JP2000166301A - Power transmission system for walking type working machine - Google Patents

Power transmission system for walking type working machine

Info

Publication number
JP2000166301A
JP2000166301A JP10346307A JP34630798A JP2000166301A JP 2000166301 A JP2000166301 A JP 2000166301A JP 10346307 A JP10346307 A JP 10346307A JP 34630798 A JP34630798 A JP 34630798A JP 2000166301 A JP2000166301 A JP 2000166301A
Authority
JP
Japan
Prior art keywords
traveling
shaft
differential
working machine
traveling transmission
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.)
Pending
Application number
JP10346307A
Other languages
Japanese (ja)
Inventor
Hiroki Shin
裕樹 新
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yanmar Agribusiness Co Ltd
Original Assignee
Seirei Industry Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Seirei Industry Co Ltd filed Critical Seirei Industry Co Ltd
Priority to JP10346307A priority Critical patent/JP2000166301A/en
Publication of JP2000166301A publication Critical patent/JP2000166301A/en
Pending legal-status Critical Current

Links

Abstract

PROBLEM TO BE SOLVED: To provide a driving transmission gear for walking type working machine enabling a slow start in high speed position as well as in low speed position preventing sudden acceleration in starting time in high speed position that is existing in conventional walking type implement comprising a gear mechanism accompanying anxiety on sudden acceleration. SOLUTION: A differential gear 2b is installed in the driving transmission gear 2 of a walking type working machine comprising a gear mechanism on a transmission path from an input shaft to a final shaft, one of the output shaft of the differential gear 2b is set as a driving shaft and the other shaft is set as a control shaft, a loading device 2e is installed on the control shaft and prevents the sudden acceleration by relieving sudden driving of the output shaft in the cooperation with the differential gear 2b.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【発明の属する技術分野】本発明は、歯車機構から成る
走行伝動装置を有する歩行型作業機において、差動装置
を内蔵した走行伝動装置に関するものである。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a walking type working machine having a traveling transmission comprising a gear mechanism, and more particularly to a traveling transmission incorporating a differential.

【0002】[0002]

【従来の技術】従来の歩行型作業機で、原動機から走行
装置に歯車機構から成る走行伝動装置を介して動力伝達
するものが多々知られているが、この様な従来のものに
おいては、時として高速走行発進時に起こりやすい急発
進現象を潜在させ、該急発進現象は運転者に危険と不安
感を与え、操縦上の不便さや煩わしさを伴っている。
2. Description of the Related Art There are many known walking type working machines which transmit power from a prime mover to a traveling device via a traveling transmission device including a gear mechanism. This causes a sudden start phenomenon that is likely to occur at the start of high-speed traveling, and this sudden start phenomenon gives the driver a sense of danger and anxiety, and involves inconvenience and inconvenience in operation.

【0003】[0003]

【発明が解決しようとする課題】歯車機構から成る走行
伝動装置を有する歩行型作業機において、高速走行発進
時と言えども、急発進現象を防止した構成からなる装置
を歩行型作業機における走行伝動装置において提供する
ことである。
SUMMARY OF THE INVENTION In a walking type working machine having a traveling transmission device composed of a gear mechanism, an apparatus having a configuration in which a sudden start phenomenon is prevented even at the time of high-speed running start is used. In the device.

【0004】[0004]

【課題を解決するための手段】歯車機構から成る走行伝
動装置を有する歩行型作業機において、該走行伝動装置
の入力軸から最終軸部に至る伝動経路内に差動装置を内
蔵して、差動作用によって入力された駆動力が歯車列を
介しながらも瞬間的に一括して走行出力軸に掛からない
様にして、急発進現象を抑制する構成にした。
SUMMARY OF THE INVENTION In a walking type work machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a differential gear is provided. The driving force input for the operation is not applied to the traveling output shaft instantaneously while passing through the gear train, so that the sudden start phenomenon is suppressed.

【0005】歯車機構から成る走行伝動装置を有する歩
行型作業機において、該走行伝動装置の入力軸から最終
軸部に至る伝動経路内に差動装置を内蔵し、該差動装置
が有する2方向の出力側の一方を走行出力軸とし他方を
制御軸として、該制御軸の回転速度を制動する事によっ
て差動効果を拡大して、入力された駆動力を制御軸の回
転速度に係わり合わせて走行出力軸に伝動させる事によ
って、高速段においても緩発進から徐々に高速化するよ
うに構成した。
In a walk-behind type working machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a two-way differential of the differential device is provided. One of the output side is a traveling output shaft and the other is a control axis, the differential effect is enlarged by braking the rotation speed of the control shaft, and the input driving force is related to the rotation speed of the control shaft. By transmitting the power to the traveling output shaft, the speed is gradually increased from the slow start even at the high speed stage.

【0006】歯車機構から成る走行伝動装置を有する歩
行型作業機において、該走行伝動装置の入力軸から最終
軸部に至る伝動経路内に差動装置を内蔵し、該差動装置
が有する2方向の出力側の一方を走行出力軸とし他方を
制御軸として、該制御軸に回転速度に伴い負荷を発生す
る負荷装置を装着して、入力された駆動力を差動作用に
よって、入力初期は瞬間的に負荷が小さい制御軸に掛
け、制御軸の負荷に伴い走行出力軸に駆動力を伝達させ
る様に構成して急発進の緩和をする様にした。
In a walk-behind work machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a two-way device included in the differential device is provided. One of the output sides is a traveling output shaft and the other is a control axis, and a load device that generates a load according to the rotational speed is attached to the control axis, and the input driving force is instantaneously input by a differential action. The control shaft with a light load is applied, and the driving force is transmitted to the traveling output shaft in accordance with the load on the control shaft, thereby alleviating sudden start.

【0007】歯車機構から成る走行伝動装置を有する歩
行型作業機において、該走行伝動装置に差動装置を内蔵
して、この差動装置に装着された制御軸に回転速度に伴
い負荷を発生する負荷装置を装着し、該負荷装置を所定
の回転速度までは負荷を次第に増大し、所定の回転速度
以上になると最大負荷を発生して、制御軸の制動による
差動作用によって、走行出力軸の回転速度を制御する様
に構成して、入力された駆動力が走行出力軸に瞬間的に
一括して掛からない様に工夫した。
In a walk-behind working machine having a traveling transmission device composed of a gear mechanism, a differential device is incorporated in the traveling transmission device, and a load is generated on a control shaft mounted on the differential device in accordance with the rotational speed. A load device is mounted, and the load is gradually increased until the load device reaches a predetermined rotation speed, and when the load device exceeds the predetermined rotation speed, a maximum load is generated. The rotation speed is controlled so that the input driving force is not applied instantaneously and collectively to the traveling output shaft.

