合、走行クローラ２５が地面から前進反力を受けることによって、走行機体１１に対してトラックフレーム１７が前方向に移動し、走行クローラ２５が前上がり姿勢に傾斜する。即ち、前記トラックフレーム１７が、前記走行機体１１に対して前方向に移動するとき、上端枢着軸２７を支点として水平面からの傾斜角度が小さくなるように、前リンク部材１９が倒れる方向に回動する。また、上端枢着軸２８を支点として水平面からの傾斜角度が大きくなるように、後リンク部材２０が起立する方向に回動する。その結果、走行クローラ２５が前上がりに傾斜して、前進移動する。
With the above configuration, when the tractor 10 is caused to travel forward, the traveling crawler 25 receives the forward reaction force from the ground, whereby the track frame 17 moves forward with respect to the traveling machine body 11 and the traveling crawler 25 rises forward. Inclined to posture. That is, when the track frame 17 moves in the forward direction with respect to the traveling machine body 11, the front link member 19 is rotated in the direction in which the front link member 19 is tilted so that the inclination angle from the horizontal plane becomes small with the upper pivot shaft 27 as a fulcrum. Move. Further, the rear link member 20 rotates in the direction in which the rear link member 20 stands up so that the inclination angle from the horizontal plane becomes larger with the upper end pivot shaft 28 as a fulcrum. As a result, the traveling crawler 25 tilts forward and moves forward.
一方、トラクタ１０を後進走行させた場合、地面から後進反力を受けることによって、走行機体１１に対してトラックフレーム１７が後ろ方向に移動し、走行クローラ２５が前下がり姿勢に傾斜する。即ち、前記トラックフレーム１７が、前記走行機体１１に対して後方向に移動するとき、上端枢着軸２７を支点として水平面からの傾斜角度が大きくなるように、前リンク部材１９が起立する方向に回動する。また、上端枢着軸２８を支点として水平面からの傾斜角度が小さくなるように、後リンク部材２０が倒れる方向に回動する。その結果、走行クローラ２５が前下がりに傾斜して、後進移動する。
On the other hand, when the tractor 10 is caused to travel backward, by receiving a reverse reaction force from the ground, the track frame 17 moves rearward with respect to the traveling machine body 11, and the traveling crawler 25 is inclined to the forward lowering posture. That is, when the track frame 17 moves rearward with respect to the traveling machine body 11, the front link member 19 rises in the direction in which the inclination angle from the horizontal plane increases with the upper end pivot shaft 27 as a fulcrum. Rotate. Further, the rear link member 20 rotates in the direction in which the rear link member 20 is tilted so that the inclination angle from the horizontal plane becomes small with the upper end pivot shaft 28 as a fulcrum. As a result, the traveling crawler 25 tilts forward and moves backward.
なお、旋回内側の走行クローラ２５の駆動を中断して、左方向または右方向に旋回移動する場合、前進走行の際には旋回内側の走行クローラ２５が前下がりに傾斜し、後進走行の際には旋回内側の走行クローラ２５が前上がりに傾斜する。
When the driving of the traveling crawler 25 inside the turn is interrupted to turn left or right, the traveling crawler 25 inside the turning tilts forward and downward during forward traveling, and during backward traveling. The traveling crawler 25 on the inner side of the turn is inclined upward.
前上端枢着軸２７を支点とした前リンク部材１９の前方回動と、後上端枢着軸２８を支点とした後リンク部材２０の後方回動とをそれぞれ規制するストッパとしての前後の規制ピン３４，３４ａ，３５，３５ａをフランジ部材１８に設けている。前上端枢着軸２７を支点として前リンク部材１９（後リンク部材２０）の下端側が前方回動する範囲を前規制ピン３４（前規制ピン３４ａ）にて設定している。後上端枢着軸２８を支点として後リンク部材２０（前リンク部材１９）の下端側が後方回動する範囲を後規制ピン３５（後規制ピン３５ａ）にて設定している。走行機体１１に対する走行クローラ２５の前後移動が、前後の規制ピン３４，３４ａ，３５，３５ａにて制限されるように構成している。
Front and rear restricting pins as stoppers for restricting forward rotation of the front link member 19 with the front upper end pivot shaft 27 as a fulcrum and rear rotation of the rear link member 20 with the rear upper end pivot shaft 28 as a fulcrum. 34, 34 a, 35, 35 a are provided on the flange member 18. A range in which the lower end side of the front link member 19 (rear link member 20) rotates forward with the front upper end pivot shaft 27 as a fulcrum is set by the front restriction pin 34 (front restriction pin 34a). A range in which the lower end side of the rear link member 20 (front link member 19) rotates backward with the rear upper end pivot shaft 28 as a fulcrum is set by the rear restriction pin 35 (rear restriction pin 35a). The forward and backward movement of the traveling crawler 25 relative to the traveling machine body 11 is configured to be restricted by the front and rear restricting pins 34, 34a, 35, and 35a.
そして、前記走行機体１１の前部が下がるようにピッチング（前傾動作）した場合、前リンク部材１９は、前下端枢着軸３０を支点として水平面からの傾斜角度が小さくなるように倒れる方向に回動する。一方、後リンク部材２０は、前記トラックフレーム１７に対して、後下端枢着軸３１を支点として水平面からの傾斜角度が大きくなるように起立する方向に回動する。これにより、走行機体１１に対して、走行クローラ２５が前上がり姿勢に支持される。
And when it pitches so that the front part of the said traveling body 11 may fall (forward inclination operation | movement), the front link member 19 will be in the direction which falls so that the inclination angle from a horizontal surface may become small with the front-lower-end pivot shaft 30 as a fulcrum. Rotate. On the other hand, the rear link member 20 rotates with respect to the track frame 17 so as to stand up so that the inclination angle from the horizontal plane becomes larger with the rear lower end pivot shaft 31 as a fulcrum. Accordingly, the traveling crawler 25 is supported in a forwardly raised posture with respect to the traveling machine body 11.
また、前記走行機体１１の前部が上がるようにピッチング（後傾動作）した場合、前リンク部材１９は、前下端枢着軸３０を支点として水平面からの傾斜角度が大きくなるように起立する方向に回動する。一方、後リンク部材２０は、後下端枢着軸３１を支点として水平面からの傾斜角度が小さくなるように倒れる方向に回動する。これにより、走行機体１１に対して、走行クローラ２５が前下がり姿勢に支持される。
Further, when pitching (backward tilting operation) so that the front portion of the traveling machine body 11 is raised, the front link member 19 stands up so that the inclination angle from the horizontal plane becomes larger with the front lower end pivot shaft 30 as a fulcrum. To turn. On the other hand, the rear link member 20 rotates in the direction of falling so that the inclination angle from the horizontal plane becomes smaller with the rear lower end pivot shaft 31 as a fulcrum. As a result, the traveling crawler 25 is supported in the forwardly lowered posture with respect to the traveling machine body 11.
ところで、フランジ部材１８と、前リンク部材１９と、後リンク部材２０と、トラックフレーム１７とによって構成される四節リンク機構において、その一つの節である前記トラックフレーム１７がその長手方向に運動するときにおける「瞬間中心」は、前リンク部材１９の延長線と、後リンク部材２０の延長線とが互いに交わる交点に位置している。前記トラックフレーム１７は、この「瞬間中心」を中心としてその長手方向に運動する。
By the way, in the four-bar linkage mechanism constituted by the flange member 18, the front link member 19, the rear link member 20, and the track frame 17, the track frame 17, which is one of the nodes, moves in the longitudinal direction. The “instantaneous center” at that time is located at the intersection where the extension line of the front link member 19 and the extension line of the rear link member 20 cross each other. The track frame 17 moves in the longitudinal direction around the “instantaneous center”.
この場合、前記前後のリンク部材１９，２０は、下広がりのハ字状に配設されていることにより、前記瞬間中心は、前記走行機体１１が前下がりにピッチングしたときには、機体後方側に移動し、前記走行機体１１が前上がりにピッチングしたときには、機体前方側に移動することになり、前記後車軸１５の高さに近似した高さの位置に前記瞬間中心を保持することができる。これにより、前記走行機体１１がピッチングする際に、トラックフレーム１７に対して走行機体１１が前後移動する距離を、先行技術の前後移動距離に比べ、大幅に縮小できる。
In this case, the front and rear link members 19 and 20 are arranged in a downwardly widened C shape, so that the instantaneous center moves to the rear side of the aircraft when the traveling vehicle 11 is pitched forward and downward. When the traveling machine body 11 is pitched forwardly, it moves to the front side of the machine body, so that the instantaneous center can be held at a height that approximates the height of the rear axle 15. As a result, when the traveling machine body 11 pitches, the distance that the traveling machine body 11 moves back and forth with respect to the track frame 17 can be significantly reduced compared to the longitudinal movement distance of the prior art.
さらに、図１、図２に示す如く、ロータリ耕耘爪２を有するロータリ耕耘作業機１を備える。前記走行機体１１の後部から後方側にロワーリンク３及びトップリンク４（三点リンク機構）を突出し、ロワーリンク３及びトップリンク４にロータリ耕耘作業機１を装着する。前記走行機体１１の後部（ミッションケース４０上部）に油圧リフト機構５を設ける。油圧リフト機構５のリフトアーム６にリフトロッド７を介してロワーリンク３の前後中間部を連結する。油圧リフト機構５の操作にてロータリ耕耘作業機１を昇降動させる一方、ロータリ耕耘爪２にて圃場の耕土を耕耘するように構成している。なお、ロータリ耕耘作業機１に代えて、各種作業機をトラクタ１０に装着できることは云うまでもない。
Further, as shown in FIGS. 1 and 2, a rotary tiller working machine 1 having a rotary tiller 2 is provided. The lower link 3 and the top link 4 (three-point link mechanism) protrude from the rear part of the traveling machine body 11 to the rear side, and the rotary tiller 1 is mounted on the lower link 3 and the top link 4. A hydraulic lift mechanism 5 is provided at the rear part of the traveling machine body 11 (upper part of the transmission case 40). A front and rear intermediate portion of the lower link 3 is connected to a lift arm 6 of the hydraulic lift mechanism 5 via a lift rod 7. While the rotary tiller 1 is moved up and down by operation of the hydraulic lift mechanism 5, the rotary tillage claws 2 are used to cultivate the soil in the field. Needless to say, various working machines can be attached to the tractor 10 instead of the rotary tilling work machine 1.
次いで、図５〜図１０を参照して、前記トラックフレーム１７、リンク部材１９，２０、フランジ部材１８の取付け構造を説明する。図８〜図１０に示す如く、フランジ部材１８は、鋼板製で平板形状の第１ブラケット体５１と、鋼板製で平板形状の第２ブラケット体５２と、鋼板製で平板形状の前後の第３ブラケット体５３，５４と、鋼板製で平板形状の前後中の横桟形ブラケット体５５，５６，５７を有する。第１ブラケット体５１と第２ブラケット体５２は、同一形状に形成する。前後の第３ブラケット体５３，５４に前後の横桟形ブラケット体５５，５６をそれぞれ溶接固定している。
Next, with reference to FIGS. 5 to 10, the mounting structure of the track frame 17, the link members 19 and 20, and the flange member 18 will be described. As shown in FIGS. 8 to 10, the flange member 18 is made of a steel plate and a flat plate-shaped first bracket body 51, a steel plate and a flat plate-shaped second bracket body 52, and a steel plate and a flat plate-shaped third bracket before and after the flat plate shape. There are bracket bodies 53, 54, and horizontal rail-shaped bracket bodies 55, 56, 57 in the front and rear of a flat plate shape made of a steel plate. The first bracket body 51 and the second bracket body 52 are formed in the same shape. The front and rear horizontal rail bracket bodies 55 and 56 are fixed to the front and rear third bracket bodies 53 and 54 by welding.
