JP2013001129A - Working vehicle - Google Patents

Working vehicle Download PDF

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JP2013001129A
JP2013001129A JP2011130528A JP2011130528A JP2013001129A JP 2013001129 A JP2013001129 A JP 2013001129A JP 2011130528 A JP2011130528 A JP 2011130528A JP 2011130528 A JP2011130528 A JP 2011130528A JP 2013001129 A JP2013001129 A JP 2013001129A
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traveling
crawler
wheel
traveling crawler
tooth
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Shinya Kawajiri
伸也 川尻
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Yanmar Co Ltd
ヤンマー株式会社
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Abstract

PROBLEM TO BE SOLVED: To provide a working vehicle capable of reducing drive loss while reducing drive noises.SOLUTION: The working vehicle includes a traveling machine body 11 which is equipped with an engine 8, a track frame 17 which is provided on the downside of the traveling machine body 11, and right and left traveling crawlers 25 which are mounted in the track frame 17 via drive wheel bodies 16 and driven wheel bodies 21 and 23. In the working vehicle which has the right and left traveling crawlers 25 provided with a plurality of core bodies 95 for being meshed with each of the drive wheel bodies 16, a rubber belt body 94a is provided in the horizontal width center part of each of the traveling crawlers 25, and a ring-shaped part 89 of each of the drive wheel bodies 16 and ring-shaped parts of the driven wheel bodies 21 and 23 abut on the rubber belt body 94a to rotate the right and left traveling crawlers 25.

Description

本発明は、エンジンなどを搭載した機体の後部に左右の走行クローラを装設するトラクタ等の作業車両に関するものである。   The present invention relates to a work vehicle such as a tractor in which left and right traveling crawlers are installed in a rear portion of an airframe equipped with an engine and the like.

トラクタ等の走行車両における機体の後部に、左右の走行クローラを装設すること、つまり、機体の前部に左右の前車輪を装設し、機体の後部に左右の走行クローラを装設することは、先行技術としての特許文献1〜3等に記載されている。   Install left and right traveling crawlers at the rear of the aircraft in a traveling vehicle such as a tractor, that is, install left and right front wheels at the front of the aircraft, and install left and right traveling crawlers at the rear of the aircraft. Are described in Patent Documents 1 to 3 as prior art.

先行技術は、走行機体の後車軸ケースに後車軸を軸支して、後車軸に駆動輪体を取付ける一方、前記後車軸ケースよりも下方の部位に前後方向に延びるトラックフレームを配設して、トラックフレームに走行クローラを装着した構造であって、トラックフレームの前後方向の略中程部を、前記後車軸ケース等の走行機体側に、前記後車軸より適宜距離だけ下方の部位に配設した1本の揺動支点軸にて回動自在に枢着し、トラックフレームをその前部及び後部が互いに逆方向に上下動するように構成している。トラックフレームの前端側に設けた前従動輪体と、後端側に設けた後従動輪体と、前記駆動輪体とにわたって略三角形状に走行クローラを巻掛け、前記駆動輪体にて走行クローラを回転することによって、走行機体を前進移動又は後進移動させるという構成にしている。   In the prior art, a rear axle is pivotally supported on a rear axle case of a traveling machine body, and a driving wheel body is attached to the rear axle, while a track frame extending in the front-rear direction is disposed at a portion below the rear axle case. The track frame is mounted with a traveling crawler, and a substantially middle portion in the front-rear direction of the track frame is disposed on the traveling machine body side of the rear axle case or the like at a position below the rear axle by an appropriate distance. The single swing fulcrum shaft is pivotally attached to the track frame so that the front and rear portions of the track frame move up and down in opposite directions. A traveling crawler is wound in a substantially triangular shape across a front driven wheel provided on the front end side of the track frame, a rear driven wheel provided on the rear end side, and the driving wheel, and the traveling crawler is driven by the driving wheel. The traveling machine body is moved forward or backward by rotating.