【0008】歯車機構から成る走行伝動装置を有する歩
行型作業機において、該走行伝動装置に差動装置を内蔵
して、この差動装置に装設された制御軸に負荷装置とし
て遠心力ブレ−キを装着して、差動装置と遠心力ブレ−
キを組合わせて出力制御をする様に構成し、所定の回転
速度以上で最大負荷を発生させ、逆に入力回転速度の低
下に伴い負荷を低減して制動力を解除する事で、軸支し
た制御軸の回転速度に係わって走行出力軸の回転速度を
制御する様に構成した。
In a walking type working machine having a traveling transmission device comprising a gear mechanism, a differential device is built in the traveling transmission device, and a centrifugal force brake is mounted on a control shaft mounted on the differential device as a load device. Attach the key and set the differential and centrifugal force
The maximum load is generated at a speed equal to or higher than a predetermined rotation speed, and conversely, the braking force is released by reducing the load as the input rotation speed decreases, thereby canceling the braking force. The rotation speed of the traveling output shaft is controlled according to the rotation speed of the control shaft.

【0009】[0009]

【実施例】本発明の実施例について図面を参照して説明
すると、図1は本発明の要部に係わる走行伝動装置の伝
動機構図である。図2は同じく本発明の要部に係わる負
荷装置としての実施例の正面図であり、図3は本発明の
要部に係わる負荷装置としての実施例の側面断面図であ
る。図4は本発明の実施例である刈取結束機の全体側面
図である。図5は本発明の実施例である刈取結束機の全
体背面図である。図6は本発明の実施例である刈取結束
機の全体平面図である。図7は本発明の実施例である刈
取結束機の走行クラッチ操作部の側面図であり、図8は
本発明の実施例である刈取結束機の走行クラッチ操作部
の断面図である。
DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a diagram of a transmission mechanism of a traveling transmission according to a main part of the present invention. FIG. 2 is a front view of an embodiment as a load device according to the main part of the present invention, and FIG. 3 is a side sectional view of the embodiment as a load device according to the main part of the present invention. FIG. 4 is an overall side view of the cutting and binding machine according to the embodiment of the present invention. FIG. 5 is an overall rear view of the cutting and binding machine according to the embodiment of the present invention. FIG. 6 is an overall plan view of a mowing and binding machine according to an embodiment of the present invention. FIG. 7 is a side view of a traveling clutch operating unit of the reaper and tying machine according to the embodiment of the present invention, and FIG.

【0010】まず、本発明に係わる実施例としての刈取
結束機の全体構成について図4〜図6により説明する。
走行車輪(1a)を装着した走行装置(1)の前部に刈
取部(9)を連設し、該刈取部(9)は前面に左右対象
に並設された一対の引起装置(4)(4)と、該引起装
置(4)(4)の後部下方にて刈取フレ−ム(11)の
左右両パイプに架設された刈刃装置(5)と、該刈刃装
置(5)に切断された穀稈を後方に搬送し結束装置(1
0)に送り込む一対の下部搬送体(7)(7)と、該下
部搬送体(7)(7)から受け継いだ穀稈を結束し後方
に放出する結束装置(10)と、該結束装置(10)か
ら放出された結束穀稈を挟持して後方に搬送する一対の
上部搬送体(6)(6)及び該上部搬送体(6)(6)
によって搬送されてきた結束穀稈を機体側方に搬送放出
する横搬送体(8)を主なる構成装置として、該各部構
成装置は刈取フレ−ム(11)を介して一体的に連結さ
れている。
First, an overall configuration of a mowing and binding machine as an embodiment according to the present invention will be described with reference to FIGS.
A mowing part (9) is continuously provided at the front of the traveling device (1) equipped with the traveling wheel (1a), and the mowing part (9) is a pair of raising devices (4) arranged side by side on the front surface. (4) a cutting blade device (5) installed on both left and right pipes of the cutting frame (11) below the rear part of the raising devices (4) and (4); and the cutting blade device (5). The cut stalks are transported backward and tied to a tying device (1
0), a bundling device (10) for bundling the cereal stems inherited from the lower carriages (7) and (7), and discharging the culm from the back, and a bundling device (7). 10) A pair of upper transporters (6) and (6) for nipping and transporting the united grain culm released from 10) and the upper transporters (6) and (6)
The main component is a horizontal transporter (8) that transports and releases the bound grain culms conveyed by the machine to the side of the machine, and these component components are integrally connected via a cutting frame (11). I have.

【0011】刈取部(9)前面に位置し、左右に並設さ
れた一対の引起装置(4)(4)は立植した穀稈を倒伏
の有無にかかわらず、付設した引起タイン付チェンの斜
上方への周回作用によって引起しながら穀稈姿勢を整
え、刈刃装置(5)の切断作用を補佐するように後傾し
装着されている。
[0011] A pair of raising devices (4) (4), which are located on the front surface of the mowing part (9) and are arranged side by side on the left and right, are provided with a chain with a raising tine attached to a cultivated cereal stem, regardless of whether or not it falls. The stalk posture is adjusted while raising by the orbiting action upward, and the cutting blade device (5) is attached backward and inclined so as to assist the cutting action.

【0012】前記上部搬送体(6)(6)は、一対の弾
性搬送無端帯を左右対象に配設してあり、平面視で各々
略三角形状に掛回し、互いに対峙する一辺は略八の字状
に後端部より前端部を大きく広げて、結束装置(10)
により放出された結束穀稈を取込みやすくし、同時に穀
稈の乱れを防止し結束穀稈の姿勢を整えて、横搬送体
(8)への受継ぎを円滑にする様に構成され、又下部搬
送体(7)(7)も同じく左右一対に配設されたタイン
付きチェンで構成され、略八の字状に後端部より前端部
を大きく広げて、刈刃装置(5)により切断された穀稈
の下部を整え強制的に結束装置(10)に送り込み、結
束装置(10)の円滑な作動を補佐している。送り込ま
れた穀稈は結束装置(10)で結束され放出ア−ム(1
4)を介して後方へ放出され、上部搬送体(6)(6)
で移送され後方に搬送されていき、横搬送体(8)に受
け継がれる。
The upper transport bodies (6) and (6) have a pair of elastic transport endless belts disposed symmetrically to the left and right. Each of the upper transport bodies (6) and (6) wraps in a substantially triangular shape in plan view. The binding device (10) with the front end wider than the rear end in a letter shape
It is configured to make it easier to take in the united cereals released by the above, and at the same time, to prevent the turbulence of the united culm, to adjust the posture of the united cereal, and to make the transfer to the horizontal conveyor (8) smooth. Carriers (7) and (7) are also composed of chains with tines, which are also arranged in a pair on the left and right. The front end is wider than the rear end in a substantially figure-eight shape, and cut by the cutting blade device (5). The lower part of the culm is trimmed and forcibly sent to the binding device (10) to assist the smooth operation of the binding device (10). The fed cereal stems are bound by the binding device (10) and released by the release arm (1).
It is discharged to the rear through 4), and the upper carrier (6) (6)
And is conveyed backward, and is inherited by the horizontal conveyance body (8).

