JP2003267255A - Traveling and transmission device of combine - Google Patents
Traveling and transmission device of combineInfo
- Publication number
- JP2003267255A JP2003267255A JP2002072251A JP2002072251A JP2003267255A JP 2003267255 A JP2003267255 A JP 2003267255A JP 2002072251 A JP2002072251 A JP 2002072251A JP 2002072251 A JP2002072251 A JP 2002072251A JP 2003267255 A JP2003267255 A JP 2003267255A
- Authority
- JP
- Japan
- Prior art keywords
- turning
- gear
- clutch
- 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
Links
Landscapes
- Guiding Agricultural Machines (AREA)
- Harvester Elements (AREA)
- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】この発明は、コンバイン等の
走行伝動装置に関し、ギヤ連動機構を有する走行用ミッ
ションケースにおいて、副変速部を経て旋回用クラッチ
と差動ギヤ装置によりマイルド旋回・ブレーキ旋回・ス
ピン旋回の各旋回モードを無段で連続して実行させると
きの旋回半径を、各種の条件に適応させて大〜小に切替
え変更を行うもの等の分野に属する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a traveling transmission device such as a combine and the like. The present invention belongs to the field of making a change in the radius of gyration when continuously performing each of the gyration modes of the spin gyration in a continuously variable manner so as to be changed between large and small in accordance with various conditions.
【0002】[0002]
【従来の技術】従来では、圃場等で走行を行うコンバイ
ン等において、走行用ミッションケースにおける副変速
部で変速された動力を、直進伝動系として、操向クラッ
チを経て常時入り状態の直進用クラッチにより車軸へ伝
動して直進走行を行わせると共に、同じく副変速部で変
速された動力を、旋回伝動系として、旋回時に常時入り
状態の直進用クラッチを切ると同時に旋回用クラッチを
入り状態とし、差動ギヤ装置を経て車軸へ伝動し旋回作
用を行わせるものにおいて、この旋回作用を、操向操作
具の傾動操作角度の小から大へ対応させてマイルド旋回
・ブレーキ旋回・スピン旋回の順に無段で連続して実行
させるもの等が開示されている。2. Description of the Related Art Conventionally, in a combine or the like that travels in a field or the like, the power that has been shifted by an auxiliary transmission unit in a transmission mission case is used as a straight transmission system to pass through a steering clutch and a straight clutch that is always engaged. With this, the power transmitted to the axle is made to travel straight, and the power that has also been shifted by the auxiliary transmission section is used as a turning transmission system, and the turning clutch that is always on during turning is turned off while the turning clutch is turned on. In the case of transmitting to the axle via a differential gear device and performing a turning action, this turning action is made to correspond to the tilt operation angle of the steering operation tool from small to large, and there is no order of mild turn, brake turn, and spin turn. It is disclosed that the steps are continuously executed.
【0003】[0003]
【発明が解決しようとする課題】しかし、このように、
操向操作具の傾動操作角度の小から大へ対応させて、旋
回用クラッチの作用圧が予め設定された1系統の圧力ラ
インに沿って昇圧し、マイルド旋回・ブレーキ旋回・ス
ピン旋回の順に無段で連続して実行させるものでは、副
変速部による変速が、例えば、路上走行用として高速側
に切り替わったときは、この高速状態でスピン旋回を実
行させるときは、急激な旋回作用によりオペレータが振
り回され危険を伴うものであった。[Problems to be Solved by the Invention] However, in this way,
Depending on the tilting operation angle of the steering operation tool from small to large, the working pressure of the swing clutch is increased along a preset pressure line of one system, and there is no order of mild swing, brake swing, and spin swing. In the case of executing continuously in steps, when the speed change by the auxiliary transmission unit is switched to the high speed side for traveling on the road, for example, when executing the spin turn in this high speed state, the operator is caused by a sudden turning action. It was swayed and dangerous.
【0004】また、軟弱な土壌面において、特に旋回作
用を行うとき等に走行クローラが土壌面に沈下して走行
が困難になるとき、この沈下状態では、前記の如く旋回
用クラッチの作用圧を予め設定された1系統の圧力ライ
ンに沿って昇圧させるのみでは、旋回外側の走行クロー
ラがスリップして益々沈下が激しくなり走行不能に陥る
等の不具合が発生する。Further, when the traveling crawler sinks on the soil surface to make it difficult to travel on a soft soil surface, especially when performing a swinging action, in this sinking state, the working pressure of the swinging clutch is increased as described above. If only the pressure is increased along the pressure line of one system set in advance, the traveling crawler on the outside of the turning slips and the sinking becomes more and more serious, resulting in the inability to travel.
【0005】このため、上記の如き、オペレータの危険
に対する防止と、軟弱な土壌面での走行不能に対する改
善を行うものである。Therefore, as described above, the operator's danger is prevented and the inability to run on a soft soil surface is improved.
【0006】[0006]
【課題を解決するための手段】請求項1の発明は、副変
速部1を経て旋回用クラッチ2と差動ギヤ装置3等によ
りマイルド旋回・ブレーキ旋回・スピン旋回の各旋回モ
ードを無段で連続して実行可能なギヤ連動機構を有する
走行用ミッションケース4において、傾動操作により各
旋回モードを連続して実行させる操向操作具5の操作角
度に対応させた旋回半径を、該副変速部1の変速切替え
に応じて大〜小に変更可能とする旋回制御手段6を設け
たことを特徴とするコンバイン等の走行伝動装置の構成
とする。According to a first aspect of the present invention, the turning clutch 2 and the differential gear device 3 and the like through the auxiliary speed change unit 1 make the turning modes of mild turning, braking turning, and spin turning stepless. In the traveling mission case 4 having the gear interlocking mechanism that can be continuously executed, the turning radius corresponding to the operation angle of the steering operation tool 5 that continuously executes each turning mode by the tilting operation is set to the sub-transmission unit. A traveling transmission device such as a combine is characterized by being provided with a turning control means 6 which can be changed to a large or small value in accordance with a gear shift of No.1.
【0007】このような構成により、コンバイン等にお
いて、走行用ミッションケース4の副変速部1で変速さ
れた動力によって圃場又は路上等で直進走行と旋回作用
を行わせるが、この旋回作用を、オペレータによる操向
操作具5の傾動操作角度の小から大への操作によって、
旋回用クラッチ2の接続圧を上昇させ旋回半径を大から
小へ、マイルド旋回・ブレーキ旋回・スピン旋回の順に
無段で連続して実行させる。With such a configuration, in a combine or the like, the power that has been shifted by the auxiliary transmission section 1 of the traveling mission case 4 causes straight traveling and a turning action in the field or on the road, and this turning action is performed by the operator. When the tilting operation angle of the steering operation tool 5 is changed from small to large,
The connection pressure of the turning clutch 2 is increased to change the turning radius from large to small, and the steps are continuously and continuously executed in the order of mild turning, braking turning, and spin turning.