そして、大径側の前後２本の規制ピン３４，３５の一端側を、第１ブラケット体５１と第２ブラケット体５２に片持ち状にボルト６１締結する。第１ブラケット体５１と第２ブラケット体５２の対向する面に、各規制ピン３４，３５の他端側を突出させる。さらに、前後中の横桟形ブラケット体５５，５６，５７の両端面を、第１ブラケット体５１と第２ブラケット体５２に両持ち状にボルト６２締結する。また、小径側の前後２本の規制ピン３４ａ，３５ａの両端ネジ部を、第１ブラケット体５１と第２ブラケット体５２に両持ち状にナット６３締結する。
Then, bolts 61 are fastened to the first bracket body 51 and the second bracket body 52 in a cantilever manner at one end side of the two front and rear restriction pins 34 and 35 on the large diameter side. The other end sides of the restricting pins 34 and 35 are projected from the opposing surfaces of the first bracket body 51 and the second bracket body 52. Furthermore, the bolts 62 are fastened to the first bracket body 51 and the second bracket body 52 in the form of both ends at both end surfaces of the front and rear horizontal cross-bar bracket bodies 55, 56, 57. Also, the nuts 63 are fastened to the first bracket body 51 and the second bracket body 52 in the form of both ends with the screw portions at both ends of the two front and rear restricting pins 34a and 35a on the small diameter side.
また、前後のリンク部材１９，２０の上端側ボス部に前後の上端枢着軸２７，２８を貫通させた状態で、前後の上端枢着軸２７，２８の両端部を、第１ブラケット体５１と第２ブラケット体５２に軸押え板体６４を介して両持ち状にボルト６５締結する。なお、軸押え板体６４をナット６３締結し、軸押え板体６４の軸心回りの回動を防止している。
In addition, the front and rear upper end pivot shafts 27 and 28 are passed through the upper end boss portions of the front and rear link members 19 and 20, and both end portions of the front and rear upper pivot shafts 27 and 28 are connected to the first bracket body 51. And the bolt 65 is fastened to the 2nd bracket body 52 via the shaft pressing plate body 64 in the both-ends form. The shaft retainer plate 64 is fastened with a nut 63 to prevent the shaft retainer plate 64 from rotating about its axis.
一方、前記第１ブラケット体５１に座板体６６を溶接固定する。第１ブラケット体５１と座板体６６を、後車軸ケース１４にそれぞれボルト６７，６８締結する。また、後車軸ケース１４に前後の第３ブラケット体５３，５４をそれぞれボルト６９，７０締結する。第１ブラケット体５１と、第３ブラケット体５３，５４の間に、後車軸ケース１４を挟持状に着脱可能に固着させる。組立作業において、第１ブラケット体５１に第２ブラケット体５２を固着して、フランジ部材１８に前後のリンク部材１９，２０を設けた状態にユニット構成する。その後、後車軸ケース１４の底面側に、ユニット構造のフランジ部材１８を、後車軸ケース１４の下方側から当接させて、第１ブラケット体５１と座板体６６と第３ブラケット体５３，５４をボルト６７，６８，６９，７０締結し、後車軸ケース１４にフランジ部材１８を介して前後のリンク部材１９，２０を組付けるように構成している。
Meanwhile, the seat plate body 66 is fixed to the first bracket body 51 by welding. The first bracket body 51 and the seat plate body 66 are fastened to the rear axle case 14 with bolts 67 and 68, respectively. Further, the front and rear third bracket bodies 53 and 54 are fastened to the rear axle case 14 with bolts 69 and 70, respectively. The rear axle case 14 is detachably fixed between the first bracket body 51 and the third bracket bodies 53 and 54 in a sandwiched manner. In the assembling operation, the second bracket body 52 is fixed to the first bracket body 51 and the front and rear link members 19 and 20 are provided on the flange member 18 to constitute a unit. After that, the flange member 18 of the unit structure is brought into contact with the bottom surface side of the rear axle case 14 from the lower side of the rear axle case 14, and the first bracket body 51, the seat plate body 66, and the third bracket bodies 53 and 54. The bolts 67, 68, 69, 70 are fastened, and the front and rear link members 19, 20 are assembled to the rear axle case 14 via the flange member 18.
さらに、前記座板体６６に振れ止めブラケット体４４を溶接固定する。耕耘作業機１（左右のロワーリンク３）が、左右方向に多少の揺動を許容した状態で、必要以上に左右に揺動しないように、スタビライザとしての左右のターンバックル式チェックチェン体４５を設ける。ロワーリンク３の前後幅中間にチェックチェン体４５の一端側をピン４６連結し、振れ止めブラケット体４４にチェックチェン体４５の他端側を着脱可能にピン４７連結している。
Further, the steady bracket body 44 is fixed to the seat plate body 66 by welding. The left and right turnbuckle check chain body 45 as a stabilizer is mounted so that the tilling work machine 1 (left and right lower links 3) does not swing to the left and right more than necessary in a state where the swinging work machine 1 allows a slight swing in the left and right direction. Provide. One end side of the check chain body 45 is connected to the middle of the front and rear width of the lower link 3, and the other end side of the check chain body 45 is detachably connected to the steady bracket body 44.
次いで、図４、図９〜図１３を参照して、前記トラックフレーム１７とリンク部材１９，２０の連結構造を説明する。図１１、図１２に示す如く、前記下端枢着軸３０，３１の一端側の機体内側軸部７６は、前記リンク部材１９，２０の下端側ボス部にすべり軸受メタル７１，７２を介して回動可能に軸支する。前記リンク部材１９，２０の下端側ボス部から機体外側方に向けて突出させる前記下端枢着軸３０，３１の他端側（機体外側）に、大径軸部７３と、先細り形状のテ―パ部７４と、小径軸部７５を設ける。大径軸部７３にテ―パ部７４を介して小径軸部７５が連接される。前記下端枢着軸３０，３１の他端側の端面にボルト孔８２を開設する。なお、大径軸部７３の外径に比べ、機体内側軸部７６の外径を大きく形成している。
Next, referring to FIGS. 4 and 9 to 13, a connection structure between the track frame 17 and the link members 19 and 20 will be described. As shown in FIGS. 11 and 12, the body inner shaft portion 76 on one end side of the lower pivot shafts 30 and 31 is rotated on the lower boss portion of the link members 19 and 20 via slide bearing metals 71 and 72. It is pivotally supported. A large-diameter shaft portion 73 and a taper-shaped tape are formed on the other end side (outside the fuselage) of the lower pivot shafts 30 and 31 that protrude from the lower boss side of the link members 19 and 20 toward the outer side of the fuselage. A pad portion 74 and a small diameter shaft portion 75 are provided. A small-diameter shaft portion 75 is connected to the large-diameter shaft portion 73 via a taper portion 74. A bolt hole 82 is formed in the end face on the other end side of the lower end pivot shafts 30 and 31. In addition, the outer diameter of the body inner shaft portion 76 is formed larger than the outer diameter of the large diameter shaft portion 73.
図１１、図１２に示す如く、前後方向に長尺な四角柱状のトラックフレーム１７の上面に軸受筒体７７を溶接固定している。前記下端枢着軸３０，３１の大径軸部７３を内挿する大径孔７８と、下端枢着軸３０，３１の小径軸部７５を内挿する小径孔７９と、小径孔７９に大径孔７８を連通するテ―パ孔８０によって軸受筒体７７の軸孔８１を形成する。そして、前記下端枢着軸３０，３１の他端側（機体外側）に、スラストワッシャ８２を被嵌させ、軸受筒体７７を被嵌させるように構成している。
As shown in FIGS. 11 and 12, a bearing cylinder 77 is welded and fixed to the upper surface of a square columnar track frame 17 elongated in the front-rear direction. The large diameter hole 78 for inserting the large diameter shaft portion 73 of the lower end pivot shafts 30 and 31, the small diameter hole 79 for inserting the small diameter shaft portion 75 of the lower end pivot shafts 30 and 31, and the small diameter hole 79 are large. A shaft hole 81 of the bearing cylinder 77 is formed by a taper hole 80 communicating with the diameter hole 78. A thrust washer 82 is fitted on the other end side (outside the machine body) of the lower pivot shafts 30 and 31, and a bearing cylinder 77 is fitted.
上記の構成により、大径孔７８側から軸孔８１内に、小径軸部７５を先頭にして、リンク部材１９，２０の下端側ボス部から突出した下端枢着軸３０，３１の他端側を挿入させる。小径孔７９側の軸受筒体７７端面に軸押え板体６４を当接させ、小径孔７９内にボルト６５の先端を挿入し、下端枢着軸３０，３１端面のボルト孔８２にボルト６５を螺着し、小径孔７９内に小径軸部７５を圧入し、大径孔７８内に大径軸部７３を圧入し、トラックフレーム１７上面の軸受筒体７７に下端枢着軸３０，３１の他端側を固着する。
With the above configuration, the other end side of the lower pivot shafts 30 and 31 projecting from the lower boss portions of the link members 19 and 20 with the small diameter shaft portion 75 as the head in the shaft hole 81 from the large diameter hole 78 side. To insert. The shaft retainer plate 64 is brought into contact with the end surface of the bearing cylinder 77 on the side of the small diameter hole 79, the tip of the bolt 65 is inserted into the small diameter hole 79, and the bolt 65 is inserted into the bolt hole 82 on the end surfaces of the lower pivot shafts 31 and 31. The small-diameter shaft portion 75 is press-fitted into the small-diameter hole 79, the large-diameter shaft portion 73 is press-fitted into the large-diameter hole 78, and the lower pivot shafts 30, 31 are inserted into the bearing cylinder 77 on the top surface of the track frame 17. Secure the other end.
図１、図４、図９〜図１３に示す如く、エンジン８を搭載する走行機体１１と、走行機体１１の前部下側に設ける左右の前車輪１２と、走行機体１１の後部下側に設けるトラックフレーム１７と、トラックフレーム１７に装着する左右の走行クローラ２５とを備え、走行クローラ２５に回転力を伝達する後車軸１５と、走行機体１１にトラックフレーム１７を揺動可能に支持する揺動支点軸としての前後の上端枢着軸２７，２８とを、離間させて設ける作業車両において、後車軸１５が軸支されるアクスルケースとしての後車軸ケース１４の直下に前後の上端枢着軸２７，２８を配置し、前後の上端枢着軸２７，２８に設ける前リンク部材１９及び後リンク部材２０を介して、後車軸ケース１４にトラックフレーム１７を連結している。したがって、例えば、前進移動時、または後進移動時、圃場の畔などの凸部を乗越える場合、前後の上端枢着軸２７，２８を中心として走行クローラ２５が前上がりまたは前下りに傾斜しても、走行クローラ２５の接地面の前後方向の傾斜角度が従来よりも小さくなる。即ち、走行機体１１の対地高さが従来よりも変化しにくく、操縦座席９に搭乗したオペレータの乗り心地を良好な状態に維持できる。
As shown in FIGS. 1, 4, and 9 to 13, a traveling machine body 11 on which the engine 8 is mounted, left and right front wheels 12 that are provided below the front part of the traveling machine body 11, and a lower rear part of the traveling machine body 11. A track frame 17 and left and right traveling crawlers 25 attached to the track frame 17, a rear axle 15 that transmits rotational force to the traveling crawler 25, and a swing that supports the track frame 17 on the traveling body 11 so as to be swingable. In a working vehicle in which the front and rear upper pivot shafts 27 and 28 as fulcrum shafts are provided apart from each other, the front and rear upper pivot shafts 27 are directly below the rear axle case 14 as an axle case on which the rear axle 15 is pivotally supported. , 28, and the track frame 17 is connected to the rear axle case 14 via the front link member 19 and the rear link member 20 provided on the front and rear upper pivot shafts 27, 28. Therefore, for example, when moving forward or backward, when traveling over a convex portion such as a farm shore, the traveling crawler 25 tilts forward or downward with the front and rear upper pivot shafts 27 and 28 as the center. However, the inclination angle in the front-rear direction of the ground contact surface of the traveling crawler 25 is smaller than that of the conventional art. That is, the ground height of the traveling machine body 11 is less likely to change than before, and the ride comfort of the operator who has boarded the control seat 9 can be maintained in a good state.