【0013】一方、略三角形に張設された上部搬送体
(6)の一辺を横側方への搬送部とし、該搬送部に対応
し略同高なる相対位置に横搬送体(8)を対峙並設し
て、上部搬送体(6)から搬送された結束穀稈を横搬送
体(8)と上部搬送体(6)の協働により挟持して機体
横側方に搬送して放出する。
On the other hand, one side of the upper transport body (6) stretched in a substantially triangular form is a transport section to the lateral side, and the horizontal transport body (8) is located at a relative position which is substantially the same height as the transport section. The united grain culms conveyed from the upper carrier (6) are confronted and arranged side by side, and are transported to the lateral side of the machine and released by the cooperation of the horizontal carrier (8) and the upper carrier (6). .

【0014】また、図4〜図6に示すように、機体の本
体部はエンジン(18)と走行伝動装置(2)を直結
し、該走行伝動装置(2)の走行出力軸(2c)に車軸
ケ−ス(1b)を添設し、更に、該車軸ケ−ス(1b)
をエンジン(18)の下方位置即ち機体の中心線上に配
設構成させることにより左右バランスを調和させ、車軸
ケ−ス(1b)から左右均等に延出した走行車軸を介し
て走行車輪(1a)が駆動される。
As shown in FIGS. 4 to 6, the main body of the body directly connects the engine (18) and the traveling transmission (2), and is connected to the traveling output shaft (2c) of the traveling transmission (2). An axle case (1b) is additionally provided, and the axle case (1b)
Is arranged below the engine (18), that is, on the center line of the fuselage, so that the left-right balance is harmonized, and the traveling wheels (1a) are extended via the traveling axle extending left and right equally from the axle case (1b). Is driven.

【0015】ここで、本発明の要部について図1〜図3
を参照して詳述する。走行伝動装置(2)の最終軸部
(2f)に差動装置(2b)を装設し、該差動装置(2
b)が有する2方向の出力側の一方を走行出力軸(2
c)とし他方を制御軸(2d)として、該制御軸(2
d)に負荷装置(2e)として遠心力ブレ−キ(3)を
軸着して、制御軸(2d)の回転速度に伴って負荷が発
生し、所定の回転速度以上になると最大負荷となり、制
御軸(2d)を制動する様に構成されている。
Here, the main parts of the present invention are shown in FIGS.
It will be described in detail with reference to FIG. A differential (2b) is mounted on the final shaft (2f) of the traveling transmission (2), and the differential (2
b) has one of the two output sides on the traveling output shaft (2).
c) and the other as the control axis (2d),
A centrifugal brake (3) is mounted on the d) as a load device (2e), and a load is generated in accordance with the rotation speed of the control shaft (2d). The control shaft (2d) is configured to be braked.

【0016】エンジン(18)から走行伝動装置(2)
に入力された駆動力は、初期段階では瞬間的に負荷の小
さい制御軸(2d)に伝動され、制御軸(2d)の回転
速度に伴って負荷が発生すると、走行出力軸(2c)側
への駆動力の伝達が加速されて、制御軸(2d)が所定
の回転速度以上になり軸着した遠心力ブレ−キ(3)に
よって制動されると、差動装置(2b)によって駆動力
は全面的に走行出力軸(2c)に伝達される。
[0016] From the engine (18) to the traveling transmission (2)
Is transmitted to the control shaft (2d) with a small load instantaneously in the initial stage, and when a load is generated according to the rotation speed of the control shaft (2d), the driving force is transmitted to the traveling output shaft (2c) side. When the transmission of the driving force is accelerated and the control shaft (2d) exceeds the predetermined rotational speed and is braked by the centrifugal brake (3) attached to the shaft, the driving force is increased by the differential device (2b). The whole is transmitted to the traveling output shaft (2c).

【0017】上記の様に負荷装置(2e)である遠心力
ブレ−キ(3)と差動装置(2b)の協働によって差動
効果を拡大し、入力された駆動力を制御軸(2d)の回
転数に係合させて走行出力軸(2c)に伝動して、高速
段においても緩発進から徐々に高速化するように構成
し、入力初期は瞬間的に負荷が小さい制御軸(2d)に
駆動力を掛けて、回転速度に伴い制御軸(2d)の負荷
が増大すると、走行出力軸(2c)に駆動力を伝達させ
る様に構成して急発進の防止をする様にした。
As described above, the differential effect is enlarged by the cooperation of the centrifugal brake (3), which is the load device (2e), and the differential device (2b), and the input driving force is controlled by the control shaft (2d). ), The transmission is transmitted to the traveling output shaft (2c) to gradually increase the speed from a slow start even in a high-speed stage. ) Is applied with a driving force, and when the load on the control shaft (2d) increases with the rotation speed, the driving force is transmitted to the traveling output shaft (2c) to prevent sudden start.

【0018】すなわち、遠心力ブレ−キ(3)を負荷装
置(2e)にすることで、所定の回転速度までは負荷が
増大するが、所定の回転速度を超え最大負荷になると制
御軸(2d)の回転を制動し、差動作用の働きで走行出
力軸(2c)の回転速度を増大させる様に構成して、入
力される駆動力が走行車軸に瞬間的に一括して掛からな
い様に工夫した。
That is, by using the centrifugal brake (3) as the load device (2e), the load increases up to a predetermined rotation speed, but when the rotation speed exceeds the predetermined rotation speed and reaches the maximum load, the control shaft (2d) is used. ), The rotation of the traveling output shaft (2c) is increased by the action of the differential action so that the input driving force is not instantaneously applied to the traveling axle at once. Devised.