特開平10−45051号公報Japanese Patent Laid-Open No. 10-45051 特開2006−96199号公報JP 2006-96199 A 特開2004−217054号公報JP 2004-217054 A

前記先行技術は、軽負荷時、走行クローラの芯金体と前記駆動輪体の歯の金属接触にて、前記駆動輪体の回転力が前記走行クローラに伝達される構造では、軽負荷時の駆動騒音を簡単に低減できない等の問題がある。また、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、前記揺動支点軸を中心として走行クローラが前上がりまたは前下りに傾斜し、前記走行クローラの接地面の前後方向の傾斜角度が大きくなりやすいから、前記走行機体の対地高さも変化しやすく、操縦座席に搭乗したオペレータの良好な乗り心地を維持できない等の問題もある。   The prior art has a structure in which the rotational force of the driving wheel body is transmitted to the traveling crawler by a metal contact between the core of the traveling crawler and the teeth of the driving wheel body at a light load. There is a problem that driving noise cannot be reduced easily. Further, when moving forward or backward, when traveling over a convex portion such as a farm shore, the traveling crawler tilts forward or downward about the swing fulcrum shaft, and the grounding surface of the traveling crawler Since the inclination angle in the front-rear direction tends to be large, the ground height of the traveling aircraft body is likely to change, and there is a problem that the good riding comfort of the operator who has boarded the control seat cannot be maintained.

そこで、本願発明は、これらの現状を検討して改善を施したトラクタなどの作業車両を提供しようとするものである。   Accordingly, the present invention seeks to provide a work vehicle such as a tractor that has been improved by examining these current conditions.

この技術的課題を達成するため、請求項1に係る発明は、エンジンを搭載する走行機体と、前記走行機体の下側に設けるトラックフレームと、前記トラックフレームに駆動輪体及び従動輪体を介して装着する左右の走行クローラとを備え、前記駆動輪体に歯合させる複数の芯金体を前記走行クローラに設ける作業車両において、前記走行クローラのうち左右幅の中央部にゴムベルト体を設け、前記駆動輪体の輪状部と従動輪体の輪状部が前記ゴムベルト体に当接して、前記走行クローラを回転するように構成したものである。   In order to achieve this technical problem, an invention according to claim 1 includes a traveling machine body on which an engine is mounted, a track frame provided on the lower side of the traveling machine body, and a drive wheel body and a driven wheel body on the track frame. A working vehicle provided with a plurality of metal cores to be engaged with the driving wheel body in the traveling crawler, a rubber belt body is provided at a central portion of the lateral width of the traveling crawler, The ring-shaped portion of the driving wheel body and the ring-shaped portion of the driven wheel body are in contact with the rubber belt body, and the traveling crawler is rotated.

請求項2に係る発明は、請求項1に記載の作業車両において、前記走行クローラ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を設け、前記走行クローラの内周面に前記接触凸部を一体的に形成し、前記駆動輪体の輪状部としての歯底部と前記従動輪体の輪状部としての外周面が前記接触凸部上にて回転するように構成したものである。   According to a second aspect of the present invention, in the work vehicle according to the first aspect, a contact convex portion as a rubber belt body is provided in a central portion of the lateral width of the traveling crawler, and the contact convex portion is provided on an inner peripheral surface of the traveling crawler. Are formed integrally so that a tooth bottom portion as a ring-shaped portion of the driving wheel body and an outer peripheral surface as a ring-shaped portion of the driven wheel body rotate on the contact convex portion.

請求項3に係る発明は、請求項2に記載の作業車両において、前記駆動輪体のうち外周部の両側に左右の歯体を突出させ、前記左右の歯体の間に前記歯底部を形成し、前記左右の歯体に前記芯金体を金属接触させ、前記左右の歯体の内側面と前記歯底部とに前記接触凸部を接触させるように構成したものである。   According to a third aspect of the present invention, in the work vehicle according to the second aspect, left and right tooth bodies are protruded on both sides of an outer peripheral portion of the drive wheel body, and the tooth bottom portion is formed between the left and right tooth bodies. Then, the metal core is brought into metal contact with the left and right tooth bodies, and the contact convex portions are brought into contact with the inner side surfaces and the tooth bottom portions of the left and right tooth bodies.