図４、図９〜図１３に示す如く、前後の上端枢着軸２７，２８と前後の下端枢着軸３０，３１とによって揺動支点軸を形成し、後車軸ケース１４に前後の上端枢着軸２７，２８を設け、トラックフレーム１７に前後の下端枢着軸３０，３１を設け、前記各枢着軸２７，２８，３０，３１に前後のリンク部材１９，２０の上下端部をそれぞれ連結している。したがって、トラックフレーム１７の走行機体１１への支持荷重が大きくても、前後の上端枢着軸２７，２８及び前後の下端枢着軸３０，３１のそれぞれの支持荷重を低減でき、作業車両の大型化を簡単に達成できる。また、前記各枢着軸２７，２８，３０，３１部の変形等による作動不良の発生などを低減でき、耐荷重または耐久性なども向上できる。
As shown in FIGS. 4 and 9 to 13, the front and rear upper pivot shafts 27 and 28 and the front and lower lower pivot shafts 30 and 31 form a swing fulcrum shaft, and the rear axle case 14 has the front and rear upper pivots. Attaching shafts 27, 28 are provided, front and rear lower pivot shafts 30, 31 are provided on the track frame 17, and upper and lower end portions of the front and rear link members 19, 20 are provided on the pivot shafts 27, 28, 30, 31, respectively. It is connected. Therefore, even if the support load to the traveling machine body 11 of the track frame 17 is large, the support loads on the front and rear upper pivot shafts 27 and 28 and the front and lower lower pivot shafts 30 and 31 can be reduced. Can be easily achieved. Further, it is possible to reduce the occurrence of malfunction due to deformation of the pivot shafts 27, 28, 30, 31 and the like, and to improve the load resistance or durability.
図９〜図１３に示す如く、後車軸ケース１４の機内側面と機外側面に、機内側支点体としての第１ブラケット体５１と機外側支点体としての第２ブラケット体５２を設け、第１ブラケット体５１と第２ブラケット体５２の間に前後の上端枢着軸２７，２８をそれぞれ挟持させ、走行機体１１に耕耘作業機１を支持するためのリンク機構としてのロワーリンク３の構成部品（チェックチェン体４５）よりも機外側方に、前後の上端枢着軸２７，２８または前後のリンク部材１９，２０をそれぞれ配置している。したがって、後上端枢着軸２７，２８または後リンク部材１９，２０にて制限されることなく、ロワーリンク３を昇降動できるものでありながら、上端枢着軸２７，２８の支持剛性を簡単に向上できる。また、上端枢着軸２７，２８の支持構造を簡略化でき、製造コストを低減できる。
As shown in FIGS. 9 to 13, a first bracket body 51 as an inboard fulcrum body and a second bracket body 52 as an outboard fulcrum body are provided on the inboard side surface and the outboard side surface of the rear axle case 14. Components of the lower link 3 as a link mechanism for supporting the tilling work machine 1 on the traveling machine body 11 by sandwiching the front and rear upper pivot shafts 27 and 28 between the bracket body 51 and the second bracket body 52 ( The front and rear upper pivot shafts 27 and 28 or the front and rear link members 19 and 20 are arranged on the outer side of the check chain body 45). Therefore, the lower link 3 can be moved up and down without being limited by the rear upper pivot shafts 27 and 28 or the rear link members 19 and 20, and the support rigidity of the upper pivot shafts 27 and 28 can be easily achieved. Can be improved. Further, the support structure for the upper pivot shafts 27 and 28 can be simplified, and the manufacturing cost can be reduced.
図１０に示す如く、走行クローラ２５の左右幅内でトラックフレーム１７に前後の下端枢着軸３０，３１を設け、トラックフレーム１７側に前後のリンク部材１９，２０の下端側をそれぞれオフセットさせるように構成している。したがって、走行クローラ２５の左右幅から下端枢着軸３０，３１またはリンク部材１９，２０を殆ど突出させることがなく、下端枢着軸３０，３１またはリンク部材１９，２０を設置できる。したがって、例えばトラクタ１０の畝跨ぎ作業における畝Ｇまたは背の高い作物から離間させて、前後の下端枢着軸３０，３１または前後のリンク部材１９，２０を支持でき、畝Ｇまたは背の高い作物などに対して十分なスペースを確保できる。
As shown in FIG. 10, the front and rear lower pivot shafts 30 and 31 are provided on the track frame 17 within the lateral width of the traveling crawler 25, and the lower ends of the front and rear link members 19 and 20 are offset to the track frame 17 side. It is configured. Therefore, the lower end pivoting shafts 30 and 31 or the link members 19 and 20 can be installed without substantially projecting the lower end pivotal shafts 30 and 31 or the link members 19 and 20 from the left and right widths of the traveling crawler 25. Therefore, for example, the front and rear lower pivot shafts 30 and 31 or the front and rear link members 19 and 20 can be supported while being separated from the heel G or the tall crop in the tractor 10 crossing ridge, and the heel G or the tall crop is supported. Sufficient space can be secured.
図１、図４、図１１に示す如く、エンジン８を搭載する走行機体１１と、走行機体１１の前部下側に設ける左右の前車輪１２と、走行機体１１の後部下側に設けるトラックフレーム１７と、トラックフレーム１７に装着する左右の走行クローラ２５と、走行クローラ２５に回転力を伝達する後車軸１５と、トラックフレーム１７に設ける複数の転動輪２６とを備え、複数の転動輪２６を介して走行クローラ２５の接地側を支持する作業車両において、後車軸１５の直下に設ける２本の上の枢着軸としての前上端枢着軸２７及び後上端枢着軸２８と、トラックフレーム１７に設ける２本の下の枢着軸としての前下端枢着軸３０及び後下端枢着軸３１の間に２本のリンク部材１９，２０を連結し、後車軸１５の前方と後方に２本の上の前上端枢着軸２７及び後上端枢着軸２８を振分けて配置し、トラックフレーム１７上面側のうち複数の転動輪２６の間の上面側に２本の下の前下端枢着軸３０及び後下端枢着軸３１の一方を配置している。したがって、複数の転動輪２６の間に設ける前下端枢着軸３０の支持高さを低くできる。上下の前上端枢着軸２７及び前下端枢着軸３０の軸受構造を低コスト化または軽量化できるものでありながら、走行クローラ２５の接地反力に対して、前下端枢着軸３０の軸受構造を強度的に有利に構成できる。また、前リンク部材１９のボス体長さを簡単に確保でき、汎用性の高いブッシュを使用して、前下端枢着軸３０に前リンク部材１９のボス体を軸支できる。
As shown in FIGS. 1, 4, and 11, a traveling machine body 11 on which the engine 8 is mounted, left and right front wheels 12 provided on the lower front side of the traveling machine body 11, and a track frame 17 provided on the lower rear side of the traveling machine body 11. The left and right traveling crawlers 25 attached to the track frame 17, the rear axle 15 for transmitting the rotational force to the traveling crawler 25, and a plurality of rolling wheels 26 provided on the track frame 17, via the plurality of rolling wheels 26. In the work vehicle that supports the grounding side of the traveling crawler 25, the front upper end pivot shaft 27 and the rear upper end pivot shaft 28 as the two upper pivot shafts provided immediately below the rear axle 15, and the track frame 17 Two link members 19 and 20 are connected between a front lower pivot shaft 30 and a rear lower pivot shaft 31 as two lower pivot shafts provided, and two link members 19 and 20 are connected to the front and rear of the rear axle 15. Top front upper pivot 27 and the rear upper end pivot shaft 28 are arranged in a distributed manner, and two lower front pivot shafts 30 and rear lower pivot shafts 31 are disposed on the upper surface side between the plurality of rolling wheels 26 on the upper surface side of the track frame 17. One of the is arranged. Therefore, the support height of the front lower end pivot shaft 30 provided between the plurality of rolling wheels 26 can be lowered. While the bearing structure of the upper and lower front upper pivot shafts 27 and the front lower pivot shaft 30 can be reduced in cost or weight, the bearing of the front lower pivot shaft 30 against the ground reaction force of the traveling crawler 25. The structure can be advantageously constructed in terms of strength. Further, the boss body length of the front link member 19 can be easily secured, and the boss body of the front link member 19 can be pivotally supported on the front lower end pivot shaft 30 by using a highly versatile bush.
図４、図１１に示す如く、トラックフレーム１７に後従動輪体２３を介して走行クローラ２５の後部接地側を支持する構造であって、後従動輪体２３に隣接する転動輪２６と後従動輪体２３の間で、トラックフレーム１７上面側に２本の前下端枢着軸３０及び後下端枢着軸３１の他方を配置している。したがって、後従動輪体２３に隣接する転動輪２６と後従動輪体２３の間に設ける後下端枢着軸３１の支持高さを低くできる。走行クローラ２５の接地反力に対して、後下端枢着軸３１の軸受構造を強度的に有利に構成できる。また、後リンク部材２０のボス体長さを簡単に確保でき、汎用性の高いブッシュを使用して、後下端枢着軸３１に後リンク部材２０のボス体を軸支できる。
As shown in FIGS. 4 and 11, the track frame 17 supports the rear grounding side of the traveling crawler 25 via the rear driven wheel body 23, and includes the rolling wheel 26 adjacent to the rear driven wheel body 23 and the rear driven wheel body 23. Between the moving wheel bodies 23, the other of the two front lower pivot shafts 30 and the rear lower pivot shaft 31 is disposed on the upper surface side of the track frame 17. Therefore, the support height of the rear lower end pivot shaft 31 provided between the rolling wheel 26 adjacent to the rear driven wheel body 23 and the rear driven wheel body 23 can be reduced. With respect to the ground reaction force of the traveling crawler 25, the bearing structure of the rear lower end pivot shaft 31 can be advantageously configured in terms of strength. Further, the boss body length of the rear link member 20 can be easily secured, and the boss body of the rear link member 20 can be pivotally supported on the rear lower end pivot shaft 31 by using a versatile bush.