【0008】この各旋回モードによる連続旋回を、コン
トローラ等に設けた旋回制御手段6により設定された、
副変速部1の変速による、例えば、低・中速の作業速で
は、マイルド旋回からブレーキ旋回を経てスピン旋回ま
で連続して実行させる旋回用クラッチ2の全接続圧ライ
ンと、高速の路上走行速では、マイルド旋回からブレー
キ旋回までの実行に止める旋回用クラッチ2の調整接続
圧ラインとを自動的に切り替え旋回作用を行わせる。The continuous turning in each turning mode is set by the turning control means 6 provided in the controller or the like.
For example, at a low / medium working speed due to the shift of the sub-transmission unit 1, all connection pressure lines of the turning clutch 2 that are continuously executed from a mild turn to a brake turn to a spin turn, and a high road speed. Then, the adjustment connection pressure line of the turning clutch 2 for stopping the execution from the mild turning to the brake turning is automatically switched to perform the turning action.
【0009】請求項2の発明は、副変速部1を経て旋回
用クラッチ2と差動ギヤ装置3等によりマイルド旋回・
ブレーキ旋回・スピン旋回の各旋回モードを無段で連続
して実行可能なギヤ連動機構を有する走行用ミッション
ケース4において、傾動操作により各旋回モードを連続
して実行させる操向操作具5の操作角度に対応させた旋
回半径を、大〜小交互に脈動状態に切替え可能とする交
互制御手段7を設けたことを特徴とする請求項1記載の
コンバイン等の走行伝動装置の構成とする。According to the second aspect of the present invention, the sub-transmission unit 1 is used to provide a mild turning / turning by the turning clutch 2 and the differential gear device 3.
In the traveling mission case 4 having the gear interlocking mechanism capable of continuously executing the respective turning modes of the brake turning and the spin turning steplessly, the operation of the steering operation tool 5 for continuously executing the respective turning modes by the tilting operation. A traveling transmission device such as a combine according to claim 1, characterized in that an alternation control means (7) is provided for enabling the turning radius corresponding to the angle to be alternately switched between large and small in a pulsating state.
【0010】このような構成により、コンバイン等にお
いて、走行用ミッションケース4の副変速部1で変速さ
れた動力によって圃場又は路上等で直進走行と旋回作用
を行わせるが、この旋回作用を、オペレータによる操向
操作具5の傾動操作角度の小から大への操作によって、
旋回用クラッチ2の接続圧を上昇させ旋回半径が大から
小へ、マイルド旋回・ブレーキ旋回・スピン旋回の順に
無段で連続して実行させる。With such a configuration, in a combine or the like, the power that has been shifted by the auxiliary transmission section 1 of the traveling mission case 4 causes straight traveling and a turning action in the field or on the road, and this turning action is performed by the operator. When the tilting operation angle of the steering operation tool 5 is changed from small to large,
The connecting pressure of the turning clutch 2 is increased to increase the turning radius from large to small, and the steps are continuously executed in a stepless manner in the order of mild turning, brake turning, and spin turning.
【0011】この各旋回モードによる連続旋回を、コン
トローラ等に設けた交互制御手段7の設定により、交互
スイッチ等をONしたときは、操向操作具5の傾動操作
による操作角度を変更することなく、旋回半径を、例え
ば、マイルド旋回からブレーキ旋回へ,ブレーキ旋回か
らマイルド旋回へと、旋回用クラッチ2の接続圧の昇降
を交互に脈動状態となるよう自動的に切り替え旋回作用
を行わせる。When the alternate switch or the like is turned on by setting the alternate control means 7 provided in the controller or the like for the continuous swing in each of the swing modes, the operation angle by the tilting operation of the steering operation tool 5 is not changed. , The turning radius is automatically changed from the mild turning to the brake turning and from the brake turning to the mild turning so that the connection pressure of the turning clutch 2 is alternately raised and lowered so as to be in a pulsating state, and the turning action is performed.
【0012】[0012]
【発明の効果】請求項1の発明では、上記作用の如く、
コンバイン等において圃場又は路上等で直進走行と旋回
作用を行わせるが、この旋回作用は操向操作具5の傾動
操作によって旋回用クラッチ2の接続圧を上昇させ旋回
半径を大から小へ無段で連続して実行させる。According to the invention of claim 1, as described above,
In a combine or the like, a straight traveling and a turning action are performed in a field or on a road. This turning action increases the connection pressure of the turning clutch 2 by tilting the steering operation tool 5 to continuously change the turning radius from large to small. To run continuously.
【0013】この連続旋回時に旋回制御手段6により、
副変速部1の変速による低・中速の作業速での全接続圧
ラインと、高速の路上走行速での調整接続圧ラインとの
2系統の接続圧ラインを自動的に切り替え旋回作用を行
わせることにより、低・中速側ではスピン旋回までのフ
ル旋回を作用可能とする機動力の向上と、高速側ではス
ピン旋回を非作用状態とし急激な旋回作用を回避可能と
する安全性の向上とを両立させ、効率の良い旋回作用を
行わせることができる。During this continuous turning, the turning control means 6
A turning action is performed by automatically switching between two connection pressure lines, a total connection pressure line at low / medium working speeds by the shift of the auxiliary transmission unit 1 and an adjustment connection pressure line at high road traveling speed. By doing so, on the low / medium speed side, the maneuverability that allows full swing up to the spin turn can be improved, and on the high speed side, the spin turn can be disabled and safety can be improved by avoiding a sudden turn effect. It is possible to achieve both and to perform an efficient turning action.
【0014】請求項2の発明では、上記作用の如く、コ
ンバイン等において圃場又は路上等で直進走行と旋回作
用を行わせるが、この旋回作用は操向操作具5の傾動操
作によって旋回用クラッチ2の接続圧を上昇させ旋回半
径を大から小へ無段で連続して実行させる。According to the second aspect of the present invention, as described above, the straight traveling and the turning action are performed in the combine or the like in the field or on the road, and the turning action is performed by the tilting operation of the steering operation tool 5. The connection pressure is increased and the turning radius is continuously changed from large to small.
【0015】この連続旋回時に交互制御手段7により、
交互スイッチ等をONしたときは、操向操作具5の傾動
操作による操作角度を変更することなく、旋回用クラッ
チ2の接続圧の昇降を自動的に交互に切り替え、旋回半
径を、例えば、マイルド旋回とブレーキ旋回の間を脈動
状態に変更させることにより、旋回内側の走行クローラ
の駆動力を変化させて(又は断続的に駆動して)、土壌
面への沈下状態から脱出させて走行不能を回避すること
ができる。During this continuous turning, the alternate control means 7
When the alternate switch or the like is turned on, the connection pressure of the turning clutch 2 is automatically changed alternately between the rising and falling of the connecting pressure of the turning clutch 2 without changing the operation angle by the tilting operation of the steering operation tool 5, and the turning radius is set to, for example, a mild value. By changing the pulsating state between turning and braking turning, the driving force of the running crawler inside the turning is changed (or intermittently driven) to escape from the state of sinking to the soil surface and disable running. It can be avoided.