【0019】本発明で負荷装置(2e)の実施例とした
遠心力ブレ−キ(3)に関し記述する。図2と図3に示
す様に遠心力ブレ−キ(3)は外ブレ−キフランジ(3
a)と内ブレ−キフランジ(3b)及び揺動テコ(3
d)を基盤として、遠心力によって揺れ動く揺動ア−ム
(3c)を内ブレ−キフランジ(3b)の外周部に3ヵ
所等分して枢着し、この揺動ア−ム(3c)を介して揺
動テコ(3d)が枢着され、制御軸(2d)の回転に伴
い該揺動テコ(3d)は揺動支点(3e)を基点として
揺動ア−ム(3c)に突き上げられ外周方向にその先端
を張り出し拡張するように構成されている。
A centrifugal brake (3) as an embodiment of the load device (2e) in the present invention will be described. As shown in FIGS. 2 and 3, the centrifugal brake (3) has an outer brake flange (3).
a), inner brake flange (3b) and swing lever (3)
On the basis of d), a swing arm (3c) which swings by centrifugal force is divided into three equal parts on the outer peripheral portion of the inner brake flange (3b) and pivotally connected, and this swing arm (3c) is attached. A swing lever (3d) is pivotally connected via the swing lever (3d), and the swing lever (3d) is pushed up to the swing arm (3c) with the swing fulcrum (3e) as a base point as the control shaft (2d) rotates. It is configured such that its tip projects and expands in the outer peripheral direction.

【0020】更に、外ブレ−キフランジ(3a)と内ブ
レ−キフランジ(3b)のボス部は嵌合し、該ボス部に
巻着された渦巻ばね(3f)によって係合されている。
又内ブレ−キフランジ(3b)の外周側に同心状にして
外ブレ−キフランジ(3a)のボス部に嵌着されたロッ
クリング(3h)があり、該ロックリング(3h)はロ
ック渦巻ばね(3k)を介して外ブレ−キフランジ(3
a)と内ブレ−キフランジ(3b)に同調して回転す
る。該ロックリング(3h)は底部を有する円筒形状を
し、底部に取付ボスを設け円筒周縁上に3等分した位置
でロック爪部を突出させ、該ロック爪部は内ブレ−キフ
ランジ(3b)の外周部に3ヵ所突設した揺動ア−ム
(3c)の枢着部と相対的な位置で揺動ア−ム(3c)
に追従し回転する様に組み付けてある。
Further, the boss portions of the outer brake flange (3a) and the inner brake flange (3b) are fitted and engaged by a spiral spring (3f) wound around the boss portion.
There is a lock ring (3h) fitted concentrically to the boss of the outer brake flange (3a) on the outer peripheral side of the inner brake flange (3b). The lock ring (3h) is a lock spiral spring (3). 3k) through the outer brake flange (3
a) and the inner brake flange (3b). The lock ring (3h) is formed in a cylindrical shape having a bottom, a mounting boss is provided on the bottom, and a lock claw is projected at three equally spaced positions on the peripheral edge of the cylinder, and the lock claw is an inner brake flange (3b). The swing arm (3c) is located at a position relative to the pivotal arm of the swing arm (3c) protruding at three places on the outer periphery of the swing arm (3c).
It is assembled to follow and rotate.

【0021】従って、制御軸(2d)の回転に伴って揺
動ア−ム(3c)が張り出し制動状態になると、該揺動
ア−ム(3c)に同調追従し回転するロックリング(3
h)はそのロック爪部を揺動ア−ム(3c)に当接さ
せ、その回転力により揺動ア−ム(3c)を押圧ロック
して制動状態を保持する様になっている。一方、制御軸
(2d)の駆動力が切断され回転力を失うと渦巻きばね
(3e)及びロック渦巻ばね(3k)のばね力で内ブレ
−キフランジ(3b)とロックリング(3h)は各々戻
し方向に滑動して揺動ア−ム(3c)は元の位置に戻さ
れ、制動状態は解除される。尚、外ブレ−キフランジ
(3a)は制御軸(2d)にキ−を介して軸着され、ボ
ス部に嵌着した内ブレ−キフランジ(3b)及びロック
リング(3h)と共に制御軸(2d)と一体的に回転す
る様に構成されている。
Accordingly, when the swing arm (3c) is in the overhanging braking state with the rotation of the control shaft (2d), the lock ring (3) that tunes and follows the swing arm (3c) and rotates.
In (h), the lock claw is brought into contact with the swing arm (3c), and the swing arm (3c) is pressed and locked by the rotational force to maintain the braking state. On the other hand, when the driving force of the control shaft (2d) is cut and the rotational force is lost, the inner brake flange (3b) and the lock ring (3h) are returned by the spring force of the spiral spring (3e) and the lock spiral spring (3k). The swing arm (3c) is returned to its original position by sliding in the direction, and the braking state is released. The outer brake flange (3a) is axially attached to the control shaft (2d) via a key, and the inner brake flange (3b) and the lock ring (3h) fitted to the boss portion together with the control shaft (2d). It is constituted so that it may rotate integrally.

【0022】即ち、制御軸(2d)の回転と共に外ブレ
−キフランジ(3a)を介して内ブレ−キフランジ(3
b)が回転し、回転速度の上昇に伴って遠心力が増大し
ていくと、遠心力によって揺動ア−ム(3c)が起立
し、揺動テコ(3d)は揺動支点(3e)を基点として
突き上げられ外周方向に張り出し拡張して、揺動テコ
(3d)の先端部にある摩擦面(イ)(ロ)(ハ)を制
動体(3g)に押圧し制動力を発生する。この時摩擦面
(イ)(ロ)(ハ)はそれぞれの揺動支点(3e)から
の位置を異にし、回転速度の上昇に伴って摩擦面は
(イ)から(ハ)へと順次加増し、所定の回転速度以上
で制動状態になり、ロックリング(3h)が起立した揺
動ア−ム(3c)を押圧ロックして該制動状態を保持す
る。又、駆動力が切断され回転力を失うと摩擦面(イ)
(ロ)(ハ)は制動体(3g)から離反して制動力を消
滅する。
That is, with the rotation of the control shaft (2d), the inner brake flange (3) is moved through the outer brake flange (3a).
When b) rotates and the centrifugal force increases as the rotation speed increases, the centrifugal force causes the swing arm (3c) to rise, and the swing lever (3d) moves to the swing fulcrum (3e). The frictional surface (a), (b), and (c) at the tip of the swing lever (3d) is pressed against the braking body (3g) to generate a braking force. At this time, the friction surfaces (a), (b), and (c) differ in position from the respective fulcrum (3e), and the friction surfaces are sequentially added from (a) to (c) as the rotation speed increases. The locking ring (3h) presses and locks the oscillating arm (3c) standing up to maintain the braking state at a predetermined rotation speed or higher. Also, when the driving force is cut and the rotational force is lost, the friction surface (a)
(B) and (c) are separated from the braking body (3g) to eliminate the braking force.