請求項4に係る発明は、請求項2に記載の作業車両において、前記駆動輪体の歯底部端面を台形状に形成し、前記歯底部の台形内周側幅と前記芯金体の爪部根元側の内幅の差よりも、前記歯底部の台形外周側幅と前記芯金体の爪部先端側の内幅の差が大きくなるように構成したものである。   According to a fourth aspect of the present invention, in the work vehicle according to the second aspect, the end surface of the bottom portion of the driving wheel body is formed in a trapezoidal shape, the trapezoidal inner peripheral side width of the bottom portion and the claw portion of the core metal body. The difference between the trapezoidal outer peripheral side width of the tooth bottom and the inner width of the claw tip end side of the metal core is greater than the difference of the inner width on the root side.

請求項1によると、エンジンを搭載する走行機体と、前記走行機体の下側に設けるトラックフレームと、前記トラックフレームに駆動輪体及び従動輪体を介して装着する左右の走行クローラとを備え、前記駆動輪体に歯合させる複数の芯金体を前記走行クローラに設ける作業車両において、前記走行クローラのうち左右幅の中央部にゴムベルト体を設け、前記駆動輪体の輪状部と従動輪体の輪状部が前記ゴムベルト体に当接して、前記走行クローラを回転するように構成したものであるから、軽負荷時、前記駆動輪体の輪状部と前記ゴムベルト体の摩擦駆動にて、前記駆動輪体の回転力が前記走行クローラに伝達される。一方、重負荷時、前記芯金体と前記駆動輪体の歯体の金属接触にて、前記駆動輪体の回転力が前記走行クローラに伝達される。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、前記従動輪体が接触凸部上を常に転動して、前記従動輪体部から発生する金属接触音を低減できる。   According to claim 1, comprising: a traveling machine body on which an engine is mounted; a track frame provided on the lower side of the traveling machine body; and left and right traveling crawlers attached to the track frame via a driving wheel body and a driven wheel body, In the work vehicle in which the traveling crawler is provided with a plurality of metal cores to be engaged with the driving wheel body, a rubber belt body is provided in a central portion of the lateral width of the traveling crawler, and the ring-shaped portion and the driven wheel body of the driving wheel body Since the ring-shaped portion of the driving wheel is in contact with the rubber belt body and the traveling crawler is rotated, the driving is performed by the friction drive between the ring-shaped portion of the driving wheel body and the rubber belt body at a light load. The rotational force of the ring body is transmitted to the traveling crawler. On the other hand, at the time of heavy load, the rotational force of the driving wheel body is transmitted to the traveling crawler by the metal contact between the metal core and the tooth body of the driving wheel body. 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 body always rolls on the contact convex portion, and the metal contact sound generated from the driven wheel body portion can be reduced.

請求項2によると、前記走行クローラ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を設け、前記走行クローラの内周面に前記接触凸部を一体的に形成し、前記駆動輪体の輪状部としての歯底部と前記従動輪体の輪状部としての外周面が前記接触凸部上にて回転するように構成したものであるから、軽負荷時、前記駆動輪体の歯底部と前記接触凸部の摩擦駆動にて、前記駆動輪体の回転力が前記走行クローラに伝達される。即ち、軽負荷時の駆動騒音を低減できる。前記駆動輪体または前記芯金体の摩耗を防止できる。一方、重負荷時、前記芯金体と前記駆動輪体の歯の金属接触にて、前記駆動輪体の回転力が前記走行クローラに伝達される。即ち、前記走行クローラのたわみまたはへたりによる駆動損失を低減できる。前記駆動輪体の歯とびを防止できる。さらに、前記従動輪体が前記接触凸部上を常に転動することにより、前記従動輪体部から発生する金属接触音を低減できる。   According to a second aspect of the present invention, a contact convex portion as a rubber belt body is provided in a central portion of the lateral width of the traveling crawler, the contact convex portion is integrally formed on an inner peripheral surface of the traveling crawler, and the driving wheel body. Since the tooth bottom portion as the ring-shaped portion and the outer peripheral surface as the ring-shaped portion of the driven wheel body are configured to rotate on the contact convex portion, at the time of light load, the tooth bottom portion of the driving wheel body The rotational force of the driving wheel body is transmitted to the traveling crawler by the friction drive of the contact convex portion. That is, it is possible to reduce drive noise at light load. Wear of the driving wheel body or the metal core can be prevented. On the other hand, at the time of heavy load, the rotational force of the driving wheel body is transmitted to the traveling crawler by the metal contact between the metal core and the teeth of the driving wheel body. That is, it is possible to reduce drive loss due to deflection or sag of the traveling crawler. It is possible to prevent skipping of the driving wheel body. Furthermore, when the driven wheel always rolls on the contact convex portion, it is possible to reduce metal contact sound generated from the driven wheel body.

