JPS6332503Y2 - - Google Patents
Info
- Publication number
- JPS6332503Y2 JPS6332503Y2 JP1983075686U JP7568683U JPS6332503Y2 JP S6332503 Y2 JPS6332503 Y2 JP S6332503Y2 JP 1983075686 U JP1983075686 U JP 1983075686U JP 7568683 U JP7568683 U JP 7568683U JP S6332503 Y2 JPS6332503 Y2 JP S6332503Y2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- gear
- rotating shaft
- rotating
- shifter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000005540 biological transmission Effects 0.000 claims description 66
- 230000007246 mechanism Effects 0.000 claims description 21
- 238000000605 extraction Methods 0.000 claims description 3
- 230000008859 change Effects 0.000 description 5
- 210000000078 claw Anatomy 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000009333 weeding Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
Landscapes
- Arrangement And Driving Of Transmission Devices (AREA)
- Arrangement Of Transmissions (AREA)
Description
【考案の詳細な説明】
本考案は、主として畦間を走行させながら中耕
除草や中耕培土等の管理作業を行うに適した小型
の移動農機の伝動構造に関する。[Detailed Description of the Invention] The present invention relates to a transmission structure for a small-sized mobile agricultural machine suitable for performing management work such as weeding and tilling soil during intercultivation while mainly traveling between furrows.
エンジンからの動力を車輪とロータリー爪とに
分岐伝動するに当たつて、従来は、実開昭54−
174128号公報に示される如く、ベベルギヤ式の正
逆転切換機構の後に設けられた車輪への伝動軸
と、ロータリー爪への伝動軸とが２重軸構造に構
成され、且つ、両軸夫々に変速ギヤが設けられて
いた為、正逆転切換機構を正転側に切換えて、任
意の変速ギヤを操作すると、車輪とロータリー爪
とが共に同調変速されるものであつた。このよう
に、車輪の変速に伴つてロータリー爪が変速駆動
されるものでは、車輪の走行速度を遅くして、ロ
ータリー爪の回転速度を速くした作業が行えない
欠点があり、又、正逆転切換機構と変速機構とを
備えただけの構造に過ぎないから、ロータリー爪
を停止して車輪のみを駆動することができないと
いう不都合もあつた。 Conventionally, when transmitting the power from the engine to the wheels and the rotary pawl,
As shown in Publication No. 174128, the transmission shaft to the wheels provided after the bevel gear type forward/reverse switching mechanism and the transmission shaft to the rotary pawl are configured in a double shaft structure, and both shafts have a speed changer. Since gears were provided, when the forward/reverse switching mechanism was switched to the forward rotation side and an arbitrary speed change gear was operated, both the wheels and the rotary pawls were shifted in synchronism. In this way, when the rotary pawl is driven at variable speeds as the wheels change speed, there is a drawback that work cannot be performed by slowing down the running speed of the wheels and increasing the rotational speed of the rotary pawl. Since the structure is merely equipped with a mechanism and a transmission mechanism, there is also the inconvenience that it is not possible to stop the rotary pawl and drive only the wheels.
本考案は、車輪とロータリー爪への伝動構造を
工夫することによつて上記欠点を解消するととも
に、その為の構造を製作加工の容易なものから得
しめ、さらには、ミツシヨンケース内の伝動機構
の配置を工夫してミツシヨンケースの横巾のコン
パクト化をはからんとすることを目的とする。 The present invention solves the above drawbacks by devising a transmission structure for the wheels and rotary pawls, and also provides a structure that is easy to manufacture and process. The purpose is to reduce the width of the transmission case by devising the arrangement of the mechanism.