【0016】また、旋回内側の車軸の回転数をフィード
バックしてアンチロック制御を行う必要がなく、制御を
簡素化することができる。Further, it is not necessary to feed back the rotational speed of the axle on the inside of the turn to perform antilock control, and the control can be simplified.
【0017】[0017]
【発明の実施の形態】以下に、この発明の実施例をコン
バインについて図面に基づき説明する。図7はコンバイ
ンの全体構成を示すもので、車台9の下部側に土壌面を
走行する左右一対の走行クローラ10を張設した走行装
置11を配設すると共に、該車台9上にフィードチェン
12に挟持して搬送供給される穀稈の脱穀を行い、この
脱穀された穀粒を選別回収して一時貯留するグレンタン
ク13と、このタンク13に貯留された穀粒を機外へ排
出する排穀オーガ14を備えた脱穀装置15を載置し、
この脱穀装置15の後端部に排藁処理装置16を装架構
成させる。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 7 shows the overall structure of the combine, in which a traveling device 11 in which a pair of left and right traveling crawlers 10 traveling on the soil surface is stretched is provided on the lower side of the chassis 9, and a feed chain 12 is provided on the chassis 9. The grain culms that are sandwiched between and conveyed to be threshed are threshed, and the grain tank 13 that sorts and collects the threshed grains and temporarily stores them, and the discharge that discharges the grains stored in this tank 13 to the outside of the machine. A threshing device 15 equipped with a grain auger 14 is placed,
A straw processing device 16 is mounted on the rear end of the threshing device 15.
【0018】該脱穀装置15の前方に、前端側から未刈
穀稈を分草する分草体17と、分草された穀稈を引き起
こす引起部18と、引き起こされた穀稈を刈り取る刈刃
部19と、この刈り取られた穀稈を掻き込むと共に、搬
送途上において扱深さを調節して搬送される穀稈を引き
継いで該フィードチェン12へ受け渡しする供給調節搬
送部20等を有する刈取装置21を、油圧駆動による刈
取昇降シリンダ22により土壌面に対して昇降自在なる
よう該車台9の前端部へ懸架構成させる。In front of the threshing device 15, a grass body 17 for weeding uncut grain culms from the front end side, a raising portion 18 for causing the weeded grain culms, and a cutting blade portion for cutting the caused grain culms. A cutting device 21 having 19 and a supply adjusting / conveying unit 20 that scrapes the cut grain culm, takes over the grain culm that is conveyed while adjusting the handling depth during the conveyance, and transfers the grain culm to the feed chain 12. Is suspended from the front end of the chassis 9 so that it can be moved up and down with respect to the soil surface by a hydraulically driven reaping lift cylinder 22.
【0019】該刈取装置21の一側にコンバインの操作
制御を行う操作装置23と、この操作のための操作席2
4を設け、この操作席24の後方側には前記グレンタン
ク13を配置し、下方側にはエンジン25を搭載すると
共に、該操作装置23と操作席24を覆うキャビン26
を配置する。これら走行装置11,脱穀装置15,刈取
装置21,操作装置23,エンジン25,キャビン26
等によってコンバインの車体27を構成させる。An operating device 23 for controlling the operation of the combine on one side of the reaping device 21, and an operating seat 2 for this operation.
4 is provided, the Glen tank 13 is arranged on the rear side of the operation seat 24, the engine 25 is mounted on the lower side, and the cabin 26 for covering the operation device 23 and the operation seat 24 is provided.
To place. These traveling device 11, threshing device 15, harvesting device 21, operating device 23, engine 25, cabin 26
The combine body 27 is configured by the above.
【0020】該走行装置11は車台9の前部側に、図3
に示す如く、走行用ミッションケース4を装架してお
り、このミッションケース4の上部側に油圧式無段変速
装置29を連動可能に接合し、この無段変速装置29の
可変ポンプ29aに軸止した入力プーリ30へ該エンジ
ン25から動力を伝達可能に伝動ベルト等を張設すると
共に、この可変ポンプ29aによって一体的に駆動され
る可変モータ29bに、第1軸としての入力軸31を連
動連結して構成させる。、該ミッションケース4のギヤ
連動機構は、入力軸31に軸止した入力ギヤ32と、第
2軸としての変速駆動軸33にスプライン等により摺動
可能に軸回転させる三連の変速伝動ギヤ34の大径ギヤ
とを噛合連動させると共に、この摺動する変速伝動ギヤ
34と、第3軸としての変速伝動軸35に軸止する高速
駆動ギヤ36,中速駆動ギヤ37,低速駆動ギヤ38と
を各々噛合連動させることによって高速,中速,低速に
変速する副変速部1を構成させる。The traveling device 11 is provided on the front side of the chassis 9 as shown in FIG.
As shown in FIG. 2, a traveling mission case 4 is mounted, and a hydraulic continuously variable transmission 29 is operably joined to an upper side of the mission case 4, and a variable pump 29a of the continuously variable transmission 29 has a shaft. A transmission belt or the like is stretched so that power can be transmitted from the engine 25 to the stopped input pulley 30, and an input shaft 31 as a first shaft is interlocked with a variable motor 29b that is integrally driven by the variable pump 29a. Connect and configure. The gear interlocking mechanism of the mission case 4 includes an input gear 32 fixed to an input shaft 31 and a triple transmission transmission gear 34 for axially slidably rotating a transmission drive shaft 33 as a second shaft by a spline or the like. Of the large-diameter gear, and the sliding transmission gear 34, the high-speed drive gear 36, the medium-speed drive gear 37, and the low-speed drive gear 38 that are fixed to the transmission transmission shaft 35 as the third shaft. The sub-transmission unit 1 that shifts to high speed, medium speed, and low speed is configured by interlocking with each other.
【0021】直進伝動系として、該変速伝動軸35の高
速駆動ギヤ36と中速駆動ギヤ37との間に軸止する変
速伝動ギヤ39と、第4A軸としての操向クラッチ軸4
0のセンターに軸止する内径左右側にクラッチ爪41a
を有する操向センタギヤ41とを噛合連動させると共
に、該操向センタギヤ41の両側に各々左右の操向クラ
ッチ42を左右摺動可能に遊転軸承して構成させる。As a linear transmission system, a speed change transmission gear 39 which is fixed between a high speed drive gear 36 and a medium speed drive gear 37 of the speed change transmission shaft 35, and a steering clutch shaft 4 as a fourth A-axis.
Clutch pawls 41a on the left and right sides of the inner diameter that locks in the center of 0
And a left and right steering clutches 42 are slidably supported on both sides of the steering center gear 41 so as to be slidable from side to side.