請求項3によると、前記駆動輪体のうち外周部の両側に左右の歯体を突出させ、前記左右の歯体の間に前記歯底部を形成し、前記左右の歯体に前記芯金体を金属接触させ、前記左右の歯体の内側面と前記歯底部とに前記接触凸部を接触させるように構成したものであるから、前記走行クローラに横滑り力が作用したときにも、前記左右の歯体の内側面と接触凸部との接触によって、前記駆動輪体から前記走行クローラが外れるのを簡単に防止できる。前記駆動輪体の外周全体に形成される歯底部と前記走行クローラの接触凸部との接触によって、前記歯底部と接触凸部との摩擦面を広く形成でき、前記歯底部と接触凸部との接触面圧を低下させることができ、前記歯底部または接触凸部の摩耗を抑制できる。   According to claim 3, left and right tooth bodies are protruded on both sides of an outer peripheral portion of the drive wheel body, the tooth bottom portion is formed between the left and right tooth bodies, and the core metal body is formed on the left and right tooth bodies. Is made to contact the metal, and the contact convex portion is brought into contact with the inner side surfaces of the left and right tooth bodies and the bottom of the tooth. Therefore, even when a side slip force acts on the traveling crawler, It is possible to easily prevent the traveling crawler from being detached from the drive wheel body by the contact between the inner surface of the tooth body and the contact convex portion. A friction surface between the tooth bottom part and the contact convex part can be widely formed by contact between the tooth bottom part formed on the entire outer periphery of the driving wheel body and the contact convex part of the traveling crawler, and the tooth bottom part and the contact convex part The contact surface pressure can be reduced, and wear of the tooth bottom part or the contact convex part can be suppressed.

請求項4によると、前記駆動輪体の歯底部端面を台形状に形成し、前記歯底部の台形内周側幅と前記芯金体の爪部根元側の内幅の差よりも、前記歯底部の台形外周側幅と前記芯金体の爪部先端側の内幅の差が大きくなるように構成したものであるから、前記走行クローラに横滑り力が作用したときにも、前記駆動輪体から前記走行クローラが外れるのを簡単に防止できる。   According to claim 4, the end surface of the bottom of the driving wheel body is formed in a trapezoidal shape, and the tooth is larger than the difference between the trapezoidal inner peripheral side width of the tooth bottom and the inner width of the claw part base side of the metal core. Since the difference between the trapezoid outer peripheral side width of the bottom part and the inner width of the claw part tip side of the metal core is increased, the driving wheel body can be used even when a side-slip force acts on the traveling crawler. Can easily prevent the traveling crawler from coming off.