図４に示す如く、前記２本のリンク部材１９，２０を機体側面視でハの字状に配置し、２本のリンク部材１９，２０の上端側の間隔よりも、２本のリンク部材１９，２０の下端側の間隔が大きくなるように構成している。したがって、従来の単一支点構造に比べ、走行クローラ２５から走行機体１１側に向けて突出させる前記２本のリンク部材１９，２０の出代を少なくすることができ、前記２本のリンク１９，２０部材が揺動するときに、２本のリンク部材１９，２０に付着した泥土が周辺の構成部品に干渉する等の不具合の発生を容易に低減できる。
As shown in FIG. 4, the two link members 19 and 20 are arranged in a letter C shape in a side view of the body, and the two link members 19 are more than the distance between the upper ends of the two link members 19 and 20. , 20 is configured such that the distance between the lower end sides thereof is increased. Therefore, compared with the conventional single fulcrum structure, the allowance of the two link members 19 and 20 projected from the traveling crawler 25 toward the traveling machine body 11 can be reduced. When the 20 member swings, it is possible to easily reduce the occurrence of problems such as the mud adhering to the two link members 19 and 20 interfering with surrounding components.
図４、図１１に示す如く、走行クローラ２５の前進側の駆動合力線Ｘの近傍に前上端枢着軸２７及び後上端枢着軸２８を配置し、機体前側の前上端枢着軸２７を前記駆動合力線Ｘよりも下方に配置し、トラックフレーム１７の揺動軌跡の中心Ｙが前記駆動合力線Ｘよりも下方になるように構成している。したがって、走行クローラ２５の前進側の駆動力に対して容易に変位しないようにリンク部材１９，２０を支持でき、転動反力に抗して前記走行クローラ２５を路面に追従させることができ、発進または停止に際して走行機体１１の前後傾動を低減でき、安定した姿勢で走行機体１１を移動できる。
As shown in FIGS. 4 and 11, a front upper end pivot shaft 27 and a rear upper pivot shaft 28 are arranged in the vicinity of the driving resultant force line X on the forward side of the traveling crawler 25, and the front upper pivot shaft 27 on the front side of the machine body is disposed. It is arranged below the driving resultant line X so that the center Y of the swing locus of the track frame 17 is below the driving resultant line X. Therefore, the link members 19 and 20 can be supported so as not to be easily displaced with respect to the driving force on the forward side of the traveling crawler 25, and the traveling crawler 25 can follow the road surface against the rolling reaction force. When starting or stopping, the traveling machine body 11 can be prevented from tilting back and forth, and the traveling machine body 11 can be moved in a stable posture.
図１１、図１２に示す如く、２段の段付き軸形状に前下端枢着軸３０及び後下端枢着軸３１を形成し、前記トラックフレーム１７に設ける下軸受体としての軸受筒体７７に、ボルト６５の締結にて前下端枢着軸３０及び後下端枢着軸３１の２段の段付き軸部（下端枢着軸の大径軸部７３、下端枢着軸の小径軸部７５）を圧入させるように構成している。したがって、前下端枢着軸３０及び後下端枢着軸３１の先端側を先細りに形成して、当該先細り部のガイド作用にて前下端枢着軸３０及び後下端枢着軸３１の組付け作業性を向上できる。例えば、打込みまたはプレス等によって前下端枢着軸３０及び後下端枢着軸３１を組込む必要がない。また、前記リンク部材１９，２０のボス体内孔に前下端枢着軸３０及び後下端枢着軸３１の２段の段部をそれぞれ圧着させて、前下端枢着軸３０及び後下端枢着軸３１の軸強度を維持できる。
As shown in FIGS. 11 and 12, a front lower end pivot shaft 30 and a rear lower pivot shaft 31 are formed in a two-stage stepped shaft shape, and a bearing cylinder 77 as a lower bearing body provided in the track frame 17 is formed. The bolt 65 is fastened, so that the front lower end pivot shaft 30 and the rear lower pivot shaft 31 have two stepped shaft portions (a large diameter shaft portion 73 of the lower end pivot shaft and a small diameter shaft portion 75 of the lower end pivot shaft). Are configured to be press-fitted. Therefore, the front lower end pivot shaft 30 and the rear lower pivot shaft 31 are tapered and the front lower pivot shaft 30 and the rear lower pivot shaft 31 are assembled by the guide action of the tapered portion. Can be improved. For example, it is not necessary to incorporate the front lower end pivot shaft 30 and the rear lower pivot shaft 31 by driving or pressing. In addition, two steps of a front lower end pivot shaft 30 and a rear lower pivot shaft 31 are respectively crimped to the boss body holes of the link members 19, 20, so that the front lower pivot shaft 30 and the rear lower pivot shaft are mounted. The axial strength of 31 can be maintained.
次いで、図１４〜図１９を参照して、前記トラックフレーム１７とリンク部材１９，２０の連結構造を説明する。図１４〜図１７に示す如く、後車軸ケース１４から外向きに突出させた後車軸１５端部の円板状取付け部１５ａにドーナツ形状の板金製リム体８６の内孔縁側をボルト８７締結する。リム体８６の外周縁側にドーナツ形状の駆動輪体１６の内孔縁側をボルト８８締結する。駆動輪体１６は、輪状のスプロケット歯底部８９と、スプロケット歯底部８９の両側から放射線方向に突出させる二股状の一対のスプロケット歯体９０とを有する。プーリ輪部８９の全域に複数組のスプロケット歯体９０を等間隔に設けている。即ち、駆動輪体１６の全外周面にスプロケット歯底部８９が無端状に形成される一方、スプロケット歯底部８９の両側縁から二股状の一対のスプロケット歯体９０が外向き放射状に突出し、駆動輪体１６の全外周面に複数組のスプロケット歯体９０が等間隔に配置される。
Next, a connection structure between the track frame 17 and the link members 19 and 20 will be described with reference to FIGS. As shown in FIGS. 14 to 17, the bolt 87 is fastened to the inner hole edge side of the donut-shaped sheet metal rim body 86 on the disc-like mounting portion 15 a at the end of the rear axle 15 that protrudes outward from the rear axle case 14. . Bolts 88 are fastened to the inner hole edge side of the donut-shaped drive wheel body 16 on the outer peripheral edge side of the rim body 86. The drive wheel body 16 has a ring-shaped sprocket tooth bottom 89 and a pair of bifurcated sprocket teeth 90 that protrude in the radial direction from both sides of the sprocket tooth bottom 89. A plurality of sets of sprocket tooth bodies 90 are provided at equal intervals throughout the pulley ring portion 89. That is, the sprocket tooth bottom 89 is formed endlessly on the entire outer peripheral surface of the drive wheel body 16, while a pair of bifurcated sprocket teeth 90 project radially outward from both side edges of the sprocket tooth bottom 89, and the drive wheel A plurality of sets of sprocket tooth bodies 90 are arranged at equal intervals on the entire outer peripheral surface of the body 16.
また、ドーナツ形状の鉄合金製駆動輪体１６は、４体の部分輪体１６ａに分割して形成する。同一円周の４分の１の大きさに１体の部分輪体１６ａの大きさを形成している。放射線方向の端面１６ｂを付き合わせて４体の部分輪体１６ａを輪形に結合し、４体の部分輪体１６ａを同一円周に配置し、駆動輪体１６を形成する。リム体８６に対して４体の部分輪体１６ａを独立的に着脱し、４体の部分輪体１６ａのいずれか１つを交換可能に構成している。即ち、組立作業などにおいて、４体の部分輪体１６ａを独立して扱えるから、単一部品（１体の部分輪体１６ａ）を軽量化して簡単に持ち運んで組付けることができる。
Further, the donut-shaped iron alloy drive wheel body 16 is formed by being divided into four partial wheel bodies 16a. The size of one partial ring body 16a is formed to a size of a quarter of the same circumference. The end surfaces 16b in the radiation direction are attached to each other, and the four partial ring bodies 16a are coupled in a ring shape, and the four partial ring bodies 16a are arranged on the same circumference to form the drive wheel body 16. The four partial ring bodies 16a are independently attached to and detached from the rim body 86, and any one of the four partial ring bodies 16a is configured to be replaceable. That is, since the four partial ring bodies 16a can be handled independently in an assembly operation or the like, the single component (one partial ring body 16a) can be reduced in weight and easily carried and assembled.
さらに、図１５、図１８に示す如く、無端帯状の走行クローラ２５は、外周面側に多数のラグ２５ａを形成した合成ゴム製クローラ本体９４と、クローラ本体９４に等間隔に埋設した複数の芯金体９５とからなる。芯金体９５は、スプロケット歯体９０を歯合させる一対の芯金爪部９５ａと、各芯金爪部９５ａを連結する芯金胴部９５ｂと、芯金胴部９５ｂの両端側から左右方向に延長させる左右の翼片部９５ｃとを有する。クローラ本体９４の内周面側の全域に複数組の芯金爪部９５ａを等間隔に突設している。なお、クローラ本体９４の構成材料である合成ゴムにて、芯金体９５の全体（芯金爪部９５ａを含む）が被覆されている。
15 and 18, the endless belt-like traveling crawler 25 includes a synthetic rubber crawler body 94 having a large number of lugs 25a formed on the outer peripheral surface side, and a plurality of cores embedded in the crawler body 94 at equal intervals. It consists of a metal body 95. The core metal body 95 includes a pair of core metal claw portions 95a that mesh the sprocket tooth bodies 90, a core metal barrel portion 95b that connects the core metal claw portions 95a, and a left-right direction from both ends of the core metal barrel portion 95b. Left and right wing pieces 95c. A plurality of sets of cored bar claws 95a are projected at equal intervals across the entire inner peripheral surface of the crawler body 94. Note that the entire core metal body 95 (including the core metal claw portion 95a) is covered with a synthetic rubber which is a constituent material of the crawler body 94.
また、クローラ本体９４の内周面のうち、無端帯の延長方向に隣接する各芯金爪部９５ａ間の内周面に、平ベルト状接触凸部９４ａを一体的に形成する。クローラ本体９４の内周面側の全域に複数の接触凸部９４ａを等間隔に突設する。なお、各接触凸部９４ａの間に、それらを連結する内周凸面部９４ｂが形成されている。走行クローラ２５の内周側に突出させる接触凸部９４ａの高さよりも、内周凸面部９４ｂの高さを低く形成する。一対の芯金爪部９５ａの内側面と接触凸部９４ａまたは内周凸面部９４ｂとの当接にて、走行クローラ２５の横ずれを防止できる。また、内周凸面部９４ｂの連結にて、走行クローラ２５内周面のゴム層を層厚に形成でき、接触凸部９４ａが補強され、走行クローラ２５内周側（接触凸部９４ａなどのゴム層）が剥離するのを防止できる。
Further, a flat belt-like contact convex portion 94a is integrally formed on the inner peripheral surface of the crawler body 94 between the cored bar claws 95a adjacent to each other in the extending direction of the endless belt. A plurality of contact protrusions 94a are provided at equal intervals over the entire inner peripheral surface of the crawler body 94. In addition, between each contact convex part 94a, the inner peripheral convex surface part 94b which connects them is formed. The height of the inner peripheral convex surface portion 94b is formed to be lower than the height of the contact convex portion 94a that protrudes toward the inner peripheral side of the traveling crawler 25. The lateral displacement of the traveling crawler 25 can be prevented by the contact between the inner side surface of the pair of cored bar claws 95a and the contact convex portion 94a or the inner peripheral convex portion 94b. Further, by connecting the inner peripheral convex surface portion 94b, the rubber layer on the inner peripheral surface of the traveling crawler 25 can be formed with a layer thickness, the contact convex portion 94a is reinforced, and the inner peripheral side of the traveling crawler 25 (rubber such as the contact convex portion 94a). Layer) can be prevented from peeling off.