【0022】該左右の操向クラッチ42のクラッチギヤ
42aを、このクラッチギヤ42aの外端部に設けた左
右のシフタ溝42bに嵌入した左右のシフタ43の作用
により、操向センタギヤ41のクラッチ爪41aに各々
噛合接続して入・切させ直進時の左右舵取り及び操向旋
回を行わせると共に、左右の操向クラッチ42の接続復
帰を補助する左右のリターンスプリング44を装填して
構成させる。なお、28は前記変速駆動軸33に軸止し
た一方向回転の刈取駆動プーリを示す。The clutch gear 42a of the left and right steering clutch 42 is fitted into the left and right shifter grooves 42b provided at the outer ends of the clutch gear 42a. 41a is engaged and disengaged with each other to be turned on and off to perform left and right steering and steering turning when going straight, and left and right return springs 44 for assisting connection and return of the left and right steering clutches 42 are mounted. Reference numeral 28 denotes a unidirectional rotation reaping drive pulley which is fixed to the variable speed drive shaft 33.
【0023】該左右の操向クラッチ42のクラッチギヤ
42aと、第7軸としての左右の車軸45の一端部に各
々軸止した車軸ギヤ46とを噛合連動させると共に、こ
の左右の車軸45の外部他端部に前記走行クローラ10
を駆動する左右の走行スプロケット47を軸止して構成
させる。A clutch gear 42a of the left and right steering clutch 42 is meshed with an axle gear 46 which is fixed to one end of each of the left and right axles 45 as a seventh shaft, and the outside of the left and right axles 45 is connected. The traveling crawler 10 is provided at the other end.
The left and right traveling sprockets 47 for driving the shaft are constructed by axial stop.
【0024】次に、旋回伝動系として、前記変速伝動軸
35の変速伝動ギヤ39と、第4軸としての中間伝動軸
48に軸回転させる二連の中間伝動ギヤ49の直進系の
大径ギヤ49aとを噛合連動させると共に、この大径ギ
ヤ49aと噛合連動する、直進ギヤ50及び連動クラッ
チとしての一方の直進用クラッチ51を両端部に固定し
た長円筒メタル52を、第5軸としての旋回クラッチ軸
53に遊転軸承して構成させる。Next, as a turning transmission system, a large-diameter linear gear of a speed change transmission gear 39 of the speed change transmission shaft 35 and two intermediate transmission gears 49 for axial rotation about an intermediate transmission shaft 48 as a fourth shaft. The long cylindrical metal 52, which is fixed to both ends of the straight-moving gear 50 and one straight-moving clutch 51 as an interlocking clutch, which meshes with the large-diameter gear 49a, is engaged with the large-diameter gear 49a. The clutch shaft 53 is configured to be idle.
【0025】該中間伝動ギヤ49の旋回系の小径ギヤ4
9bと噛合連動する旋回ギヤ55と、連動クラッチとし
ての他方の旋回用クラッチ2を隣接して固定した短円筒
メタル56を、長円筒メタル52の外周に重設して遊転
軸承させると共に、旋回用クラッチ2と直進用クラッチ
51との間に、直進用クラッチ51を常時作動可能に押
圧するバネ57を配設し、該両クラッチ51,2の外枠
リング58を旋回クラッチ軸53の一方の軸端部に軸止
して構成させる。Small diameter gear 4 of the swivel system of the intermediate transmission gear 49
A short cylinder metal 56, in which an orbiting gear 55 interlockingly engaged with 9b and the other orbiting clutch 2 as an interlocking clutch is fixed adjacently, is provided on the outer periphery of the long cylinder metal 52 so as to support the idle shaft, and to rotate. A spring 57 for urging the straight-travel clutch 51 to be always operable is disposed between the vehicle clutch 2 and the straight-travel clutch 51, and the outer frame rings 58 of the both clutches 51 and 52 are connected to one of the turning clutch shafts 53. A shaft is fixed to the end of the shaft.
【0026】該旋回クラッチ軸53の他端部に軸止した
旋回駆動ギヤ59と、差動ギヤ装置3においてデファレ
ンシャルギヤ3aを内装したデフケース3bを回転駆動
するデフケースギヤ3cとを噛合連動させ、左右方向の
デファレンシャルギヤ3aを、第6軸としてのデフ支軸
61に遊転軸承すると共に、このデファレンシャルギヤ
3aのボス部に左右のデフ出力ギヤ62を各々軸止し、
このデフ出力ギヤ62と前記車軸ギヤ46とを噛合連動
して構成させる。The turning drive gear 59 fixed to the other end of the turning clutch shaft 53 and the differential case gear 3c for rotationally driving the differential case 3b in which the differential gear 3a is installed in the differential gear device 3 are meshed and interlocked with each other. Direction differential gear 3a is idle-supported on a differential support shaft 61 as a sixth shaft, and the left and right differential output gears 62 are axially fixed to the boss portion of this differential gear 3a, respectively.
The differential output gear 62 and the axle gear 46 are configured to mesh with each other.
【0027】該両クラッチ51,2の外枠リング58に
隣接して、カムの作用により該リング58を押圧して制
動する駐車ブレーキ63を配設すると共に、この駐車ブ
レーキ63を作動させるブレーキレバー64を該ミッシ
ョンケース4の外部に取り付けて構成させる。A parking brake 63 is provided adjacent to the outer frame ring 58 of the both clutches 51 and 52 to press and brake the ring 58 by the action of a cam, and a brake lever for operating the parking brake 63. 64 is attached to the outside of the mission case 4 and configured.
【0028】車体27の操向旋回作用を左右側への傾動
操作により実行させる操向操作具5としてのパワステレ
バー5を前記操作装置23の一側に配設して構成させ
る。図2に示す如く、CPUを主体的に配して自動回路
の演算制御を行うと共に、前記副変速部1の変速切替え
に応じて旋回半径を大〜小に変更させる旋回制御手段6
と、該パワステレバー5の傾動操作角度を変更すること
なく旋回半径を大〜小交互に脈動状態に切り替えさせる
交互制御手段7とを内蔵するコントローラ65を設けて
構成させる。A power steering lever 5 as a steering operation tool 5 for performing the steering and turning action of the vehicle body 27 by tilting operation to the left and right sides is arranged at one side of the operating device 23. As shown in FIG. 2, a turning control means 6 is provided mainly for arranging a CPU to perform arithmetic control of an automatic circuit and to change a turning radius from large to small in accordance with a shift change of the sub transmission unit 1.
Further, the controller 65 is provided with the built-in controller 65, and the alternate control means 7 for switching the turning radius to the pulsating state alternately between large and small without changing the tilting operation angle of the power steering lever 5.
【0029】該コントローラ65の入力側に、該副変速
部1の変速位置を各々検出する低速・中速・高速センサ
66a,66b,66cと、該交互制御手段7による脈
動状態の旋回作用を開始させる交互スイッチ67とを各
々接続すると共に、その出力側に、前記バネ57により
常時入りとしている直進用クラッチ51を切ると同時
に、旋回用クラッチ2を入り作用させる旋回用電磁油圧
弁68を接続して構成させる。At the input side of the controller 65, low-speed / medium-speed / high-speed sensors 66a, 66b, 66c for respectively detecting the shift position of the sub-transmission unit 1 and the pulsating turning operation by the alternate control means 7 are started. Each of them is connected to an alternation switch 67 for switching, and the output side thereof is connected to a turning electromagnetic hydraulic valve 68 for turning on and operating the turning clutch 2 at the same time as disengaging the straight clutch 51 which is always turned on by the spring 57. To configure.