上記目的を達成する為に講じた本考案の特徴構
成は、トランスミツシヨンケース内に互いに平行
な前後向き姿勢で二本の回転軸を支承し、その二
本の回転軸のうち、一方の回転軸に対して直交す
る横向き姿勢で走行用伝動軸を設け、その走行用
伝動軸と前記一方の回転軸とをベベルギヤ対を介
して連動連結するとともに、この一方の回転軸の
後端部に動力取出軸を同芯状に配置して設け、こ
の動力取出軸と前記他方の回転軸とをギヤを介し
て連動連結するとともに、前記二本の回転軸間に
ギヤ式変速機構を設け、さらに、前記他方の回転
軸に主クラツチ用シフターと前記ギヤ式変速機構
の変速操作用シフターならびに前記動力取出軸に
対する伝動クラツチ用シフターを各々、摺動自在
に嵌合保持し、さらに、前記一方の回転軸に装着
されたギヤ式変速機構のギヤと、前記一方の回転
軸と同芯上に配置され、且つ、他方の回転軸から
前記連動ギヤを介して駆動される前記動力取出軸
の入力ギヤとの間隔を長くして、その間隔内に、
前記一方の回転軸と走行用伝動軸とを連動連結す
る前記ベベルギヤを配置した点にあり、斯かる構
成から次の作用効果を奏する。 The characteristic configuration of the present invention, which was taken to achieve the above object, is that two rotating shafts are supported in the transmission case in a mutually parallel front-back orientation, and one of the two rotating shafts is rotated. A traveling power transmission shaft is provided in a horizontal position orthogonal to the shaft, and the traveling power transmission shaft and the one rotating shaft are interlocked and connected via a pair of bevel gears, and a power source is connected to the rear end of this one rotating shaft. A power extraction shaft is arranged concentrically, the power extraction shaft and the other rotating shaft are interlocked and connected via a gear, and a gear type transmission mechanism is provided between the two rotating shafts, and further, A shifter for the main clutch, a shifter for shifting the gear type transmission mechanism, and a shifter for a power transmission clutch for the power take-off shaft are each slidably fitted and held on the other rotating shaft; and an input gear of the power take-off shaft that is arranged coaxially with the one rotating shaft and is driven from the other rotating shaft via the interlocking gear. Increase the interval and within that interval,
The present invention is characterized by the arrangement of the bevel gear that interlocks and connects the one rotating shaft and the traveling power transmission shaft, and this configuration provides the following effects.
すなわち、車輪への伝動軸としての一方の回転
軸とロータリー爪への伝動軸としての他方の回転
軸を別軸に構成して、両者間にギヤ式変速機構を
設けたから、ロータリー爪への伝動軸としての他
方の回転軸を定速回転にした状態で、車輪への伝
動軸としての一方の回転軸をギヤ式変速機構を介
して変速することができ、これによつて、ロータ
リー爪を定速回転させた状態で車輪の走行速度を
変更することができることから、車輪の走行速度
を遅くしてもロータリー爪を相対的に高速回転す
ることができ、良好な除草作業が行える。そし
て、ギヤ式変速機構よりも伝動下手側にロータリ
ー爪のクラツチ用シフター、つまり、ロータリー
爪に対するクラツチを設けたから、車輪を駆動し
た状態でロータリー爪を停止することができ、圃
場端での機体方向転換を、ロータリー爪の回転を
停止した状態で安全に行える。 In other words, one rotating shaft as the transmission shaft to the wheel and the other rotating shaft as the transmission shaft to the rotary pawl are configured as separate shafts, and a gear type transmission mechanism is installed between them, so that the transmission to the rotary pawl is While the other rotating shaft rotates at a constant speed, one rotating shaft serving as a transmission shaft to the wheels can be changed in speed via a gear type transmission mechanism, thereby allowing the rotary pawl to be rotated at a constant speed. Since the running speed of the wheels can be changed while the wheels are rotating quickly, the rotary claws can be rotated at a relatively high speed even if the running speed of the wheels is slowed down, and good weeding work can be performed. In addition, we installed a shifter for the rotary pawl clutch on the lower transmission side of the gear type transmission mechanism, in other words, a clutch for the rotary pawl, so the rotary pawl can be stopped while the wheels are being driven. Conversion can be performed safely with the rotary claw stopped rotating.