即ち、図１５に示す如く、駆動輪体１６に走行クローラ２５を巻装した場合、プーリ形状に形成したスプロケット歯底部８９に接触凸部９４ａがゴム接触にて圧接され、スプロケット歯底部８９と接触凸部９４ａ間の摩擦にて、駆動輪体１６の低トルク回転力が走行クローラ２５側に伝達される。前記ゴム接触にて駆動騒音を低減できる。また、無端帯の延長方向に隣接する各芯金爪部９５ａ間にスプロケット歯体９０が嵌り込み、スプロケット歯体９０が芯金爪部９５ａに金属接触にて当接し、スプロケット歯体９０と芯金爪部９５ａの噛み合いにて、駆動輪体１６の高トルク回転力が走行クローラ２５側に伝達される。前記金属接触にて駆動損失を低減でき、かつ歯とび（空転）等の発生を防止できる。
That is, as shown in FIG. 15, when the traveling crawler 25 is wound around the driving wheel body 16, the contact convex portion 94 a is pressed by rubber contact with the sprocket tooth bottom 89 formed in a pulley shape, and is in contact with the sprocket tooth bottom 89. The low torque torque of the drive wheel body 16 is transmitted to the traveling crawler 25 side by friction between the convex portions 94a. Driving noise can be reduced by the rubber contact. Further, the sprocket tooth body 90 is fitted between the core metal claws 95a adjacent to each other in the extending direction of the endless belt, and the sprocket tooth body 90 is brought into contact with the metal core claws 95a by metal contact. The high torque rotational force of the driving wheel body 16 is transmitted to the traveling crawler 25 side by the engagement of the gold pawl portion 95a. Driving loss can be reduced by the metal contact, and occurrence of tooth jumping (idling) can be prevented.
また、図１８に示す如く、駆動輪体１６のスプロケット歯底部８９の断面端面形状を台形状に形成している。スプロケット歯底部８９の台形内周側幅ａと芯金体９５の芯金爪部９５ａの根元側内幅ｂの差（ｂ−ａ）よりも、スプロケット歯底部８９の台形外周側幅ｃと芯金体９５の芯金爪部９５ａの先端側内幅ｄの差（ｄ−ｃ）が大きくなるように構成している。
Further, as shown in FIG. 18, the cross-sectional end face shape of the sprocket tooth bottom 89 of the drive wheel body 16 is formed in a trapezoidal shape. The trapezoid outer peripheral side width c of the sprocket tooth bottom 89 and the core are larger than the difference (ba) between the trapezoid inner peripheral width a of the sprocket tooth bottom 89 and the root inner width b of the core claw 95a of the metal core 95. A difference (dc) in the tip side inner width d of the metal core claw portion 95a of the metal body 95 is configured to be large.
なお、スプロケット歯底部８９の台形外周側幅ｃと芯金体９５の芯金爪部９５ａの先端側内幅ｄの差（ｄ−ｃ）を最も大きく形成し、その差（ｄ−ｃ）に比べ、スプロケット歯底部８９の台形内周側幅ａと芯金体９５の芯金爪部９５ａの先端側内幅ｄの差（ｄ−ａ）を小さく形成し、スプロケット歯底部８９の台形内周側幅ａと芯金体９５の芯金爪部９５ａの根元側内幅ｂの差（ｂ−ａ）をさらに小さく形成している。
The difference (dc) between the trapezoid outer peripheral side width c of the sprocket tooth bottom 89 and the tip side inner width d of the core metal claw portion 95a of the core metal body 95 is formed to be the largest, and the difference (dc) In comparison, the difference (da) between the trapezoid inner peripheral width a of the sprocket tooth bottom 89 and the tip inner width d of the metal core claw 95a of the metal core 95 is formed to be small, and the trapezoid inner periphery of the sprocket tooth bottom 89 is formed. The difference (ba) between the side width a and the base side inner width b of the cored bar claw portion 95a of the cored bar 95 is further reduced.
図１、図１４〜図１６、図１８に示す如く、エンジン８を搭載する走行機体１１と、走行機体１１の下側に設けるトラックフレーム１７と、トラックフレーム１７に駆動輪体１６及び従動輪体２１，２３を介して装着する左右の走行クローラ２５とを備え、駆動輪体１６に歯合させる複数の芯金体９５を走行クローラ２５に設ける作業車両において、走行クローラ２５のうち左右幅の中央部にゴムベルト体としての接触凸部９４ａを設け、駆動輪体１６の輪状部としてのスプロケット歯底部８９と従動輪体２１，２３の輪状部が接触凸部９４ａに当接して、走行クローラ２５を回転するように構成している。したがって、軽負荷時、駆動輪体１６のスプロケット歯底部８９と接触凸部９４ａの摩擦駆動にて、駆動輪体１６の回転力が走行クローラ２５に伝達される。一方、重負荷時、芯金体９５と前記駆動輪体１６の歯体（スプロケット歯体９０）の金属接触にて、駆動輪体１６の回転力が前記走行クローラ２５に伝達される。即ち、軽負荷時の駆動騒音を低減できるものでありながら、たわみ等による駆動損失を低減でき、重負荷時の歯とびを防止できる。さらに、従動輪体２１，２３が接触凸部９４ａ上を常に転動して、従動輪体２１，２３部から発生する金属接触音を低減できる。
As shown in FIGS. 1, 14 to 16, and 18, a traveling machine body 11 on which the engine 8 is mounted, a track frame 17 provided below the traveling machine body 11, a driving wheel body 16 and a driven wheel body on the track frame 17. In a work vehicle that includes left and right traveling crawlers 25 that are mounted via 21 and 23 and that has a plurality of metal cores 95 that mesh with the driving wheel body 16 in the traveling crawler 25, A contact convex portion 94a as a rubber belt body is provided at the portion, and the sprocket tooth bottom portion 89 as the annular portion of the driving wheel body 16 and the annular portions of the driven wheel bodies 21 and 23 abut against the contact convex portion 94a, so that the traveling crawler 25 is It is configured to rotate. Accordingly, during light load, the rotational force of the drive wheel body 16 is transmitted to the traveling crawler 25 by the friction drive between the sprocket tooth bottom 89 of the drive wheel body 16 and the contact convex portion 94a. On the other hand, during heavy load, the rotational force of the driving wheel 16 is transmitted to the traveling crawler 25 by metal contact between the metal core 95 and the toothed body (sprocket toothing 90) of the driving wheel 16. That is, while it is possible to reduce driving noise at light load, it is possible to reduce drive loss due to deflection and the like, and to prevent tooth jump at heavy load. Furthermore, the driven wheel bodies 21 and 23 always roll on the contact convex portions 94a, and the metal contact sound generated from the driven wheel bodies 21 and 23 can be reduced.
図１５、図１８に示す如く、走行クローラ２５のうち左右幅の中央部にゴムベルト体としての接触凸部９４ａを設け、走行クローラ２５の内周面に接触凸部９４ａを一体的に形成し、駆動輪体１６の輪状部としてのスプロケット歯底部８９と従動輪体２１，２３の輪状部としての外周面が接触凸部９４ａ上にて回転するように構成している。したがって、軽負荷時、駆動輪体１６のスプロケット歯底部８９と接触凸部９４ａの摩擦駆動にて、駆動輪体１６の回転力が走行クローラ２５に伝達される。即ち、軽負荷時の駆動騒音を低減できる。駆動輪体１６または芯金体９５の摩耗を防止できる。一方、重負荷時、芯金体９５と駆動輪体１６の歯の金属接触にて、駆動輪体１６の回転力が走行クローラ２５に伝達される。即ち、走行クローラ２５のたわみまたはへたりによる駆動損失を低減できる。駆動輪体１６の歯とびを防止できる。さらに、従動輪体２１，２３が接触凸部９４ａ上を常に転動することにより、従動輪体２１，２３部から発生する金属接触音を低減できる。
As shown in FIGS. 15 and 18, a contact convex portion 94 a as a rubber belt body is provided in the central portion of the lateral width of the traveling crawler 25, and the contact convex portion 94 a is integrally formed on the inner peripheral surface of the traveling crawler 25. A sprocket tooth bottom 89 as a ring-shaped portion of the driving wheel body 16 and an outer peripheral surface as a ring-shaped portion of the driven wheel bodies 21 and 23 are configured to rotate on the contact convex portion 94a. Accordingly, during light load, the rotational force of the drive wheel body 16 is transmitted to the traveling crawler 25 by the friction drive between the sprocket tooth bottom 89 of the drive wheel body 16 and the contact convex portion 94a. That is, it is possible to reduce drive noise at light load. Wear of the driving wheel body 16 or the metal core body 95 can be prevented. On the other hand, during heavy load, the rotational force of the drive wheel body 16 is transmitted to the traveling crawler 25 by metal contact between the teeth of the metal core 95 and the drive wheel body 16. That is, the drive loss due to the deflection or sag of the traveling crawler 25 can be reduced. The tooth jump of the drive wheel body 16 can be prevented. Furthermore, since the driven wheel bodies 21 and 23 always roll on the contact convex portions 94a, the metal contact sound generated from the driven wheel bodies 21 and 23 portions can be reduced.
図１５、図１８に示す如く、前記駆動輪体１６のうち外周部の両側に左右のスプロケット歯体９０を突出させ、左右のスプロケット歯体９０の間にスプロケット歯底部８９を形成し、左右のスプロケット歯体９０に前記芯金体９５を金属接触させ、左右のスプロケット歯体９０の内側面とスプロケット歯底部８９とに前記接触凸部９４ａを接触させるように構成している。したがって、走行クローラ２５に横滑り力が作用したときにも、左右のスプロケット歯体９０の内側面と接触凸部９４ａとの接触によって、駆動輪体１６から走行クローラ２５が外れるのを簡単に防止できる。駆動輪体１６の外周全体に形成されるスプロケット歯底部８９と走行クローラ２５の接触凸部９４ａとの接触によって、スプロケット歯底部８９と接触凸部９４ａとの摩擦面を広く形成でき、スプロケット歯底部８９と接触凸部９４ａとの接触面圧を低下させることができ、スプロケット歯底部８９または接触凸部９４ａの摩耗を抑制できる。
As shown in FIGS. 15 and 18, left and right sprocket teeth 90 are protruded on both sides of the outer peripheral portion of the driving wheel body 16, and a sprocket tooth bottom 89 is formed between the left and right sprocket teeth 90. The metal core 95 is brought into metal contact with the sprocket tooth body 90, and the contact convex portion 94 a is brought into contact with the inner surface of the left and right sprocket tooth bodies 90 and the sprocket tooth bottom 89. Therefore, even when a side-slip force is applied to the traveling crawler 25, it is possible to easily prevent the traveling crawler 25 from being detached from the drive wheel body 16 due to the contact between the inner side surfaces of the left and right sprocket tooth bodies 90 and the contact convex portions 94a. . Due to the contact between the sprocket tooth bottom 89 formed on the entire outer periphery of the drive wheel 16 and the contact convex portion 94a of the traveling crawler 25, the friction surface between the sprocket tooth bottom 89 and the contact convex portion 94a can be widely formed. The contact surface pressure between 89 and the contact convex portion 94a can be reduced, and wear of the sprocket tooth bottom 89 or the contact convex portion 94a can be suppressed.