【0023】一方、走行クラッチ操作部(30)は図7
〜図8に示す如く、走行クラッチレバ−(31)と一体
構成を成すクラッチカム(32)及び案内金具(33)
を主なる構成部材として、該クラッチカム(32)は断
面がコの字形のクラッチカム体(32a)に各左右一対
の上支点(A)と下支点(B)を固着し、ばね掛け棒
(32b)をコの字形の内側に橋架固着した構成になっ
ている。
On the other hand, the traveling clutch operating section (30) is shown in FIG.
As shown in FIG. 8, a clutch cam (32) and a guide fitting (33) are formed integrally with the traveling clutch lever (31).
The clutch cam (32) has a pair of upper fulcrums (A) and lower fulcrums (B) fixed to a pair of left and right sides on a clutch cam body (32a) having a U-shaped cross section. 32b) is fixed to the inside of a U-shape by a bridge.

【0024】前記走行クラッチレバ−(31)を前後進
クラッチ操作すると、一体構成を成すクラッチカム(3
2)は案内金具(33)に穿孔した円弧状のリ−ド穴に
挿入した左右一対の上支点(A)又は下支点(B)を回
動支点として、クラッチレバ−(31)と一体的に回動
する。この時、クラッチレバ−(31)を前に押すと上
支点(A)が回動支点となり後方向に引くと下支点
(B)が回動支点となる。クラッチレバ−(31)の前
後操作方向によって回動支点が上支点(A)と下支点
(B)で相互に移行するようになっている。尚、前記ば
ね掛け棒(32b)を介してクラッチカム(32)には
コイルばね(32c)が装着され、該コイルばね(32
c)は走行クラッチレバ−(31)の操作で前進時は上
支点(A)又後進時は下支点(B)を支点越えして、走
行クラッチレバ−(31)の操作位置を安定させてい
る。
When the traveling clutch lever (31) is operated in forward and backward clutch operation, an integral clutch cam (3) is formed.
2) is integrated with the clutch lever (31) using a pair of left and right upper fulcrums (A) or lower fulcrums (B) inserted into an arc-shaped lead hole drilled in the guide fitting (33) as rotation fulcrums. To rotate. At this time, when the clutch lever (31) is pushed forward, the upper fulcrum (A) becomes a pivot, and when it is pulled backward, the lower fulcrum (B) becomes a pivot. The rotation fulcrum shifts between the upper fulcrum (A) and the lower fulcrum (B) depending on the front-rear operation direction of the clutch lever (31). A coil spring (32c) is attached to the clutch cam (32) via the spring hook (32b).
c) The operation of the traveling clutch lever (31), which exceeds the upper fulcrum (A) when moving forward and the lower fulcrum (B) when moving backward to stabilize the operating position of the traveling clutch lever (31). I have.

【0025】走行クラッチレバ−(31)に併設された
ブレ−キレバ−(34)はクラッチカム体(32a)の
外側壁に固着してあるブレ−キレバ−支点(C)に枢着
されて回動するが、該ブレ−キレバ−(34)の先端は
別に先レバ−支点(D)で回動するように配設したブレ
−キ先レバ−(35)の一端に、該ブレ−キ先レバ−
(35)に装着したブレ−キ戻しばね(36)によって
当接されている。更に、該ブレ−キ先レバ−(35)の
他端はクラッチカム体(32a)の下端に突着したブレ
−キ戻しピン(37)と走行クラッチレバ−(31)の
後進操作時に当接し、ブレ−キを解除する様に構成され
ている。
A brake lever (34) attached to the traveling clutch lever (31) is pivotally attached to a brake lever fulcrum (C) fixed to the outer wall of the clutch cam body (32a). However, the tip of the brake lever (34) is attached to one end of a brake tip lever (35), which is disposed so as to rotate separately at the tip lever fulcrum (D). Lever
It is in contact with a brake return spring (36) mounted on (35). Further, the other end of the brake lever (35) comes into contact with the brake return pin (37) abutting on the lower end of the clutch cam body (32a) during the reverse operation of the traveling clutch lever (31). , The brake is released.

【0026】更にブレ−キレバ−(34)にはブレ−キ
レバ−突起(38)が固設してあり、走行クラッチレバ
−(31)が前進操作時、該ブレ−キレバ−突起(3
8)は走行クラッチレバ−(31)に当接し、ブレ−キ
レバ−(34)を引くとブレ−キレバ−突起(38)に
よって走行クラッチレバ−(31)は自動的に中立位置
に戻されると同時にブレ−キが効くようになっている。
逆に走行クラッチレバ−(31)を前進操作するとブレ
−キレバ−突起(38)を押して、ブレ−キを解除する
様になる。従って、前後進いずれのクラッチ接続操作に
おいてもブレ−キを自動解除する。又ブレ−キを効き状
態にすると走行クラッチレバ−(31)は前後進いずれ
の状態でも自動的に中立位置に戻るように構成され、ク
ラッチ操作とブレ−キ操作が連動して容易になってい
る。
A brake lever projection (38) is fixedly mounted on the brake lever (34), and when the traveling clutch lever (31) is operated forward, the brake lever projection (3) is provided.
8) comes into contact with the traveling clutch lever (31), and when the braking lever (34) is pulled, the traveling clutch lever (31) is automatically returned to the neutral position by the braking lever projection (38). At the same time, the brakes work.
Conversely, when the traveling clutch lever (31) is operated forward, the brake lever projection (38) is pushed to release the brake. Therefore, the brake is automatically released in any of the clutch connection operations in the forward and backward directions. When the brake is activated, the traveling clutch lever (31) is configured to automatically return to the neutral position in any of the forward and backward directions, so that the clutch operation and the brake operation are easily performed in conjunction with each other. I have.

【0027】この様に構成された走行クラッチ操作部
(30)の作用は以下の様になる。走行クラッチレバ−
(31)を前側に倒すと上支点(A)が支点となり、ク
ラッチカム(32)が回動しコイルばね(32c)は支
点越えして、クラッチワイヤ−が緩み前進へクラッチが
接続する。走行クラッチレバ−(31)を後側に引くと
下支点(B)が支点となり、クラッチカム(32)は前
進時とは逆方向に回動し、コイルばね(32c)は支点
越えしてクラッチワイヤ−を引っ張り後進へクラッチが
接続する。いずれの場合でも併設されたブレ−キレバ−
(34)を効かすと、該ブレ−キレバ−(34)に固設
したブレ−キレバ−突起(38)又はブレ−キ戻しピン
(37)を介して、走行クラッチレバ−(31)を連動
的に中立位置に戻す様になっている。
The operation of the traveling clutch operating section (30) configured as described above is as follows. Travel clutch lever
When (31) is tilted forward, the upper fulcrum (A) becomes the fulcrum, the clutch cam (32) rotates, the coil spring (32c) moves over the fulcrum, the clutch wire is loosened and the clutch is connected to the forward movement. When the traveling clutch lever (31) is pulled rearward, the lower fulcrum (B) becomes the fulcrum, the clutch cam (32) rotates in the direction opposite to that in the forward movement, and the coil spring (32c) moves over the fulcrum to engage the clutch. The clutch is connected to the reverse by pulling the wire. In any case, the attached brake lever
When (34) is activated, the traveling clutch lever (31) is interlocked via the brake lever projection (38) or the brake return pin (37) fixed to the brake lever (34). To return to the neutral position.