そして、ギヤ式変速機構を切換え操作する時に
用いる主クラツチ用シフター、並びに、ギヤ式変
速機構の変速操作用シフター、さらに、ロータリ
ー爪に対する伝動クラツチ用シフターを、ロータ
リー爪への伝動軸として他方の回転軸側に集めて
配設してあるから、例えば、車輪への伝動軸とし
ての一方の回転軸と、ロータリー爪への伝動軸と
しての他方の回転軸とに混在させて配設する場合
に比して、軸にシフターの為のスプライン加工を
施す場合に、両軸にスプライン加工を施す必要が
なく、伝動構造の製作加工の容易化が図れる。 The shifter for the main clutch used when switching the gear type transmission mechanism, the shifter for the gear change operation of the gear type transmission mechanism, and the shifter for the transmission clutch for the rotary pawl are used as the transmission shaft for the rotary pawl to rotate the other side. Because they are arranged together on the shaft side, for example, compared to the case where one rotating shaft is used as the transmission shaft for the wheel, and the other rotational shaft is used as the transmission shaft for the rotary pawl, they are arranged together. Therefore, when performing spline processing on the shaft for the shifter, there is no need to perform spline processing on both shafts, and the manufacturing process of the transmission structure can be facilitated.
さらに、一方の回転軸に装着されたギヤ式変速
機構のギヤと、前記一方の回転軸と同芯上に配置
され、且つ、他方の回転軸から前記連動ギヤを介
して駆動される前記動力取出軸の入力ギヤとの間
隔を長くして、その間隔内に、前記一方の回転軸
と走行用伝動軸とを連動連結する前記ベベルギヤ
を配置したから、例えば、前記一方の回転軸に装
着されたギヤ式変速機構のギヤと、前記一方の回
転軸と同芯上に配置され、且つ、他方の回転軸か
ら連動ギヤを介して駆動される動力取出軸の入力
ギヤとの間隔を狭くした場合のように、ミツシヨ
ンケースの横巾が大型化することがない。 Furthermore, a gear of a gear type transmission mechanism mounted on one rotating shaft, and the power output that is arranged coaxially with the one rotating shaft and is driven from the other rotating shaft via the interlocking gear. Since the distance between the shaft and the input gear is lengthened, and the bevel gear that interlocks and connects the one rotating shaft and the traveling transmission shaft is arranged within that distance, for example, the bevel gear that is attached to the one rotating shaft When the distance between the gear of the gear type transmission mechanism and the input gear of the power take-off shaft that is arranged concentrically with the one rotating shaft and is driven from the other rotating shaft via an interlocking gear is narrowed. As a result, the width of the transmission case does not become large.
つまり、前記一方の回転軸に装着されたギヤ式
変速機構のギヤと、前記一方の回転軸と同芯上に
配置され、且つ、他方の回転軸から連動ギヤを介
して駆動される動力取出軸の入力ギヤとの間隔を
狭くすると、走行用伝動軸を動力取出軸の入力ギ
ヤを越えて動力取出軸側に配置して、一方の回転
軸に装着のベベルギヤを大径にして、前記動力取
出軸の入力ギヤを避けて走行用伝動軸のベベルギ
ヤを設けなければならないことから、ミツシヨン
ケースの横巾が大型化するが、一方の回転軸に装
着されたギヤ式変速機構のギヤと、前記一方の回
転軸と同芯上に配置され、且つ、他方の回転軸か
ら連動ギヤを介して駆動される動力取出軸の入力
ギヤとの間隔を長くして、その間隔内に、前記前
記一方の回転軸と走行用伝動軸とを連動連結する
ベベルギヤを配置すれば、一方の回転軸に装着の
ベベルギヤを小さくして、走行用伝動軸のベベル
ギヤを一方の回転軸に近付けて配置し得ることか
ら、ミツシヨンケースの横巾のコンパクト化をは
かれるに至つた。 That is, a gear of a gear type transmission mechanism attached to the one rotating shaft, and a power take-off shaft that is arranged coaxially with the one rotating shaft and is driven from the other rotating shaft via an interlocking gear. By narrowing the distance between the input gear and the power output shaft, the traveling transmission shaft is placed beyond the input gear of the power output shaft and on the power output shaft side, and the bevel gear attached to one rotating shaft is made larger in diameter. Since the bevel gear of the driving transmission shaft must be provided to avoid the input gear of the shaft, the width of the transmission case becomes larger. The distance between the input gear and the power take-off shaft that is arranged concentrically with one of the rotational shafts and is driven from the other rotational shaft via an interlocking gear is increased, and within that distance, said one of said By arranging a bevel gear that interlocks and connects the rotating shaft and the driving power transmission shaft, the bevel gear attached to one of the rotating shafts can be made smaller and the bevel gear of the traveling power transmission shaft can be placed closer to one of the rotating shafts. This led to the reduction of the width of the transmission case.