図１５、図１８に示す如く、前記駆動輪体１６のスプロケット歯底部８９端面を台形状に形成し、スプロケット歯底部８９の台形内周側幅ａと前記芯金体９５の爪部根元側の内幅ｂの差（ａ−ｂ）よりも、スプロケット歯底部８９の台形外周側幅ｃと前記芯金体９５の爪部先端側の内幅ｄの差（ｃ−ｄ）が大きくなるように構成している。したがって、前記走行クローラ２５に横滑り力が作用したときにも、前記駆動輪体１６から前記走行クローラ２５が外れるのを簡単に防止できる。
As shown in FIGS. 15 and 18, the end surface of the sprocket tooth bottom 89 of the drive wheel body 16 is formed in a trapezoidal shape, and the trapezoid inner peripheral side width a of the sprocket tooth bottom 89 and the claw part base side of the metal core 95 are formed. The difference (cd) between the trapezoid outer peripheral side width c of the sprocket tooth bottom 89 and the inner width d on the tip end side of the claw part of the metal core 95 is larger than the difference (ab) of the inner width b. It is composed. Therefore, it is possible to easily prevent the traveling crawler 25 from being detached from the driving wheel body 16 even when a side slip force is applied to the traveling crawler 25.
また、図１７、図１９、図２５を参照して駆動輪体１６の構造を説明する。図１７は走行機体１１の左側に駆動輪体１６を配置する説明図、図１９は走行機体１１の右側に駆動輪体１６を配置する説明図であり、後車軸１５に平板状のリム体８６を締結する構造であって、リム体８６に貫通孔９１を形成し、貫通孔９１にボルト８８を貫通させる一方、駆動輪体１６にネジ孔９２を形成し、ネジ孔９２に前記ボルト８８を螺着し、リム体８６に駆動輪体１６を締結している。
Further, the structure of the drive wheel body 16 will be described with reference to FIGS. 17, 19, and 25. FIG. 17 is an explanatory diagram in which the driving wheel body 16 is disposed on the left side of the traveling machine body 11, and FIG. 19 is an explanatory diagram in which the driving wheel body 16 is disposed on the right side of the traveling machine body 11, and a flat rim body 86 on the rear axle 15. The through-hole 91 is formed in the rim body 86 and the bolt 88 is passed through the through-hole 91, while the screw hole 92 is formed in the drive wheel body 16, and the bolt 88 is inserted into the screw hole 92. The drive wheel body 16 is fastened to the rim body 86 by screwing.
上記の構成により、一般的に、前進移動時間が後進よりも多いトラクタ１０では、駆動輪体１６のスプロケット歯体９０のうち、前進移動にて芯金爪部９５ａに当接する前記スプロケット歯体９０の前進側面が後進側面よりも多く摩耗する。例えば、スプロケット歯体９０の前進側面が摩耗した場合、図１７のように走行機体１１の左側に配置していた駆動輪体１６を、図１９のように走行機体１１の右側に配置することにより、図１７におけるスプロケット歯体９０の前進側面が、図１９では後進側面になり、図１７における後進側面が図１９では前進側面になる。即ち、走行機体１１の左側と右側の各駆動輪体１６を入れ換えることによって、摩耗が少ない後進側面を前進側面として、左右の各駆動輪体１６を使用でき、駆動輪体１６の耐用時間を長くして、部品交換コストを低減できる。また、走行機体１１の左側と右側とで、リム体８６に対する駆動輪体１６の当たり面（締結面）が同一面になるから、駆動輪体１６の当たり面（一側面）だけをフライス加工すればよく、加工コストも低減できる。
With the above configuration, in general, in the tractor 10 in which the forward movement time is longer than the reverse movement, the sprocket tooth body 90 that abuts on the metal core claw portion 95a by forward movement among the sprocket tooth bodies 90 of the drive wheel body 16. The forward side is worn more than the reverse side. For example, when the advancing side surface of the sprocket tooth body 90 is worn, the driving wheel body 16 arranged on the left side of the traveling machine body 11 as shown in FIG. 17 is arranged on the right side of the traveling machine body 11 as shown in FIG. The forward side surface of the sprocket tooth body 90 in FIG. 17 is the reverse side surface in FIG. 19, and the reverse side surface in FIG. 17 is the forward side surface in FIG. That is, by replacing the left and right driving wheel bodies 16 on the left and right sides of the traveling machine body 11, the left and right driving wheel bodies 16 can be used with the reverse side surface with less wear as the forward side surface, and the service life of the driving wheel body 16 is increased. Thus, the part replacement cost can be reduced. Further, since the contact surface (fastening surface) of the drive wheel body 16 with respect to the rim body 86 is the same surface on the left side and the right side of the traveling machine body 11, only the contact surface (one side surface) of the drive wheel body 16 is milled. The processing cost can be reduced.
さらに、図２５に示す如く、４体の部分輪体１６ａに分割して駆動輪体１６を形成し、放射線方向の端面１６ｂを付き合わせて４体の部分輪体１６ａを輪形に結合して同一円周に配置する構造において、駆動輪体１６両端側の各端面１６ｂに付合せ段部１６ｃをそれぞれ形成する。肉薄に形成する一方の端面１６ｂの付合せ段部１６ｃに貫通孔１６ｄを開設する。肉厚に形成する他方の端面１６ｂの付合せ段部１６ｃにネジ孔１６ｅを設ける。
Further, as shown in FIG. 25, the driving wheel body 16 is formed by being divided into four partial ring bodies 16a, and the four partial ring bodies 16a are joined in a ring shape by attaching the end faces 16b in the radial direction. In the structure arranged on the circumference, an attachment step 16c is formed on each end face 16b on both ends of the drive wheel body 16 respectively. A through hole 16d is formed in the attachment step 16c of one end face 16b that is formed to be thin. A screw hole 16e is provided in the attachment step 16c of the other end surface 16b formed to be thick.
即ち、前記リム体８６の一側面に部分輪体１６ａを当接させ、前記リム体８６及び部分輪体１６ａに、貫通孔９１及び貫通孔１６ｄを介して、前記リム体８６の他側面側からボルト８８を挿入させ、次いで隣接させる部分輪体１６ａのネジ孔１６ｅにボルト８８を挿入させる。隣り合う各部分輪体１６ａの付合せ段部１６ｃを合体させ、リム体８６の一側面に、隣り合う各部分輪体１６ａを前記リム体８６に締結する。そのため、各部分輪体１６ａの付合せ段部１６ｃの合体にて、各部分輪体１６ａの固定位置を簡単に決定できる。また、作業者は、一方の手で部分輪体１６ａを支持しながら、もう一方の手で工具を握り、ボルト８８を螺着操作できる。
That is, the partial ring body 16a is brought into contact with one side surface of the rim body 86, and the rim body 86 and the partial ring body 16a are contacted from the other side surface of the rim body 86 via the through hole 91 and the through hole 16d. The bolt 88 is inserted, and then the bolt 88 is inserted into the screw hole 16e of the adjacent partial ring body 16a. The joining step portions 16 c of the adjacent partial ring bodies 16 a are combined, and the adjacent partial ring bodies 16 a are fastened to the rim body 86 on one side surface of the rim body 86. Therefore, the fixed position of each partial ring body 16a can be easily determined by the combination of the attachment step portions 16c of each partial ring body 16a. In addition, the operator can hold the tool with the other hand while screwing the bolt 88 while supporting the partial ring body 16a with one hand.
次いで、図９、図２２〜図２４、図２６を参照して後クローラ走行装置１３の構造を説明する。図２６に示す如く、駆動輪体１６及び従動輪体２１，２３及び転動輪２６を介して前記トラックフレーム１７に前記走行クローラ２５を張設するもので、駆動輪体１６の左右幅中心線Ｐに対して、機体内側方に一定幅Ｓだけ、従動輪体２１，２３及び転動輪２６の左右幅中心線Ｑをオフセットさせている。即ち、走行クローラ２５の芯金爪部９５ａに対して、駆動輪体１６はこの歯底部８９が外側で接触する位置に、従動輪体２１，２３及び転動輪２６はこの内側で接触する位置に、それぞれオフセットさせている。
Next, the structure of the rear crawler traveling device 13 will be described with reference to FIGS. 9, 22 to 24, and 26. As shown in FIG. 26, the traveling crawler 25 is stretched on the track frame 17 via the drive wheel body 16, the driven wheel bodies 21 and 23, and the rolling wheel 26. On the other hand, the left and right width center lines Q of the driven wheels 21 and 23 and the rolling wheels 26 are offset by a certain width S toward the inside of the machine body. That is, the driving wheel 16 is in a position where the tooth bottom 89 contacts the outside of the core claw 95a of the traveling crawler 25, and the driven wheels 21, 23 and the rolling wheel 26 are in contact with the inside. , Each offset.
上記の構成により、従動輪体２１，２３及び転動輪２６にて走行クローラ２５の接地側を支持することによって、走行クローラ２５の旋回外側方向への横滑り力（外向きの力）が駆動輪体１６に作用するのを阻止する。走行クローラ２５に駆動輪体１６が適正に歯合される。例えば、旋回外側方向への横滑り力（外向きの力）が発生し易い走行状態でも、または走行駆動負荷が高負荷の状態下で高速移動するときであっても、駆動輪体１６から走行クローラ２５が離脱するのを防止できる。
With the configuration described above, the grounding side of the traveling crawler 25 is supported by the driven wheel bodies 21 and 23 and the rolling wheel 26, so that the side slip force (outward force) of the traveling crawler 25 in the turning outer direction is driven wheel body. 16 is prevented. The driving wheel 16 is properly meshed with the traveling crawler 25. For example, the traveling crawler from the driving wheel body 16 even in a traveling state in which a side slip force (outward force) in the direction of the turning outer side is easily generated or when the traveling drive load moves at a high speed under a high load state. 25 can be prevented from leaving.
図２２に示す如く、駆動輪体１６の歯底部８９のうち、軸心線方向に切断した歯底部８９端面の形状を、駆動輪体１６の左右幅中心に対して非対称の台形状に形成するもので、駆動輪体１６の歯底部８９は、駆動輪体の左右幅中心線Ｐに対して、その端面の機外側幅Ｔよりも、その端面の機内側幅Ｕを大きく形成している。したがって、従動輪体２１，２３及び転動輪２６に対して、駆動輪体１６を機外側方に簡単にオフセットできるものでありながら、駆動輪体１６を軽量に形成できる。
As shown in FIG. 22, the shape of the end surface of the tooth bottom portion 89 cut in the axial direction in the tooth bottom portion 89 of the drive wheel body 16 is formed in an asymmetric trapezoidal shape with respect to the center of the left-right width of the drive wheel body 16. Therefore, the tooth bottom portion 89 of the drive wheel body 16 is formed such that the machine inside width U of the end face is larger than the machine outside width T of the end face with respect to the lateral center line P of the drive wheel body. Therefore, the drive wheel body 16 can be formed lighter while the drive wheel body 16 can be easily offset to the outer side of the driven wheel bodies 21 and 23 and the rolling wheel 26.