【0028】従来の技術でもクラッチワイヤ−を押し引
きして、前後進の走行クラッチを断続する構成は公知の
ものとして開示されているが、クラッチワイヤ−の一端
側を戻しばねを介して走行クラッチと接続しているのが
一般的である。この場合断続操作の過程で戻しばねに抗
してクラッチワイヤ−を押すか又は引く位置では、操作
荷重が高くなりクラッチ操作が重くなるが、前記の構成
によって実施例のような走行クラッチ機構においては、
前後進のクラッチ操作を一本のクラッチワイヤ−で可能
とし、しかも引張コイルばねから成る戻しばねに抗する
位置で操作荷重が高くなっても、クラッチ操作力を軽減
する事が出来る。
In the prior art, a configuration in which the clutch wire is pushed / pulled to connect / disconnect the traveling clutch for forward / backward traveling is disclosed as a known one, but one end of the clutch wire is connected to the traveling clutch via a return spring. It is generally connected to. In this case, in the position where the clutch wire is pushed or pulled against the return spring in the process of the intermittent operation, the operation load becomes high and the clutch operation becomes heavy, but in the traveling clutch mechanism such as the embodiment by the above configuration, ,
Forward and backward clutch operation can be performed with a single clutch wire, and the clutch operation force can be reduced even if the operation load increases at a position against the return spring formed by a tension coil spring.

【0029】即ち、前記の構成において走行クラッチレ
バ−(31)を前側に倒し前進へクラッチを接続する
と、上支点(A)を支点としてコイルばね(32c)は
支点越えし、クラッチワイヤ−を押すので走行クラッチ
と接続している引張コイルばねから成る戻しばねに対し
ても押す戻す方向となり、戻しばねのばね力も加わり、
クラッチ操作力は軽くてすむ。逆に走行クラッチレバ−
(31)を後側に引き後進へクラッチを接続すると、下
支点(B)を支点としてコイルばね(32c)は支点越
えするので、クラッチワイヤ−を引き、戻しばねに抗し
ても支点が下支点(B)に移るので、走行クラッチレバ
−(31)に掛かる力点と支点との長さが長くなり、ク
ラッチ操作力は軽減される。この様に走行クラッチレバ
−(31)の前後進操作方向に対して、走行クラッチレ
バ−(31)の支点を上支点(A)と下支点(B)とで
相互に移行させる事で、前後進操作力をいずれも軽減す
るように構成されている事を特徴とした走行クラッチ操
作部(30)である。
That is, in the above configuration, when the traveling clutch lever (31) is tilted forward and the clutch is connected forward, the coil spring (32c) exceeds the fulcrum with the upper fulcrum (A) as the fulcrum, and pushes the clutch wire. Therefore, the direction of pushing back is also applied to the return spring composed of the extension coil spring connected to the traveling clutch, and the spring force of the return spring is also applied,
The clutch operating force is light. Conversely, the traveling clutch lever
When the clutch (31) is pulled rearward and the clutch is connected to the reverse, the coil spring (32c) goes over the fulcrum with the lower fulcrum (B) as the fulcrum. Since the fulcrum moves to the fulcrum (B), the length of the fulcrum and the force applied to the traveling clutch lever (31) becomes longer, and the clutch operating force is reduced. In this way, the fulcrum of the traveling clutch lever (31) is shifted between the upper fulcrum (A) and the lower fulcrum (B) with respect to the forward / rearward operation direction of the traveling clutch lever (31), so that it can be moved forward and backward. A traveling clutch operating section (30) characterized in that it is configured to reduce any forward operating force.

【0030】[0030]

【発明の効果】本発明は、以上説明したような形態で実
施され、以下に記載されるような効果を奏する。
The present invention is embodied in the form described above and has the following effects.

【0031】歯車機構から成る走行伝動装置(2)を有
する歩行型作業機において、該走行伝動装置(2)の入
力軸(2a)から最終軸部(2f)に至る伝動経路内に
差動装置(2b)を内蔵して、差動作用によって入力さ
れた駆動力が歯車列を介し瞬間的に一括して走行車軸に
掛からない様にして、急発進現象を抑制する構成にした
ので、高低段いずれの変速位置においても走行クラッチ
接続操作時に瞬間的に急発進するのを防止する事ができ
て、安全で操作性を容易にする事ができる。
In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) to a final shaft portion (2f) of the traveling transmission (2). (2b) is incorporated so that the driving force input by the differential action is not instantaneously applied to the traveling axle via the gear train instantaneously, thereby suppressing the sudden start phenomenon. In any shift position, it is possible to prevent instantaneous sudden start during the operation of connecting the traveling clutch, and it is possible to safely and easily operate.

【0032】歯車機構から成る走行伝動装置(2)を有
する歩行型作業機において、該走行伝動装置(2)の入
力軸(2a)から最終軸部(2f)に至る伝動経路内に
差動装置(2b)を内蔵し、該差動装置(2b)が有す
る2方向の出力側の一方を走行出力軸(2c)とし他方
を制御軸(2d)として、該制御軸(2d)の回転速度
を制動する事によって差動効果を拡大し、入力された駆
動力を制御軸(2d)の回転速度に係わり合わせて走行
車軸に伝動させて、高速段においても緩発進から徐々に
高速化するように構成したので、低速段時同様に高速段
からのクラッチ接続操作時においても、急発進を回避し
て安全な操作性と容易な操作性を可能とする事が出来
る。
In a walking type work machine having a traveling transmission (2) comprising a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f). (2b), one of the two output sides of the differential device (2b) is a traveling output shaft (2c) and the other is a control shaft (2d), and the rotational speed of the control shaft (2d) is By increasing the differential effect by braking, the input driving force is transmitted to the traveling axle in relation to the rotation speed of the control shaft (2d), so that the speed gradually increases from a slow start even at a high speed stage. With this configuration, it is possible to avoid sudden start and enable safe operability and easy operability even at the time of clutch connection operation from the high speed stage as well as at the low speed stage.