【0030】エンジン25からの動力を、油圧式無段変
速装置29の可変ポンプ29aへ入力し、この可変ポン
プ29aによって駆動される油圧モータ29bによる主
変速動力を入力軸31に入力連動し、この入力軸31の
入力ギヤ32から変速駆動軸33に摺動する三連の変速
伝動ギヤ34の大径ギヤに連動し、この変速伝動ギヤ3
4を摺動させて高速駆動ギヤ36,中速駆動ギヤ37,
低速駆動ギヤ38に各々連動させることによって副変速
駆動を行わせる。The power from the engine 25 is input to the variable pump 29a of the hydraulic continuously variable transmission 29, and the main shift power by the hydraulic motor 29b driven by the variable pump 29a is input and interlocked with the input shaft 31. The transmission gears 3 are interlocked with the large-diameter gears of the three speed change transmission gears 34 sliding from the input gear 32 of the input shaft 31 to the speed change drive shaft 33.
4 by sliding high speed drive gear 36, medium speed drive gear 37,
The sub-shift drive is performed by interlocking with each of the low speed drive gears 38.
【0031】この副変速された動力によって車体27を
直進させるときは、変速伝動軸35の変速伝動ギヤ39
から操向クラッチ軸40の操向センタギヤ41に連動
し、この操向センタギヤ41に左右の操向クラッチ42
のクラッチギヤ42aを噛合接続させ、このクラッチギ
ヤ42aから左右の車軸ギヤ46への連動により左右の
走行スプロケット47を同時に駆動させる。When the vehicle body 27 is moved straight by the power that has been sub-shifted, the shift transmission gear 39 of the shift transmission shaft 35 is used.
To the steering center gear 41 of the steering clutch shaft 40, and the left and right steering clutches 42 are connected to the steering center gear 41.
The clutch gear 42a is engaged with the clutch gear 42a, and the left and right traveling sprockets 47 are simultaneously driven by interlocking the clutch gear 42a with the left and right axle gears 46.
【0032】一方、該変速伝動軸35の変速伝動ギヤ3
9から中間伝動軸48の中間伝動ギヤ49の直進系の大
径ギヤ49aを介して直進ギヤ50に連動し、この直進
ギヤ50から長円筒メタル52を介して、バネ57によ
って常時入りとしている直進用クラッチ51の作用によ
り旋回クラッチ軸53を駆動させる。On the other hand, the speed change transmission gear 3 of the speed change transmission shaft 35
9 to the intermediate transmission gear 49 of the intermediate transmission shaft 48 through the linear large-diameter gear 49a of the intermediate transmission gear 49, which is interlocked with the linear movement gear 50. The swing clutch shaft 53 is driven by the action of the clutch 51 for use.
【0033】この旋回クラッチ軸53の駆動により旋回
駆動ギヤ59から差動ギヤ装置3におけるデフケース3
bのデフケースギヤ3cに連動すると共に、このデフケ
ースギヤ3cからデファレンシャルギヤ3aの作用によ
り差動連動される左右のデフ出力ギヤ62を、前記左右
の車軸ギヤ46の回転に対し各々同速回転となるよう組
み合わせて連動させる。この連動により該操向クラッチ
42の入・切によるショックを緩和することができる。By driving the orbiting clutch shaft 53, the orbiting drive gear 59 to the differential case 3 in the differential gear unit 3 are driven.
The left and right differential output gears 62 that are interlocked with the differential case gear 3c of FIG. 3b and are differentially interlocked by the action of the differential gear 3a from the differential case gear 3c are rotated at the same speed with respect to the rotation of the left and right axle gears 46, respectively. To work together. This interlocking can alleviate the shock caused by turning on / off the steering clutch 42.
【0034】次に、車体27を旋回させるときは、該変
速伝動軸35の変速伝動ギヤ39から中間伝動軸48の
中間伝動ギヤ49の旋回系の小径ギヤ49bを介して旋
回ギヤ55に連動し、この旋回ギヤ55から短円筒メタ
ル56を介し旋回用クラッチ2を旋回用電磁油圧弁68
により油圧作用させ、該バネ57の押圧を解除して直進
用クラッチ51を切ると同時に旋回用クラッチ2の入り
により旋回クラッチ軸53を駆動させる。Next, when turning the vehicle body 27, the speed change transmission gear 39 of the speed change transmission shaft 35 is interlocked with the turning gear 55 via the small diameter gear 49b of the intermediate transmission gear 49 of the intermediate transmission shaft 48 of the turning system. , The turning clutch 2 is connected to the turning electromagnetic hydraulic valve 68 from the turning gear 55 via the short cylindrical metal 56.
To release the pressing force of the spring 57 to disengage the straight clutch 51, and at the same time, to engage the turning clutch 2 to drive the turning clutch shaft 53.
【0035】この旋回クラッチ軸53の駆動により旋回
駆動ギヤ59から差動ギヤ装置3におけるデフケース3
bのデフケースギヤ3cに連動すると共に、このデフケ
ースギヤ3cからデファレンシャルギヤ3aの作用によ
り差動連動される左右のデフ出力ギヤ62を駆動させ
る。By driving the orbiting clutch shaft 53, the orbiting drive gear 59 to the differential case 3 in the differential gear unit 3 are driven.
The left and right differential output gears 62 that are interlocked with the differential case gear 3c of b and are differentially interlocked by the action of the differential gear 3a are driven from the differential case gear 3c.
【0036】この駆動により、例えば、左へ旋回すると
きは、左の操向クラッチ42を切ると同時に、旋回用ク
ラッチ2の入りを半接続状態から完全接続状態まで変化
させることにより、左のデフ出力ギヤ62により左の車
軸ギヤ46の回転数を、通常回転の右車軸ギヤ46に対
し、緩やかに減速回転させるマイルド旋回,停止を行う
ブレーキ旋回,1/4逆回転させるスピン旋回の各旋回
モードを、車体27を停止させることなく無段で連続し
て円滑な旋回作用を実行させることができる。By this drive, for example, when turning to the left, the left steering clutch 42 is disengaged, and at the same time, the turning clutch 2 is turned on from a semi-connected state to a fully-connected state so that the left diff is changed. With the output gear 62, the rotational speed of the left axle gear 46 is gently decelerated with respect to the normal rotation right axle gear 46, a mild rotation, a brake rotation for stopping, and a spin rotation for reverse rotation of 1/4. Therefore, it is possible to continuously and smoothly execute the turning action without stopping the vehicle body 27.