本発明の実施形態を示すトラクタの側面図である。It is a side view of the tractor which shows the embodiment of the present invention. 同平面図である。It is the same top view. クローラ走行装置の側面拡大図である。It is a side enlarged view of a crawler traveling device. トラックフレーム部の側面図である。It is a side view of a track frame part. クローラ走行装置の右後方視の分解斜視図である。It is a disassembled perspective view of the crawler traveling device in the right rear view. クローラ走行装置の左後方視の分解斜視図である。It is a disassembled perspective view of the crawler traveling device in the left rear view. トラックフレーム支持部の右後方視の分解斜視図である。It is a disassembled perspective view of the right rear view of a track frame support part. トラックフレーム支持部の左側視の分解斜視図である。It is a disassembled perspective view of the left side view of a track frame support part. クローラ走行装置の後方視の断面説明図である。It is a cross-sectional explanatory drawing of the back view of a crawler traveling apparatus. トラックフレーム支持部の後方視の断面説明図である。It is sectional explanatory drawing of the back view of a track frame support part. トラックフレーム支持部の拡大断面図である。It is an expanded sectional view of a track frame support part. 図11の分解説明図である。It is decomposition | disassembly explanatory drawing of FIG. 転動輪部の後方視の拡大説明図である。It is expansion explanatory drawing of the rear view of a rolling wheel part. 駆動輪体部の後方視の拡大断面図である。It is an expanded sectional view of a driving wheel body part in the back view. 駆動輪体部の部分拡大説明図である。It is a partial expanded explanatory view of a driving wheel body part. 駆動輪体部の部分斜視図である。It is a fragmentary perspective view of a driving wheel body part. 駆動輪体部の分解説明図である。It is decomposition | disassembly explanatory drawing of a driving wheel body part. 走行クローラと駆動輪体部の部分拡大説明図である。It is a partial expanded explanatory view of a traveling crawler and a driving wheel body part. 駆動輪体部の取付け変形例を示す要部拡大説明図である。It is a principal part expanded explanatory view which shows the attachment modification of a drive wheel body part. 走行クローラの部分拡大断面図である。It is a partial expanded sectional view of a traveling crawler. 走行クローラの変形例を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the modification of a driving | running | working crawler. 駆動輪体部の変形例を示す要部拡大説明図である。It is a principal part enlarged explanatory view which shows the modification of a drive wheel body part. 走行クローラと駆動輪体部の変形例を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the modification of a driving | running | working crawler and a driving wheel body part. 走行クローラと転動輪部の変形例を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the modification of a driving | running | working crawler and a rolling wheel part. 駆動輪体における部分輪体の連結構造を示す要部説明図である。It is principal part explanatory drawing which shows the connection structure of the partial ring body in a drive wheel body. 走行クローラと駆動輪体の配置を示す要部説明図である。It is principal part explanatory drawing which shows arrangement | positioning of a driving | running | working crawler and a driving wheel body. 転動輪部の軸受構造を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the bearing structure of a rolling wheel part. 転動輪部の軸受構造の変形例を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the modification of the bearing structure of a rolling wheel part. 転動輪部の軸受構造の変形例を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the modification of the bearing structure of a rolling wheel part. 従動輪部の軸受構造を示す要部拡大説明図である。It is principal part expansion explanatory drawing which shows the bearing structure of a driven wheel part.

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. It 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。なお、駆動輪体16のスプロケット歯底部89の断面端面形状は、スプロケット歯底部89の台形内周側幅aよりもスプロケット歯底部89の台形外周側幅cを小さくした(c<a)台形状である。   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. Note that the cross-sectional end face shape of the sprocket tooth bottom 89 of the drive wheel body 16 is such that the trapezoid outer peripheral side width c of the sprocket tooth bottom 89 is smaller than the trapezoid inner peripheral side width a of the sprocket tooth bottom 89 (c <a). It is.

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。   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.

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 has a high inside. 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, and uneven wear of the traveling crawler 25 or the rolling wheels 26 can be easily performed. 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-sliding 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, so that wrapping of grass or the like, or intrusion of muddy water is suppressed, and the dust seal 115 is damaged. 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.

8 エンジン
11 走行機体
16 駆動輪体
17 トラックフレーム
21 前従動輪体
23 後従動輪体
25 走行クローラ
89 スプロケット歯底部(輪状部)
90 スプロケット歯体(左右の歯体)
94a 接触凸部(ゴムベルト体)
95 芯金体
a スプロケット歯底部の台形内周側幅
b 芯金体の爪部の根元側内幅
c スプロケット歯底部の台形外周側幅
d 芯金体の爪部の先端側内幅
8 Engine 11 Traveling machine body 16 Driving wheel body 17 Track frame 21 Front driven wheel body 23 Rear driven wheel body 25 Traveling crawler 89 Sprocket tooth bottom (ring-shaped part)
90 Sprocket tooth bodies (left and right tooth bodies)
94a Contact convex part (rubber belt)
95 Metal core a Trapezoid inner peripheral side width b of sprocket tooth bottom Root side inner width c of metal core claw Trapezoid outer peripheral side width of sprocket tooth bottom part Inner end side inner width of metal core claw

Claims (4)