図２３に示す如く、走行クローラ２５の内周面のうち、駆動輪体１６の歯底部８９が通過する面、または従動輪体２１，２３が通過する面を、機体外側が低く機体内側が高い傾斜面に形成もので、走行クローラ２５が機体外側方に移動する横滑り力に対して、前記傾斜面によって走行クローラ２５のテンションを増大させる。即ち、走行クローラ２５の横滑り力（外向きの力）に対して、走行クローラ２５を機体内側方に移動する反力（内向きの力）を発生させるもので、走行クローラ２５の離脱を防止し、または走行クローラ２５の偏摩耗を抑制する。なお、駆動輪体１６の歯底部８９が通過する面を、機体外側が高く機体内側が低い傾斜面に、走行クローラ２５の内周面を形成してもよい。走行クローラ２５の内周面と同様に、歯底部８９も傾斜させてもよい。
As shown in FIG. 23, on the inner peripheral surface of the traveling crawler 25, the surface through which the tooth bottom 89 of the driving wheel 16 passes or the surface through which the driven wheels 21 and 23 pass is low and the inside of the airframe is high. It is formed on the inclined surface, and the tension of the traveling crawler 25 is increased by the inclined surface with respect to the side slip force that the traveling crawler 25 moves outward of the machine body. That is, it generates a reaction force (inward force) that moves the traveling crawler 25 inward of the machine against the side slip force (outward force) of the traveling crawler 25, and prevents the traveling crawler 25 from being detached. Alternatively, uneven wear of the traveling crawler 25 is suppressed. In addition, the inner peripheral surface of the traveling crawler 25 may be formed on the surface through which the tooth root portion 89 of the driving wheel body 16 passes on an inclined surface that is higher on the outer side of the body and lower on the inner side of the body. Similarly to the inner peripheral surface of the traveling crawler 25, the tooth bottom 89 may be inclined.
図２４に示す如く、転動輪２６の周面のうち内側が当接する前記走行クローラ２５の内周面の一部を凸状内周面２５ｂに形成するもので、凸状内周面２５ｂは、走行クローラ２５の内周側に向けて芯金爪部９５ａ位置の部分を最も突出させるように形成する。走行クローラ２５の両側縁方向に向けて凸状内周面２５ｂが傾斜するように構成している。即ち、走行クローラ２５の接地側において、凸状内周面２５ｂは、芯金爪部９５ａに近い位置の部分が最も高くなり、走行クローラ２５の両側縁方向に向けて低くなる傾斜面に形成している。
As shown in FIG. 24, a part of the inner peripheral surface of the traveling crawler 25 with which the inner side of the peripheral surface of the rolling wheel 26 abuts is formed on the convex inner peripheral surface 25b. The convex inner peripheral surface 25b is The core claw portion 95a is formed so as to protrude most toward the inner peripheral side of the traveling crawler 25. The convex inner peripheral surface 25 b is configured to be inclined toward both side edges of the traveling crawler 25. That is, on the ground contact side of the traveling crawler 25, the convex inner peripheral surface 25b is formed on an inclined surface that is highest at a position close to the cored bar claw portion 95a and decreases toward both side edges of the traveling crawler 25. ing.
上記の構成により、走行クローラ２５が機体外側方または機体内側方にずれる横滑り力に対して、走行クローラ２５を所定位置に戻す力が発生し、走行クローラ２５または転動輪２６の偏摩耗を抑制する。即ち、走行クローラ２５の凸状内周面２５ｂによって、転動輪２６の左右の輪体に外向きの力がそれぞれ加えられるから、走行クローラ２５と転動輪２６が中心位置で釣り合うように、転動輪２６に走行クローラ２５が支持される。即ち、転動輪２６と芯金爪部９５ａが接触するのを低減し、その接触によって転動輪２６または芯金爪部９５ａが摩耗するのを防止でき、かつそれらの金属接触音の発生を抑制できる。
With the above configuration, a force for returning the traveling crawler 25 to a predetermined position is generated with respect to a side slip force that the traveling crawler 25 shifts to the outer side or the inner side of the body, thereby suppressing uneven wear of the traveling crawler 25 or the rolling wheels 26. . In other words, the convex inner peripheral surface 25b of the traveling crawler 25 applies an outward force to the left and right wheels of the rolling wheel 26, so that the rolling wheel 25 and the rolling wheel 26 are balanced at the center position. The traveling crawler 25 is supported by 26. That is, the contact between the rolling wheel 26 and the cored bar claw portion 95a can be reduced, the contact between the rolling wheel 26 and the cored bar claw portion 95a can be prevented, and the generation of the metal contact noise can be suppressed. .
図１、図９、図２６に示す如く、エンジン８を搭載する走行機体１１と、走行機体１１の下側に設けるトラックフレーム１７と、トラックフレーム１７に装着する走行クローラ２５とを備え、駆動輪体１６及び前従動輪体２１及び後従動輪体２３及び転動輪２６を介してトラックフレーム１７に走行クローラ２５を張設する作業車両において、駆動輪体１６の左右幅中心線Ｐに対して、機体内側方に一定幅Ｓだけ、従動輪体２１，２３及び転動輪２６の左右幅中心線Ｑをオフセットさせている。したがって、旋回外側方向の力（横滑り力）が駆動輪体１６に作用するのを簡単に阻止できる。即ち、駆動輪体１６に対して、前従動輪体２１及び後従動輪体２３及び転動輪２６を機内側方にオフセットして、前従動輪体２１及び後従動輪体２３及び転動輪２６にて走行クローラ２５の接地側を支持することによって、走行クローラ２５に駆動輪体１６を適正に歯合させ、走行駆動負荷が増大するのを防止できる。例えば、走行機体１１が旋回するときに、旋回外側方向の力（横滑り力）が発生し易い場合でも、または走行駆動負荷が高負荷で高速移動するときであっても、駆動輪体１６から走行クローラ２５が離脱するのを防止できる。また、駆動輪体１６の左右幅中心線Ｐに対して、機体内側方に一定幅Ｓだけ、転動輪２６の左右幅中心線Ｑをオフセットさせることにより、走行クローラ２５によって転動輪２６が擦られるのを防止でき、転動輪２６の偏摩耗を低減できる。
As shown in FIGS. 1, 9, and 26, the vehicle includes a traveling machine body 11 on which the engine 8 is mounted, a track frame 17 provided on the lower side of the traveling machine body 11, and a traveling crawler 25 attached to the track frame 17. In the work vehicle in which the traveling crawler 25 is stretched on the track frame 17 via the body 16, the front driven wheel body 21, the rear driven wheel body 23, and the rolling wheel 26, The left and right width center lines Q of the driven wheel bodies 21 and 23 and the rolling wheels 26 are offset by a certain width S toward the inside of the machine body. Therefore, it is possible to easily prevent the force in the turning outer side (side slip force) from acting on the drive wheel body 16. That is, the front driven wheel body 21, the rear driven wheel body 23, and the rolling wheel 26 are offset toward the inside of the machine with respect to the driving wheel body 16, so that the front driven wheel body 21, the rear driven wheel body 23, and the rolling wheel 26 are offset. By supporting the grounding side of the traveling crawler 25, the driving wheel body 16 can be properly meshed with the traveling crawler 25, and an increase in traveling driving load can be prevented. For example, when the traveling machine body 11 turns, even if a force (slipping force) in the direction of the turning outer side is likely to be generated, or even when the traveling drive load moves at a high speed with a high load, the traveling vehicle body 11 travels. The crawler 25 can be prevented from separating. Further, the running wheel 26 is rubbed by the traveling crawler 25 by offsetting the left and right width center line Q of the rolling wheel 26 by a certain width S inward of the left and right width center line P of the driving wheel body 16. Can be prevented, and uneven wear of the rolling wheels 26 can be reduced.
図２６に示す如く、前記走行クローラ２５の芯金爪部９５ａに対して、前記駆動輪体１６はこのスプロケット歯底部８９が外側で接触する位置に、前従動輪体２１及び後従動輪体２３及び転動輪２６はこの内側で接触する位置に、それぞれオフセットさせている。したがって、駆動輪体１６または前従動輪体２１及び後従動輪体２３または転動輪２６が、走行クローラ２５の芯金爪部９５ａに当接する力を軽減でき、芯金爪部９５ａ、または駆動輪体１６または前従動輪体２１及び後従動輪体２３または転動輪２６の偏摩耗を低減できる。
As shown in FIG. 26, the driving wheel 16 is in a position where the sprocket tooth bottom 89 is in contact with the outer side of the core metal claw 95a of the traveling crawler 25, and the front driven wheel 21 and the rear driven wheel 23. The rolling wheels 26 are offset to the positions where they contact each other. Therefore, it is possible to reduce the force with which the driving wheel body 16 or the front driven wheel body 21 and the rear driven wheel body 23 or the rolling wheel 26 abut on the core metal claw portion 95a of the traveling crawler 25, and the core metal claw portion 95a or the driving wheel. Uneven wear of the body 16 or the front driven wheel body 21 and the rear driven wheel body 23 or the rolling wheel 26 can be reduced.
図２２に示す如く、駆動輪体１６のスプロケット歯底部８９のうち、軸心線方向に切断した歯底部８９端面の形状を、駆動輪体１６の左右幅中心に対して非対称の台形状に形成している。したがって、前記歯底部８９端面の機体外側よりも機体内側方を広く形成して、駆動輪体１６を軽量化し、かつ走行クローラ２５と駆動輪体１６の歯合を適正に維持できるものでありながら、前従動輪体２１及び後従動輪体２３及び転動輪２６に対して、駆動輪体１６を機外側方に簡単にオフセットできる。また、前記歯底部８９端面を台形状に形成することによって、例えば四角形状などに比べ、駆動輪体１６の製造コストまたは自重を低減できる。
As shown in FIG. 22, among the sprocket tooth bottom portions 89 of the drive wheel body 16, the shape of the end surface of the tooth bottom portion 89 cut in the axial direction is formed in an asymmetric trapezoidal shape with respect to the center of the left and right width of the drive wheel body 16. doing. Accordingly, the inner side of the fuselage is formed wider than the outer side of the fuselage 89 at the end surface of the tooth bottom 89, the driving wheel 16 can be reduced in weight, and the engagement between the traveling crawler 25 and the driving wheel 16 can be properly maintained. The driving wheel body 16 can be easily offset outward from the front driven wheel body 21, the rear driven wheel body 23, and the rolling wheel 26. In addition, by forming the end face of the tooth bottom portion 89 in a trapezoidal shape, the manufacturing cost or the own weight of the drive wheel body 16 can be reduced as compared with, for example, a square shape.
図２３に示す如く、走行クローラ２５の内周面のうち、駆動輪体１６の歯底部８９が通過する面、または前従動輪体２１及び後従動輪体２３が通過する面を、機体外側が低く機体内側が高い傾斜面に形成している。したがって、走行クローラ２５が機体外側方に移動する横滑り力に対して、前記傾斜面によって前記走行クローラ２５のテンションを増大させることができる。即ち、走行クローラ２５の横滑り力に対して、走行クローラ２５を機体内側方に移動する反力が発生して、走行クローラ２５の離脱を防止でき、または走行クローラ２５の偏摩耗を簡単に抑制できる。
As shown in FIG. 23, on the inner peripheral surface of the traveling crawler 25, the surface through which the tooth bottom portion 89 of the driving wheel body 16 passes, or the surface through which the front driven wheel body 21 and the rear driven wheel body 23 pass, It is formed on an inclined surface that is low and the inside of the fuselage is high. Therefore, it is possible to increase the tension of the traveling crawler 25 by the inclined surface with respect to the side slip force that the traveling crawler 25 moves outward of the machine body. That is, a reaction force that moves the traveling crawler 25 toward the inside of the machine body is generated with respect to the side slip force of the traveling crawler 25, so that the traveling crawler 25 can be prevented from being detached or uneven wear of the traveling crawler 25 can be easily suppressed. .