【0037】なお、直進時において、左右の操向クラッ
チ42の切りの段階で、各旋回モードに連続して操向微
調整モードにより左右の舵取りを行う操向作用を実行さ
せることができる。このようなコンバイン作業における
旋回作用時に、該パワステレバー5の傾動操作角度の小
から大への操作によって、通常では、前記旋回用クラッ
チ2の接続圧を予め設定された1系統の圧力ラインに沿
って昇圧させ、旋回半径を大から小へ、マイルド旋回・
ブレーキ旋回・スピン旋回の順に無段で連続して実行さ
せるが、このとき、該副変速部1を高速側へ切り替えス
ピン旋回を実行させるときは、急激な旋回作用によりオ
ペレータが危険である。It should be noted that, when the vehicle is traveling straight ahead, at the stage of disengagement of the left and right steering clutches 42, the steering action for steering left and right can be executed in succession to each turning mode in the steering fine adjustment mode. At the time of the turning action in such a combine operation, the tilting operation angle of the power steering lever 5 is usually operated from a small angle to a large angle, so that the connection pressure of the turning clutch 2 is normally set along a preset pressure line of one system. To increase the turning radius from large to small, mild turning
The brake turn and the spin turn are continuously performed in a stepless manner. At this time, when the sub-transmission unit 1 is switched to the high speed side and the spin turn is performed, the operator is dangerous due to a sudden turning action.
【0038】この危険を回避するため、各旋回モードに
よる連続旋回を行うときに、該副変速部1の変速位置を
低速・中速・高速センサ66a,66b,66cにより
各々検出したときは、コントローラ65に内蔵した旋回
制御手段6を作用させる。この旋回制御手段6を作用に
より、図1の線図に示す如く、低・中速の作業速では、
マイルド旋回からブレーキ旋回を経てスピン旋回まで連
続して実行させる旋回用クラッチ2の全接続圧ラインa
と、高速の路上走行速では、マイルド旋回からブレーキ
旋回までの実行に止める旋回用クラッチ2の調整接続圧
ラインbとを自動的に切り替えて旋回作用を行わせる。In order to avoid this danger, when performing continuous turning in each turning mode, when the shift position of the sub transmission unit 1 is detected by the low speed / medium speed / high speed sensors 66a, 66b, 66c, respectively, the controller The turning control means 6 built in 65 is operated. By the action of the turning control means 6, as shown in the diagram of FIG. 1, at low and medium working speeds,
All connecting pressure lines a of the turning clutch 2 for continuously executing from mild turning to brake turning to spin turning
Then, at a high road speed, the adjustment connection pressure line b of the turning clutch 2 that stops execution from mild turning to braking turning is automatically switched to perform the turning action.
【0039】このように、連続旋回時に旋回制御手段6
によって、低・中速での全接続圧ラインaと、高速での
調整接続圧ラインbとの2系統の圧力ラインを自動的に
切り替えることにより、低・中速側ではスピン旋回まで
のフル旋回を作用可能とする機動力の向上と、高速側で
はスピン旋回を非作用状態とし急激な旋回作用を回避可
能とする安全性の向上とを両立させ、効率の良い旋回作
用を行わせることができる。In this way, the turning control means 6 is used during continuous turning.
By automatically switching between the two pressure lines, the low and medium speed full connection pressure line a and the high speed adjustment connection pressure line b It is possible to achieve an efficient swivel action by improving both the mobility that makes it possible to act and the safety that makes it possible to avoid a sudden swirling action by making spin swirl inactive on the high speed side. .
【0040】また、コンバインの作業時に軟弱な土壌面
等において旋回作用を行うときに、走行クローラ10が
土壌面に沈下して走行が困難になるという不具合が発生
し易いが、この不具合発生時に交互スイッチ67をON
させることにより、コントローラ65に内蔵した交互制
御手段7を作用させる。Further, when a turning action is performed on a soft soil surface during the operation of the combine, the running crawler 10 sinks on the soil surface, which makes it difficult to run. Switch 67 ON
By doing so, the alternate control means 7 incorporated in the controller 65 is operated.
【0041】この交互制御手段7の作用により、前記パ
ワステレバー5の傾動操作による操作角度を変更するこ
となく、旋回用クラッチ2の接続圧の昇降を自動的に交
互に切り替え、旋回半径を、例えば、マイルド旋回とブ
レーキ旋回の間を脈動状態に変更させることにより、旋
回内側の走行クローラ10の駆動力を変化させて(又は
断続的に駆動して)、土壌面への沈下状態から脱出させ
走行不能を回避することができる。By the action of the alternate control means 7, the connection pressure of the turning clutch 2 is automatically switched alternately up and down without changing the operation angle by the tilting operation of the power steering lever 5 to change the turning radius, for example. By changing the pulsating state between the mild turn and the brake turn, the driving force of the running crawler 10 on the inside of the turn is changed (or intermittently driven) to escape from the sinking state to the soil surface and run. Impossible can be avoided.
【0042】なお、旋回内側の車軸の回転数をフィード
バックしてアンチロック制御を行う必要がなく、制御を
簡素化することができる。また、前記差動ギヤ装置3や
油圧系の故障等によって、バネ57により常時入りとし
ている直進用クラッチ51が切れなくなると旋回不能と
なる。The anti-lock control need not be performed by feeding back the rotation speed of the axle on the inside of the turn, and the control can be simplified. If the linear clutch 51, which is always engaged by the spring 57, cannot be disengaged due to a failure of the differential gear device 3 or the hydraulic system, it becomes impossible to turn.
【0043】そこで、この不具合を防止するため、図4
に示す如く、前記ミッションケース4のギヤ連動機構に
おいて、旋回伝動系として、前記第3軸としての変速伝
動軸35の変速伝動ギヤ39と、第4軸としての中間伝
動軸48にスプライン等により摺動可能に軸回転させる
二連の中間伝動ギヤ49の直進系の大径ギヤ49aとを
噛合連動させる。Therefore, in order to prevent this problem, FIG.
As shown in FIG. 5, in the gear interlocking mechanism of the transmission case 4, as a swivel transmission system, the transmission transmission gear 39 of the transmission transmission shaft 35 as the third shaft and the intermediate transmission shaft 48 as the fourth shaft are slid by a spline or the like. The two intermediate transmission gears 49 for rotatably rotating the shaft are meshed with the large-diameter linear gear 49a.
【0044】該中間伝動ギヤ49の直進系の大径ギヤ4
9aと旋回系の小径ギヤ49bを、第5軸としての旋回
クラッチ軸53に遊転軸承する直進用クラッチ51と連
動する直進ギヤ50、及び旋回用クラッチ2と連動する
旋回ギヤ55に各々非噛合となるよう摺動させ、直進用
クラッチ51と旋回用クラッチ2を共に切り状態とする
ことにより、該差動ギヤ装置3がフリーの状態となるた
め前記操向クラッチ42のみの作用によって旋回が可能
となり、緊急時の対応として活用できる。Large diameter gear 4 of the linear system of the intermediate transmission gear 49
9a and the small-diameter gear 49b of the swivel system are not meshed with the straight-moving gear 50 that interlocks with the straight-travel clutch 51 that idles on the swivel clutch shaft 53 as the fifth shaft, and the swivel gear 55 that interlocks with the swivel clutch 2. The differential gear device 3 is in a free state by sliding the clutch 51 for straight advancement and the clutch 2 for swivel in the disengaged state so that the steering can be performed only by the operation of the steering clutch 42. It can be used as an emergency response.