【0033】歯車機構から成る走行伝動装置(2)を有
する歩行型作業機において、該走行伝動装置(2)の入
力軸(2a)から最終軸部(2f)に至る伝動経路内に
差動装置(2b)を内蔵し、該差動装置(2b)が有す
る2方向の出力側の一方を走行出力軸(2c)とし他方
を制御軸(2d)として、該制御軸(2d)には回転速
度に伴い負荷を発生する負荷装置(2e)を装着して、
入力された駆動力を差動作用によって入力初期は瞬間的
に負荷が小さい制御軸(2d)に掛け、回転速度に伴い
制御軸(2d)の負荷が増大すると、走行出力軸(2
c)を介して走行車軸に駆動力を伝達させる様に構成し
たので、制御軸(2d)の回転速度により差動効果を拡
大して、急発進の防止をより確実にする事ができる。
In a walking type work machine having a traveling transmission (2) comprising a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f). (2b), one of the two output sides of the differential device (2b) is a traveling output shaft (2c) and the other is a control shaft (2d), and the control shaft (2d) has a rotational speed. A load device (2e) that generates a load is attached with
The input driving force is applied to the control shaft (2d) with a small load instantaneously at the beginning of the input by the differential action, and when the load on the control shaft (2d) increases with the rotation speed, the traveling output shaft (2d)
Since the driving force is transmitted to the traveling axle via c), the differential effect is enlarged by the rotation speed of the control shaft (2d), and the sudden start can be more reliably prevented.

【0034】歯車機構から成る走行伝動装置(2)を有
する歩行型作業機において、該走行伝動装置(2)に差
動装置(2b)を内蔵して、この差動装置(2b)に装
着された制御軸(2d)に回転速度に伴い負荷を発生す
る負荷装置(2e)を装着し、該負荷装置(2e)は所
定の回転速度までは負荷を次第に増大し、所定の回転速
度以上になると最大負荷を発生して、軸支する制御軸
(2d)の回転を制動して、差動装置(2b)と協働し
て走行出力軸(2c)の回転速度を徐々に増大させる様
に構成され、走行車軸に入力される駆動力が瞬間的に一
括して掛からない様にしたので、駆動力の急速な伝達を
緩和し急発進を防止する事ができ、運転操作性を容易に
し且つ安全なるものにする事ができる。
In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential (2b) is built in the traveling transmission (2) and mounted on the differential (2b). A load device (2e) that generates a load in accordance with the rotation speed is mounted on the control shaft (2d), and the load device (2e) gradually increases the load up to a predetermined rotation speed, and when the load device exceeds the predetermined rotation speed. The maximum load is generated, the rotation of the control shaft (2d) that is supported is braked, and the rotation speed of the traveling output shaft (2c) is gradually increased in cooperation with the differential device (2b). As a result, the driving force input to the traveling axle is not applied instantaneously and collectively, so that the rapid transmission of the driving force can be alleviated and sudden start can be prevented, making the driving operability easy and safe. It can be.

【0035】歯車機構から成る走行伝動装置(2)を有
する歩行型作業機において、該走行伝動装置(2)に差
動装置(2b)を内蔵して、この差動装置(2b)に装
設された制御軸(2d)に負荷装置(2e)として遠心
力ブレ−キ(3)を装着し、差動装置(2b)と遠心力
ブレ−キ(3)を組み合わて出力制御をするようにし
て、制御軸(2d)の回転速度に係わって負荷を発生す
る様に構成したので、差動作用により入力される駆動力
は初期的には制御軸(2d)側に流れ、この制御軸(2
d)に軸着した遠心力ブレ−キ(3)によって制動力が
発生すると走行出力軸(2c)側に駆動力が伝達され、
差動装置(2b)と遠心力ブレ−キ(3)の相乗効果に
より、走行装置の急発進作動を回避する事ができる。
In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential (2b) is built in the traveling transmission (2) and mounted on the differential (2b). A centrifugal brake (3) is mounted on the control shaft (2d) as a load device (2e), and the output is controlled by combining the differential device (2b) and the centrifugal brake (3). Therefore, since the load is generated in accordance with the rotational speed of the control shaft (2d), the driving force input by the differential action initially flows to the control shaft (2d) side, and the control shaft (2d) 2
When a braking force is generated by the centrifugal brake (3) attached to d), the driving force is transmitted to the traveling output shaft (2c),
By the synergistic effect of the differential device (2b) and the centrifugal brake (3), it is possible to avoid a sudden start operation of the traveling device.

【図面の簡単な説明】[Brief description of the drawings]

【図1】本発明の要部に係わる走行伝動装置の伝動機構
図である。
FIG. 1 is a transmission mechanism diagram of a traveling transmission device according to a main part of the present invention.

【図2】本発明の要部に係わる負荷装置としての実施例
の正面図である。
FIG. 2 is a front view of an embodiment as a load device according to a main part of the present invention.

【図3】本発明の要部に係わる負荷装置としての実施例
の断面図である。
FIG. 3 is a sectional view of an embodiment as a load device according to a main part of the present invention.

【図4】本発明の実施例である刈取結束機の全体側面図
である。
FIG. 4 is an overall side view of a cutting and binding machine according to an embodiment of the present invention.

【図5】本発明の実施例である刈取結束機の全体背面図
である。
FIG. 5 is an overall rear view of the cutting and binding machine according to the embodiment of the present invention.

【図6】本発明の実施例である刈取結束機の全体平面図
である。
FIG. 6 is an overall plan view of a cutting and binding machine according to an embodiment of the present invention.

【図7】本発明の実施例である刈取結束機の走行クラッ
チ操作部の側面図である。
FIG. 7 is a side view of a traveling clutch operating unit of the mowing and binding machine according to the embodiment of the present invention.

【図8】本発明の実施例である刈取結束機の走行クラッ
チ操作部の断面図である。
FIG. 8 is a cross-sectional view of a traveling clutch operating unit of the mowing and binding machine according to the embodiment of the present invention.