以下、本考案の実施例を図面に基いて説明す
る。 Embodiments of the present invention will be described below with reference to the drawings.
第１図で示す一輪歩行型作業機は、伝動ケース
１４の下部一側に駆動車輪Ｗが支持され、前記伝
動ケース１４の上部にトランスミツシヨンケース
１及びエンジンＥが塔載され、前記駆動車輪Ｗ後
部にロータリー爪等からなる作業機１５が連設さ
れている。 In the single-wheel walking type work machine shown in FIG. 1, a drive wheel W is supported on one side of the lower part of a transmission case 14, a transmission case 1 and an engine E are mounted on the upper part of the transmission case 14, and the drive wheel W is supported on one side of the lower part of the transmission case 14. A working device 15 consisting of a rotary claw or the like is connected to the rear of W.
前記エンジンＥからトランスミツシヨンケース
１を介しての車輪Ｗ及び作業機１５への伝動構造
を第２図及び第３図に基づいて詳述する。カム軸
１６を出力軸とするエンジンＥ出力を受けるトラ
ンスミツシヨンケース１内の入力軸１７の回転を
受けて回転する互いに平行な前後向き姿勢で、同
一平面内に位置するように支承された二本の回転
軸２，３のうち、一方の回転軸２とこれに軸芯が
直交する横向き姿勢で前記伝動ケース１４に支承
された走行用伝動軸４とがベベルギヤ対５，６を
介して連動連結されているとともに、この一方の
回転軸２の後端部に、前記回転軸３に入り付勢さ
れた伝動クラツチ用シフター１３とともに嵌合保
持された駆動ギヤ９に噛合うギヤー８を一体連設
した後方へ向つて突出する動力取出軸７が同芯状
に配置支承されている。又、前記回転軸２の後端
は前記動力取出軸７の肉厚内でベアリング支承さ
れている。この動力取出軸７はベベルギヤ対２０
及び２１，２１を介して作業機１５に動力伝達さ
れるものであるから、車輪Ｗ回転速度と独立し
て、作業機１５の回転速度を設定出来る。 The transmission structure from the engine E to the wheels W and the work implement 15 via the transmission case 1 will be described in detail with reference to FIGS. 2 and 3. The two motors are supported so as to be located in the same plane in a parallel front-back posture and rotate in response to the rotation of the input shaft 17 in the transmission case 1 which receives the engine E output with the camshaft 16 as the output shaft. Among the rotating shafts 2 and 3 of the book, one rotating shaft 2 and the traveling transmission shaft 4 supported by the transmission case 14 in a horizontal position with the axis perpendicular to the rotating shaft 2 are interlocked via a pair of bevel gears 5 and 6. A gear 8 is integrally connected to the rear end of one of the rotating shafts 2 and meshes with a drive gear 9 that is fitted and held together with a power transmission clutch shifter 13 that enters the rotating shaft 3 and is energized. A power take-off shaft 7 protruding toward the rear is arranged and supported concentrically. Further, the rear end of the rotary shaft 2 is supported by a bearing within the thickness of the power take-off shaft 7. This power take-off shaft 7 has a bevel gear pair 20
Since the power is transmitted to the working machine 15 via the wheels W and 21, 21, the rotational speed of the working machine 15 can be set independently of the wheel W rotational speed.