【0045】また、上記と異なる別の走行用ミッション
ケース70のギヤ連動機構として、図5に示す如く、左
右側に配置した左右の油圧式無段変速装置71の出力軸
71aに軸止した左右の出力ギヤ72と、アイドル軸7
3に軸止する左右のアイドルギヤ74とを各々噛合連動
させると共に、このアイドルギヤ74の一方側に左右の
回転数を調整するための直進用クラッチ74aを内設し
アイドル軸73に軸止して構成させる。As another gear interlocking mechanism of the traveling mission case 70, which is different from the above, as shown in FIG. 5, the left and right hydraulic shaftless transmissions 71 of the left and right hydraulic continuously variable transmissions 71 are axially fixed to each other. Output gear 72 and idle shaft 7
The left and right idle gears 74 that are axially locked to 3 are meshed and interlocked with each other, and a straight clutch 74a for adjusting the left and right rotational speeds is internally provided on one side of the idle gear 74 to lock the idle shaft 73 to the idle shaft 73. To configure.
【0046】該左右のアイドルギヤ74と、減速軸75
に軸承する左右の減速ギヤ76とを噛合連動させ、更
に、左右の減速ギヤ76と、左右の車軸77の一端部に
各々軸止した左右の車軸ギヤ78とを噛合連動させると
共に、該左右の減速ギヤ76に各々一方向回転クラッチ
76aを内設し減速軸75に軸止して構成させる。The left and right idle gears 74 and the reduction shaft 75
The left and right reduction gears 76 that are supported by the left and right gears are meshed with each other, and the left and right reduction gears 76 are also meshed with the left and right axle gears 78 that are respectively fixed to one ends of the left and right axles 77. Each reduction gear 76 is internally provided with a one-way rotation clutch 76a, and is configured to be fixed to the reduction shaft 75 by a shaft.
【0047】なお、79は、該左右の無段変速装置71
に各々動力を入力する左右の入力プーリ、80は、該減
速軸75に軸止した刈取駆動プーリ、81は、該左右の
車軸77に各々軸止した左右の走行スプロケットを示
す。このような構成により、左右の無段変速装置71か
ら伝達される動力を、左右のアイドルギヤ74から左右
の減速ギヤ76を経て、左右の車軸ギヤ78を介して左
右の走行スプロケット81へ伝達させる。この動力伝達
により、直進走行時には、左右の伝動系の回転速度を直
進用クラッチ74aの作用によって一致させ直進性を損
なわないようにできると共に、旋回作用時には、該左右
の無段変速装置71の各々独立した変速により旋回半径
を適宜に調節することができる。The reference numeral 79 designates the left and right continuously variable transmissions 71.
Left and right input pulleys for inputting power respectively, 80 is a mowing drive pulley axially fixed to the reduction shaft 75, and 81 is a left and right traveling sprocket axially fixed to the left and right axles 77, respectively. With this structure, the power transmitted from the left and right continuously variable transmissions 71 is transmitted to the left and right traveling sprockets 81 from the left and right idle gears 74, the left and right reduction gears 76, and the left and right axle gears 78. . By this power transmission, the rotational speeds of the left and right transmission systems can be matched by the action of the straight traveling clutch 74a during straight traveling so as not to impair the straight traveling performance, and at the time of turning action, each of the left and right continuously variable transmissions 71 is separated. The turning radius can be adjusted appropriately by independent gear shifting.
【0048】なお、刈取駆動プーリ80は、一方向回転
クラッチ76aを介して減速軸75の高速側(旋回外
側)により駆動するため、刈取作業における操向時に刈
取速度の低下を抑制し、刈取作業を円滑に行わせること
ができる。また、上記と異なる別の走行用ミッションケ
ース82のギヤ連動機構として、図6に示す如く、油圧
式無段変速装置83の出力側に連動連結した入力軸84
に軸止した入力ギヤ84aと、変速駆動軸85に摺動可
能に軸回転させる三連の変速伝動ギヤ85aの大径ギヤ
とを噛合連動して構成させる。Since the mowing drive pulley 80 is driven by the high speed side (outer side of the turning) of the reduction shaft 75 via the one-way rotating clutch 76a, the mowing speed is suppressed from decreasing during the steering operation, and the mowing operation is suppressed. Can be done smoothly. Further, as another gear interlocking mechanism for the traveling mission case 82 different from the above, as shown in FIG. 6, an input shaft 84 interlockingly coupled to the output side of the hydraulic continuously variable transmission 83 is provided.
The input gear 84a, which is axially stopped, and the large-diameter gears of the three speed change transmission gears 85a, which are slidably rotated on the speed change drive shaft 85, are engaged with each other.
【0049】該変速伝動ギヤ85aと、変速伝動軸86
に軸止する高速駆動ギヤ86a,中速駆動ギヤ86b,
低速駆動ギヤ86cとを各々噛合連動させることによっ
て高速,中速,低速に変速する副変速部を形成させると
共に、更に、この変速伝動軸86に軸止した変速伝動ギ
ヤ86dと、差動クラッチ軸87に軸止した差動センタ
ギヤ87aとを噛合連動して構成させる。The speed change transmission gear 85a and the speed change transmission shaft 86
A high speed drive gear 86a, a medium speed drive gear 86b,
The low-speed drive gear 86c is meshed with each other to form a sub-transmission portion that shifts to a high speed, a medium speed, and a low speed, and further, the transmission transmission gear 86d fixed to the transmission transmission shaft 86 and a differential clutch shaft. A differential center gear 87a, which is axially fixed to 87, is meshed with and configured.
【0050】該差動センタギヤ87aの両側に各々左右
対称で配置させる遊星ギヤ機構88は、該差動クラッチ
軸87に軸止した左右のサンギヤ88aを中心に、差動
クラッチ軸87に軸遊転する左右のキャリア88bに支
承した各複数個の遊星ギヤ88cと、内周リングギヤ8
8dとによって差動変速して構成させる。The planetary gear mechanism 88, which is symmetrically arranged on both sides of the differential center gear 87a, has a left and right sun gears 88a that are axially fixed to the differential clutch shaft 87, and is rotated around the differential clutch shaft 87. Each of the plurality of planet gears 88c supported on the left and right carriers 88b, and the inner peripheral ring gear 8
8d and a differential gear shift.