エンジンを搭載する走行機体と、前記走行機体の下側に設けるトラックフレームと、前記トラックフレームに駆動輪体及び従動輪体を介して装着する左右の走行クローラとを備え、前記駆動輪体に歯合させる複数の芯金体を前記走行クローラに設ける作業車両において、
前記走行クローラのうち左右幅の中央部にゴムベルト体を設け、前記駆動輪体の輪状部と従動輪体の輪状部が前記ゴムベルト体に当接して、前記走行クローラを回転するように構成したことを特徴とする作業車両。
A traveling machine body on which an engine is mounted; a track frame provided on a lower side of the traveling machine body; and left and right traveling crawlers attached to the track frame via a driving wheel body and a driven wheel body; In a work vehicle in which a plurality of metal cores to be combined are provided on the traveling crawler,
A rubber belt body is provided at a central portion of the lateral width of the traveling crawler, and the traveling crawler is configured to rotate by contacting the rubber belt body with the annular portion of the driving wheel body and the annular portion of the driven wheel body. A working vehicle characterized by
前記走行クローラ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を設け、前記走行クローラの内周面に前記接触凸部を一体的に形成し、前記駆動輪体の輪状部としての歯底部と前記従動輪体の輪状部としての外周面が前記接触凸部上にて回転するように構成したことを特徴とする請求項1に記載の作業車両。   A contact convex portion as a rubber belt body is provided in a central portion of the lateral width of the traveling crawler, the contact convex portion is integrally formed on an inner peripheral surface of the traveling crawler, and teeth as a ring-shaped portion of the driving wheel body The work vehicle according to claim 1, wherein an outer peripheral surface as a ring-shaped portion of the bottom portion and the driven wheel body is configured to rotate on the contact convex portion. 前記駆動輪体のうち外周部の両側に左右の歯体を突出させ、前記左右の歯体の間に前記歯底部を形成し、前記左右の歯体に前記芯金体を金属接触させ、前記左右の歯体の内側面と前記歯底部とに前記接触凸部を接触させるように構成したことを特徴とする請求項2に記載の作業車両。   Left and right tooth bodies are protruded on both sides of the outer peripheral portion of the drive wheel body, the tooth bottom portion is formed between the left and right tooth bodies, the metal core is in metal contact with the left and right tooth bodies, and The work vehicle according to claim 2, wherein the contact convex portion is configured to contact the inner side surfaces of the left and right tooth bodies and the tooth bottom portion. 前記駆動輪体の歯底部端面を台形状に形成し、前記歯底部の台形内周側幅と前記芯金体の爪部根元側の内幅の差よりも、前記歯底部の台形外周側幅と前記芯金体の爪部先端側の内幅の差が大きくなるように構成したことを特徴とする請求項2に記載の作業車両。   The bottom end face of the driving wheel body is formed in a trapezoidal shape, and the trapezoid outer peripheral side width of the tooth bottom part is larger than the difference between the trapezoid inner peripheral side width of the tooth bottom part and the inner width of the base part of the claw part of the metal core. 3. The work vehicle according to claim 2, wherein a difference in inner width between the tip and the claw part of the metal core is increased.
JP2011130528A 2011-06-10 2011-06-10 Working vehicle Pending JP2013001129A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014213807A (en) * 2013-04-26 2014-11-17 株式会社クボタ Crawler travel device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06263067A (en) * 1993-03-15 1994-09-20 Ohtsu Tire & Rubber Co Ltd :The Elastic crawler device
WO2011040606A1 (en) * 2009-10-01 2011-04-07 株式会社ブリヂストン Sprocket, and rubber crawler assembly provided therewith
WO2011045993A1 (en) * 2009-10-13 2011-04-21 株式会社クボタ Crawler travel unit
WO2012137887A1 (en) * 2011-04-05 2012-10-11 株式会社ブリヂストン Crawler travel device and elastic crawler

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06263067A (en) * 1993-03-15 1994-09-20 Ohtsu Tire & Rubber Co Ltd :The Elastic crawler device
WO2011040606A1 (en) * 2009-10-01 2011-04-07 株式会社ブリヂストン Sprocket, and rubber crawler assembly provided therewith
WO2011045993A1 (en) * 2009-10-13 2011-04-21 株式会社クボタ Crawler travel unit
WO2012137887A1 (en) * 2011-04-05 2012-10-11 株式会社ブリヂストン Crawler travel device and elastic crawler

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014213807A (en) * 2013-04-26 2014-11-17 株式会社クボタ Crawler travel device

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