前記二本の回転軸２，３間に構成されるギヤ式
変速機構１０は、前記入力軸１７にニードルベア
リングを介して支承されたギヤ２２と減速連動す
る前記回転軸３に固着されたギヤ２３に入り付勢
された主クラツチ用シフター１１が並設され、前
記回転軸３において、前記ギヤ２３より後側に変
速操作用シフター１２が摺動自在に嵌合保持さ
れ、このシフター１２の切換操作によつて、低速
時は前記回転軸２にニードルベアリングを介して
支承の中間第１ギヤ２４と高速時は前記回転軸３
にニードルベアリングを介して支承の中間第２ギ
ヤ２５とに接続され、最終的に前記出力軸２に固
着された最終ギヤ２６に連動される。このように
各シフター１１，１２，１３が前記減速された回
転軸３側に摺動自在に嵌合保持されているので、
クラツチON−OFF時の衝撃を低減化できる。 The gear type transmission mechanism 10 configured between the two rotating shafts 2 and 3 includes a gear 22 supported by the input shaft 17 via a needle bearing, and a gear 23 fixed to the rotating shaft 3 that is interlocked for deceleration. A shifter 11 for the main clutch which is biased and energized is arranged in parallel, and a shifter 12 for gear change operation is slidably fitted and held at the rear side of the gear 23 on the rotating shaft 3, and the shifter 12 for the shifter 12 is operated to switch the gear. Accordingly, when the speed is low, the intermediate first gear 24 is supported by the rotating shaft 2 through a needle bearing, and when the speed is high, the rotating shaft 3 is supported.
It is connected to an intermediate second gear 25 of the support via a needle bearing, and is finally interlocked with a final gear 26 fixed to the output shaft 2. In this way, each shifter 11, 12, 13 is slidably fitted and held on the side of the decelerated rotating shaft 3, so that
The impact when the clutch is turned on and off can be reduced.
尚、実用新案登録請求の範囲の項に図面との対
照を便利にする為に符号を記すが、該記入により
本考案は添付図面の構造に限定されるものではな
い。 Note that although reference numerals are written in the claims section of the utility model registration for convenience of comparison with the drawings, the present invention is not limited to the structure of the attached drawings by such entry.
図面は本考案に係る移動農機の伝動構造の実施
例を示し、第１図は一輪歩行型作業機を示す斜視
図、第２図は全体横断平面図、第３図は全体縦断
側面図である。
１……トランスミツシヨンケース、２，３……
回転軸、４……走行用伝動軸、５，６……ベベル
ギヤ対、７……動力取出軸、８，９……ギヤ、１
０……ギヤ式変速機構、１１……主クラツチ用シ
フター、１２……変速操作用シフター、１３……
伝動クラツチ用シフター、２４……ギヤ式変速機
構のギヤ。
The drawings show an embodiment of the power transmission structure of a mobile agricultural machine according to the present invention, in which Fig. 1 is a perspective view showing a single-wheeled walking type working machine, Fig. 2 is an overall cross-sectional plan view, and Fig. 3 is an overall vertical cross-sectional side view. . 1... Transmission case, 2, 3...
Rotating shaft, 4...Transmission shaft for traveling, 5, 6...Bevel gear pair, 7...Power take-off shaft, 8, 9...Gear, 1
0... Gear type transmission mechanism, 11... Shifter for main clutch, 12... Shifter for speed change operation, 13...
Shifter for transmission clutch, 24... Gear of gear type transmission mechanism.