【符号の説明】[Explanation of symbols]

1 走行装置 1a 走行車輪 1b 車軸ケ−ス 2 走行伝動装置 2b 差動装置 2e 負荷装置 3 遠心力ブレ−キ 3a 外ブレ−キフランジ 3b 内ブレ−キフランジ 3c 揺動ア−ム 3d 揺動テコ 3h ロックリング 4 引起装置 9 刈取部 10 結束装置 18 エンジン 30 走行クラッチ操作部 31 走行クラッチレバ− 32 クラッチカム 34 ブレ−キレバ− 35 ブレ−キ先レバ− 38 ブレ−キレバ−突起 A 上支点 B 下支点 DESCRIPTION OF SYMBOLS 1 Traveling device 1a Running wheel 1b Axle case 2 Traveling transmission device 2b Differential device 2e Loading device 3 Centrifugal force brake 3a Outer brake flange 3b Inner brake flange 3c Swing arm 3d Swing lever 3h Lock Ring 4 Raising device 9 Cutting unit 10 Binding device 18 Engine 30 Traveling clutch operating unit 31 Traveling clutch lever 32 Clutch cam 34 Braking lever 35 Braking lever 38 Braking lever projection A Upper fulcrum B Lower fulcrum

Claims (5)

【特許請求の範囲】[Claims] 【請求項1】 歯車機構から成る走行伝動装置(2)を
有する歩行型作業機において、該走行伝動装置(2)の
入力軸(2a)から最終軸部(2f)に至る伝動経路内
に差動装置(2b)を内蔵したことを特徴とする歩行型
作業機における走行伝動装置。
1. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A traveling transmission device for a walk-behind working machine, wherein the traveling device (2b) is incorporated.
【請求項2】 歯車機構から成る走行伝動装置(2)を
有する歩行型作業機において、該走行伝動装置(2)の
入力軸(2a)から最終軸部(2f)に至る伝動経路内
に差動装置(2b)を内蔵し、該差動装置(2b)が有
する2方向の出力側の一方を走行出力軸(2c)とし、
他方を制御軸(2d)とした事を特徴とする歩行型作業
機における走行伝動装置。
2. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A driving device (2b), and one of two output sides of the differential device (2b) is a traveling output shaft (2c);
A traveling transmission device for a walking type working machine, characterized in that the other is a control shaft (2d).
【請求項3】 歯車機構から成る走行伝動装置(2)を
有する歩行型作業機において、該走行伝動装置(2)の
入力軸(2a)から最終軸部(2f)に至る伝動経路内
に差動装置(2b)を内蔵し、該差動装置(2b)が有
する2方向の出力側の一方を走行出力軸(2c)とし、
他方を制御軸(2d)として、該制御軸(2d)には回
転速度に伴い負荷を発生する負荷装置(2e)を装着し
た事を特徴とする歩行型作業機における走行伝動装置。
3. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A driving device (2b), and one of two output sides of the differential device (2b) is a traveling output shaft (2c);
A traveling transmission device for a walk-behind type working machine, characterized in that the other is a control shaft (2d), and a load device (2e) for generating a load according to a rotation speed is mounted on the control shaft (2d).
【請求項4】 歯車機構から成る走行伝動装置(2)を
有する歩行型作業機において、該走行伝動装置(2)に
差動装置(2b)を内蔵して、この差動装置(2b)に
装着された制御軸(2d)に回転速度に伴い負荷を発生
する負荷装置(2e)を装着し、該負荷装置(2e)を
所定の回転速度までは負荷を次第に増大し、所定の回転
速度以上になると最大負荷を発生して、制御軸(2d)
の制動による差動作用によって、走行出力軸(2c)の
回転速度を制御する様に構成した事を特徴とする請求項
3記載の歩行型作業機における走行伝動装置。
4. A walking type working machine having a traveling transmission (2) composed of a gear mechanism, wherein the traveling transmission (2) has a differential (2b) built therein, and the differential (2b) A load device (2e) that generates a load according to the rotation speed is mounted on the mounted control shaft (2d), and the load is gradually increased until the load device (2e) reaches a predetermined rotation speed. , The maximum load is generated and the control axis (2d)
The traveling transmission device for a walking-type working machine according to claim 3, wherein the rotational speed of the traveling output shaft (2c) is controlled by a differential action by braking.
【請求項5】 歯車機構から成る走行伝動装置(2)を
有する歩行型作業機において、該走行伝動装置(2)に
差動装置(2b)を内蔵して、この差動装置(2b)に
装設された制御軸(2d)に負荷装置(2e)として遠
心力ブレ−キ(3)を装着して、差動装置(2b)と遠
心力ブレ−キ(3)を組合わせて出力制御をする事を特
徴とする請求項4記載の歩行型作業機における走行伝動
装置。
5. A walking type work machine having a traveling transmission (2) comprising a gear mechanism, wherein the traveling transmission (2) has a differential (2b) built therein, and the differential (2b) has A centrifugal brake (3) is mounted as a load device (2e) on the installed control shaft (2d), and output control is performed by combining the differential device (2b) and the centrifugal brake (3). The traveling transmission device for a walking-type working machine according to claim 4, wherein:
JP10346307A 1998-12-07 1998-12-07 Power transmission system for walking type working machine Pending JP2000166301A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP10346307A JP2000166301A (en) 1998-12-07 1998-12-07 Power transmission system for walking type working machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP10346307A JP2000166301A (en) 1998-12-07 1998-12-07 Power transmission system for walking type working machine

Publications (1)

Publication Number Publication Date
JP2000166301A true JP2000166301A (en) 2000-06-20

Family

ID=18382525

Family Applications (1)

Application Number Title Priority Date Filing Date
JP10346307A Pending JP2000166301A (en) 1998-12-07 1998-12-07 Power transmission system for walking type working machine

Country Status (1)

Country Link
JP (1) JP2000166301A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103277478A (en) * 2013-05-08 2013-09-04 姚捷 Combined-harvester four-gear gearbox assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103277478A (en) * 2013-05-08 2013-09-04 姚捷 Combined-harvester four-gear gearbox assembly

Similar Documents

Publication Publication Date Title
JP3894757B2 (en) Riding mower
US5152382A (en) Accelerator pedal and brake mechanism
US5136899A (en) Accelerator pedal and brake mechanism
US4285419A (en) Brake clutch release control for belt driven riding mowers
JP2009278954A (en) Operation control apparatus for working vehicle
US2151659A (en) Power lawn mower
JP2000166301A (en) Power transmission system for walking type working machine
JP5019529B2 (en) Combine operation structure
JP2003232414A (en) Tension clutch and agricultural machinery using tension clutch
JP2721067B2 (en) Drive structure of combine
JP4321920B2 (en) Riding work machine
JP3346559B2 (en) Bulb vegetable harvester
JP4407153B2 (en) Combine
JPS5921952Y2 (en) mobile agricultural machinery
JPS6222116Y2 (en)
JPS5931469Y2 (en) Travel transmission structure of mobile agricultural machinery
JP4105349B2 (en) Combine harvesting drive
JPS5819246B2 (en) combine
JPH046514Y2 (en)
JP2003127697A (en) Farm working machinery
JPS5845545Y2 (en) mobile agricultural machinery
KR101138040B1 (en) Operating lever device for power carrier
JP4035565B2 (en) Riding machine
JP4970648B2 (en) Combine
JP2563764Y2 (en) Drive structure of combine