図２４に示す如く、転動輪２６の周面のうち内側が当接する走行クローラ２５の内周面の一部を凸状内周面２５ｂにて凸状に形成している。したがって、走行クローラ２５が機体外側方または機体内側方にずれる横滑り力に対して、走行クローラ２５を所定位置に戻す力を発生させることができ、走行クローラ２５または転動輪２６の偏摩耗を簡単に抑制できる。
As shown in FIG. 24, a part of the inner peripheral surface of the traveling crawler 25 with which the inside abuts out of the peripheral surface of the rolling wheel 26 is formed in a convex shape by a convex inner peripheral surface 25b. Therefore, it is possible to generate a force for returning the traveling crawler 25 to a predetermined position with respect to a side slip force that the traveling crawler 25 shifts to the outer side of the machine body or the inner side of the machine body. Can be suppressed.
さらに、図２０〜図２１に示す如く、クローラ本体９４の内周面のうち、無端帯の左右幅方向に隣接する各芯金爪部９５ａ間の内周面に、内周凸面部９４ｂが形成されている。転動輪２６の通過面（凸状内周面２５ｂ）に対する芯金爪部９５ａの高さ寸法Ｈ１に比べ、内周凸面部９４ｂに対する芯金爪部９５ａの高さ寸法Ｈ２を大きく形成する。無端帯の左右幅方向に隣接する各芯金爪部９５ａ間で、内周凸面部９４ｂの形成にてクローラ本体９４のゴム部分を隆起させている。そのため、前従動輪体２１や後従動輪体２３が内周凸面部９４ｂ上を通過でき、走行クローラ２５の駆動に伴う振動または騒音を低減できる。
Furthermore, as shown in FIGS. 20-21, the inner peripheral convex surface part 94b is formed in the inner peripheral surface between each metal core claw part 95a adjacent to the left-right width direction of an endless belt among the inner peripheral surfaces of the crawler main body 94. Has been. The height dimension H2 of the metal core claw portion 95a with respect to the inner peripheral convex surface portion 94b is formed larger than the height dimension H1 of the metal core claw portion 95a with respect to the passing surface (convex inner peripheral surface 25b) of the rolling wheel 26. The rubber portion of the crawler body 94 is raised by forming the inner peripheral convex surface portion 94b between the core metal claws 95a adjacent to each other in the left-right width direction of the endless belt. Therefore, the front driven wheel body 21 and the rear driven wheel body 23 can pass over the inner peripheral convex surface portion 94b, and vibration or noise associated with driving of the traveling crawler 25 can be reduced.
一方、転動輪２６の通過面（凸状内周面２５ｂ）と、芯金体９５の翼片部９５ｃ根元部分の上面との距離、即ち転動輪２６の通過面部分のクローラ本体９４の厚み寸法Ｈ３に比べ、無端帯の左右幅方向に隣接する各芯金爪部９５ａの間（芯金胴部９５ｂ上面側）のクローラ本体９４の厚み寸法Ｈ４を大きく形成する。そのため、クローラ本体９４の左右幅中央部と芯金爪部９５ａ上部との高さの差を確保でき、走行クローラ２５に横滑り力や傾き力が作用しても、走行クローラ２５の離脱を阻止できる。
On the other hand, the distance between the passing surface (convex inner peripheral surface 25 b) of the rolling wheel 26 and the upper surface of the root portion of the blade piece 95 c of the metal core 95, that is, the thickness dimension of the crawler body 94 at the passing surface portion of the rolling wheel 26. Compared with H3, the thickness dimension H4 of the crawler body 94 between the cored bar claws 95a adjacent to the endless belt in the left-right width direction (upper side of the cored bar body 95b) is formed larger. For this reason, a difference in height between the central portion of the crawler body 94 in the left-right width and the upper portion of the cored bar claw portion 95a can be secured, and even when a side slipping force or a tilting force acts on the traveling crawler 25, the traveling crawler 25 can be prevented from being detached. .
さらに、走行クローラ２５の外周側に芯金胴部９５ｂを突出させ、クローラ本体９４のうち芯金胴部９５ｂの両側方に補強用のスチールコード９６を埋設している。クローラ本体９４の厚みを必要最低限におさえるように構成する。また、芯金体９５は、翼片部９５ｃの幅Ｈ６に比べ、芯金胴部９５ｂの幅Ｈ５を広く形成する。そのため、芯金体９５の強度を確保できると共に、例えば、芯金胴部９５ｂの表面に凹部を形成して、クローラ本体９４とのゴム接着面積を大きくすることによって、芯金体９５に対してクローラ本体９４が剥離するのを低減して、クローラ本体９４と芯金体９５の間に泥水が侵入するのを低減できる。
Further, a cored bar body 95b is protruded on the outer peripheral side of the traveling crawler 25, and reinforcing steel cords 96 are embedded on both sides of the cored bar body 95b in the crawler main body 94. The crawler body 94 is configured to have a minimum thickness. Further, the cored bar 95 is formed with a width H5 of the cored bar body 95b wider than the width H6 of the blade piece 95c. Therefore, the strength of the core metal body 95 can be secured, and, for example, a concave portion is formed on the surface of the core metal barrel portion 95b to increase the rubber bonding area with the crawler main body 94, so It is possible to reduce separation of the crawler main body 94 and muddy water from entering between the crawler main body 94 and the metal core 95.
次いで、図２４、図２７〜図３６を参照して、左右一対のトラックローラ２６ａを有する転動輪２６の支持構造を説明する。図２４、図２７に示す如く、トラックフレーム１７の下面にローラ支持筒体１１１をボルト締結する。一対のベヤリング軸受１１２を介してローラ軸体１１３を回転自在に軸支する。ローラ支持筒体１１１の左右の開口から左右外側方に向けてローラ軸体１１３の両端側を突出させる。ローラ軸体１１３の両端部に締結ナット１１４にて左右一対のトラックローラ２６ａを固着する。ローラ支持筒体１１１の左右の開口部のうち、ベヤリング軸受１１２の外側にダストシール１１５を設ける。なお、一対のベヤリング軸受１１２の間には、潤滑油（グリス）を充填する。
Next, with reference to FIGS. 24 and 27 to 36, a support structure for the rolling wheel 26 having a pair of left and right track rollers 26a will be described. As shown in FIGS. 24 and 27, the roller support cylinder 111 is bolted to the lower surface of the track frame 17. A roller shaft body 113 is rotatably supported via a pair of bearing bearings 112. Both end sides of the roller shaft body 113 protrude from the left and right openings of the roller support cylinder 111 toward the left and right outer sides. A pair of left and right track rollers 26 a are fixed to both ends of the roller shaft body 113 by fastening nuts 114. A dust seal 115 is provided outside the bearing bearing 112 in the left and right openings of the roller support cylinder 111. Note that a lubricating oil (grease) is filled between the pair of bearing bearings 112.
また、図２７に示す如く、ベヤリング軸受１１２外側のローラ軸体１１３にスリーブ１１６（またはカラー）を介してダストシール１１５を被嵌する。トラックローラ２６ａとスリーブ１１６の間に摩耗抑制板体１１７を挟持する。即ち、締結ナット１１４を締付けたときに、トラックローラ２６ａとベヤリング軸受１１２の間に、スリーブ１１６と摩耗抑制板体１１７が固着され、ダストシール１１５のリップ１１５ａに摩耗抑制板体１１７を接触させる。そのため、泥水侵入によるリップ１１５ａ及びその当たり面の摩耗を抑制でき、ベヤリング軸受１１２内部への泥水侵入を防止できる。
Further, as shown in FIG. 27, a dust seal 115 is fitted on the roller shaft body 113 outside the bearing bearing 112 via a sleeve 116 (or collar). An abrasion suppression plate 117 is sandwiched between the track roller 26 a and the sleeve 116. That is, when the fastening nut 114 is tightened, the sleeve 116 and the wear suppressing plate body 117 are fixed between the track roller 26a and the bearing bearing 112, and the wear suppressing plate body 117 is brought into contact with the lip 115a of the dust seal 115. Therefore, wear of the lip 115a and the contact surface thereof due to muddy water intrusion can be suppressed, and muddy water intrusion into the bearing bearing 112 can be prevented.
さらに、図２８に示す如く、ローラ支持筒体１１１の左右の開口縁にラビリンス用凹部１１１ａを形成し、摩耗抑制板体１１７の外周側端面１１７ａをローラ支持筒体１１１側に折り曲げ、ラビリンス用凹部１１１ａに前記外周側端面１１７ａを遊嵌状に挿入し、ラビリンス用凹部１１１ａと前記外周側端面１１７ａによってラビリンス隙間を形成し、草などの巻き付き、または泥水の侵入などを抑制し、ダストシール１１５の損傷を防止してもよい。
Further, as shown in FIG. 28, a labyrinth recess 111a is formed at the left and right opening edges of the roller support cylinder 111, and the outer peripheral side end surface 117a of the wear suppression plate 117 is bent toward the roller support cylinder 111, thereby forming the labyrinth recess. The outer peripheral side end surface 117a is inserted in a loosely fitting manner in 111a, and a labyrinth gap is formed by the labyrinth concave portion 111a and the outer peripheral side end surface 117a. May be prevented.
さらに、図２９に示す如く、ローラ支持筒体１１１の左右の開口縁にラビリンス用多段部１１１ｂを形成し、ラビリンス用多段部１１１ｂと相似形の多段端面２６ｂをトラックローラ２６ａの対向面に形成し、ラビリンス用多段部１１１ｂに相似形の多段端面２６ｂを対面させてラビリンス隙間を形成し、草などの巻き付き、または泥水の侵入などを抑制し、ダストシール１１５の損傷を防止してもよい。
Further, as shown in FIG. 29, a labyrinth multi-step portion 111b is formed on the left and right opening edges of the roller support cylinder 111, and a multi-step end surface 26b similar to the labyrinth multi-step portion 111b is formed on the opposing surface of the track roller 26a. The labyrinth multi-step portion 111b may be faced with a multi-step end surface 26b having a similar shape to form a labyrinth gap to prevent wrapping of grass or mud water and to prevent damage to the dust seal 115.
なお、図３０は前従動輪体２１（または後従動輪体２３）の部分拡大図であり、従動輪軸体２２１にベヤリング軸受１１２を介して従動輪体２１，２３を軸支すると共に、トラックフレーム１７に設けた従動輪ホルダ２２２に従動輪軸体２２１をナット１１４締結した構造において、図２７と同様に、ダストシール１１５、スリーブ１１６、摩耗抑制板体１１７を組付けたもので、締結ナット１１４を締付けたときに、従動輪ホルダ２２２とベヤリング軸受１１２の間に、スリーブ１１６と摩耗抑制板体１１７が固着され、ダストシール１１５のリップ１１５ａに摩耗抑制板体１１７を接触させ、泥水侵入によるリップ１１５ａ及びその当たり面の摩耗を抑制でき、ベヤリング軸受１１２内部への泥水侵入を防止できる。
30 is a partially enlarged view of the front driven wheel body 21 (or the rear driven wheel body 23). The driven wheel bodies 21 and 23 are pivotally supported on the driven wheel shaft body 221 via the bearing bearing 112, and the track frame. In the structure in which the driven wheel shaft body 221 is fastened to the nut 114 by the driven wheel holder 222 provided in the structure 17, as shown in FIG. 27, the dust seal 115, the sleeve 116, and the wear suppression plate 117 are assembled, and the fastening nut 114 is tightened. The sleeve 116 and the wear suppressing plate 117 are fixed between the driven wheel holder 222 and the bearing bearing 112, the wear suppressing plate 117 is brought into contact with the lip 115a of the dust seal 115, and the lip 115a and its Wear of the contact surface can be suppressed, and muddy water can be prevented from entering the bearing bearing 112.