Claims (1)
な前後向き姿勢で二本の回転軸２，３を支承
し、その二本の回転軸２，３のうち、一方の回
転軸２に対して直交する横向き姿勢で走行用伝
動軸４を設け、その走行用伝動軸４と前記一方
の回転軸２とをベベルギヤ対５，６を介して連
動連結するとともに、この一方の回転軸２の後
端部に動力取出軸７を同芯状に配置して設け、
この動力取出軸７と前記他方の回転軸３とをギ
ヤ８，９を介して連動連結するとともに、前記
二本の回転軸２，３間にギヤ式変速機構１０を
設け、さらに、前記他方の回転軸３に主クラツ
チ用シフター１１と前記ギヤ式変速機構１０の
変速操作用シフター１２ならびに前記動力取出
軸７に対する伝動クラツチ用シフター１３を
各々、摺動自在に嵌合保持し、さらに、前記一
方の回転軸２に装着されたギヤ式変速機構１０
のギヤ２４と、前記一方の回転軸２と同芯上に
配置され、且つ、他方の回転軸３から前記連動
ギヤ９を介して駆動される前記動力取出軸７の
入力ギヤ８との間隔を長くして、その間隔内
に、前記一方の回転軸２と走行用伝動軸４とを
連動連結する前記ベベルギヤ５，６を配置して
ある移動農機の伝動構造。 ２ 前記二本の回転軸２，３が同一平面内に位置
するように支承されている実用新案登録請求の
範囲第１項に記載の移動農機の伝動構造。[Claims for Utility Model Registration] 1. Two rotating shafts 2 and 3 are supported in a transmission case 1 in a mutually parallel front-back orientation, and one of the two rotating shafts 2 and 3 is rotated. A traveling power transmission shaft 4 is provided in a horizontal position orthogonal to the shaft 2, and the traveling power transmission shaft 4 and the one rotating shaft 2 are interlocked and connected via a pair of bevel gears 5 and 6, and the rotation of this one is A power take-off shaft 7 is arranged concentrically at the rear end of the shaft 2, and
This power extraction shaft 7 and the other rotating shaft 3 are interlocked and connected via gears 8 and 9, and a gear type transmission mechanism 10 is provided between the two rotating shafts 2 and 3. A shifter 11 for the main clutch, a shifter 12 for shift operation of the gear type transmission mechanism 10, and a shifter 13 for the power transmission clutch for the power take-off shaft 7 are each slidably fitted and held on the rotating shaft 3, and A gear type transmission mechanism 10 attached to a rotating shaft 2 of
and the input gear 8 of the power take-off shaft 7 which is arranged coaxially with the one rotating shaft 2 and is driven from the other rotating shaft 3 via the interlocking gear 9. A power transmission structure for a mobile agricultural machine, in which the bevel gears 5 and 6 are arranged to interlock and connect the one rotary shaft 2 and the traveling power transmission shaft 4 within a long interval. 2. The power transmission structure for a mobile agricultural machine according to claim 1, wherein the two rotating shafts 2 and 3 are supported so as to be located in the same plane.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7568683U JPS59179123U (en) | 1983-05-18 | 1983-05-18 | Transmission structure of mobile agricultural machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7568683U JPS59179123U (en) | 1983-05-18 | 1983-05-18 | Transmission structure of mobile agricultural machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59179123U JPS59179123U (en) | 1984-11-30 |
| JPS6332503Y2 true JPS6332503Y2 (en) | 1988-08-30 |
Family
ID=30205749
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7568683U Granted JPS59179123U (en) | 1983-05-18 | 1983-05-18 | Transmission structure of mobile agricultural machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59179123U (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4327604Y1 (en) * | 1964-12-21 | 1968-11-15 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5933700Y2 (en) * | 1978-05-29 | 1984-09-19 | 井関農機株式会社 | power mobile machine |
-
1983
- 1983-05-18 JP JP7568683U patent/JPS59179123U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4327604Y1 (en) * | 1964-12-21 | 1968-11-15 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59179123U (en) | 1984-11-30 |
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