【0051】該左右のキャリア88bの各外周リングギ
ヤ88eと、変速駆動軸85から入力する副変速非同調
式、又は変速伝動軸86から入力する副変速同調式の無
段変速器89(リングコーンや摩擦クラッチ等によるも
の)の出力側の変速制御ギヤ89a(一方は反転ギヤを
介して)とを、逆方向へ噛合連動して変速可能に構成さ
せる。The outer peripheral ring gears 88e of the left and right carriers 88b and the auxiliary transmission non-synchronized type input from the speed change drive shaft 85 or the auxiliary transmission synchronized type input from the speed change transmission shaft 86 (a ring cone or An output-side shift control gear 89a (of which a friction clutch or the like is provided) (one of which is through a reversing gear) is configured to be meshed in the opposite direction and gear-shiftable.
【0052】該左右のキャリア88b外周に設けた各差
動変速ギヤ88fと、左右の車軸90の一端部に軸止し
た車軸ギヤ90aとを噛合連動し、その他端部に走行ス
プロケット90bを軸止して構成させる。このような構
成により、旋回作用を行わせるときは、該無段変速器8
9の変速操作により、遊星ギヤ機構88の左右の外周リ
ングギヤ88eを逆方向へ変速駆動して左右のキャリア
88bに回転速度差を生ぜしめ、旋回半径を適宜に調節
することができるものであり、この変速機構は、走行伝
動系の動力を無段変速器89により変速して遊星ギヤ機
構88へ伝達するものであるから、旋回用の油圧式無段
変速装置等を別途設ける必要がなく、安価に提供するこ
とができる。The differential transmission gears 88f provided on the outer circumferences of the left and right carriers 88b are meshed with the axle gears 90a fixed to one end of the left and right axles 90, and the traveling sprocket 90b is fixed to the other end. And configure it. With such a configuration, when the turning action is performed, the continuously variable transmission 8
By the gear shifting operation of 9, the left and right outer peripheral ring gears 88e of the planetary gear mechanism 88 are gear-shifted in the opposite direction to generate a rotational speed difference between the left and right carriers 88b, and the turning radius can be adjusted appropriately. Since this transmission mechanism changes the power of the traveling transmission system by the continuously variable transmission 89 and transmits it to the planetary gear mechanism 88, there is no need to separately provide a hydraulic continuously variable transmission for turning, etc. Can be provided to.
【図1】旋回用クラッチの接続圧ラインの圧力カーブを
2系統とした状態を示す線図。FIG. 1 is a diagram showing a state in which a pressure curve of a connecting pressure line of a turning clutch has two systems.
【図2】操向操作における旋回時に各種の自動制御を行
う電気回路を示すブロック図。FIG. 2 is a block diagram showing an electric circuit that performs various automatic controls during turning in a steering operation.
【図3】走行用ミッションケースのギヤ連動機構におけ
る伝動状態を示す正面展開図。FIG. 3 is a front development view showing a transmission state in a gear interlocking mechanism of a traveling mission case.
【図4】ミッションケースの伝動構成による部分的なギ
ヤ配列状態を示す正面展開図。FIG. 4 is a front development view showing a partial gear arrangement according to the transmission configuration of the mission case.
【図5】別のミッションケースのギヤ連動機構における
伝動状態を示す正面展開線図。FIG. 5 is a front development line diagram showing a transmission state in a gear interlocking mechanism of another mission case.
【図6】別のミッションケースのギヤ連動機構における
伝動状態を示す正面展開線図。FIG. 6 is a front development line diagram showing a transmission state in a gear interlocking mechanism of another mission case.
【図7】コンバインにおける全体構成を示す側面図。FIG. 7 is a side view showing the overall configuration of the combine.
1. 副変速部 2. 旋回用クラッチ 3. 差動ギヤ装置 4. 走行用ミッションケース 5. 操向操作具 6. 旋回制御手段 7. 交互制御手段 1. Sub-transmission unit 2. Swing clutch 3. Differential gear device 4. Traveling mission case 5. Steering operation tool 6. Turning control means 7. Alternate control means
───────────────────────────────────────────────────── フロントページの続き (72)発明者 廣田 幹司 愛媛県伊予郡砥部町八倉1番地 井関農機 株式会社技術部内 Fターム(参考) 2B043 AA03 AB08 AB11 AB19 BA05 BB14 DA05 DB07 DB20 DC01 EA02 EA04 EA13 EB02 EB07 EB10 EB14 EB22 EC15 ED03 ED04 ED05 ED23 2B076 AA03 BA05 BA07 CC02 DA03 DB06 DB08 DB09 DC01 DD02 EA03 EA06 EB05 EC23 ED27 3D052 AA02 AA05 AA12 BB09 BB11 BB19 DD04 EE01 FF01 GG04 GG05 HH01 HH02 HH03 JJ08 JJ12 JJ21 JJ22 JJ31 JJ37 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Miki Hirota No. 1 Yakura, Tobe-cho, Iyo-gun, Ehime Prefecture Technology Department Co., Ltd. F-term (reference) 2B043 AA03 AB08 AB11 AB19 BA05 BB14 DA05 DB07 DB20 DC01 EA02 EA04 EA13 EB02 EB07 EB10 EB14 EB22 EC15 ED03 ED04 ED05 ED23 2B076 AA03 BA05 BA07 CC02 DA03 DB06 DB08 DB09 DC01 DD02 EA03 EA06 EB05 EC23 ED27 3D052 AA02 AA05 AA12 BB09 BB11 BB19 DD04 EE01 FF01 GG04 GG05 HH01 HH02 HH03 JJ08 JJ12 JJ21 JJ22 JJ31 JJ37
Claims (2)
動ギヤ装置3等によりマイルド旋回・ブレーキ旋回・ス
ピン旋回の各旋回モードを無段で連続して実行可能なギ
ヤ連動機構を有する走行用ミッションケース4におい
て、傾動操作により各旋回モードを連続して実行させる
操向操作具5の操作角度に対応させた旋回半径を、該副
変速部1の変速切替えに応じて大〜小に変更可能とする
旋回制御手段6を設けたことを特徴とするコンバイン等
の走行伝動装置。1. A gear interlocking mechanism capable of continuously executing, in a stepless manner, each swing mode of a mild swing, a brake swing, and a spin swing by means of a swing clutch 2 and a differential gear device 3 via a sub transmission unit 1. In the traveling mission case 4, the turning radius corresponding to the operation angle of the steering operation tool 5 for continuously executing the respective turning modes by the tilting operation is increased or decreased in accordance with the shift change of the sub transmission unit 1. A traveling transmission device such as a combine, which is provided with a turning control means 6 that can be changed.
動ギヤ装置3等によりマイルド旋回・ブレーキ旋回・ス
ピン旋回の各旋回モードを無段で連続して実行可能なギ
ヤ連動機構を有する走行用ミッションケース4におい
て、傾動操作により各旋回モードを連続して実行させる
操向操作具5の操作角度に対応させた旋回半径を、大〜
小交互に脈動状態に切替え可能とする交互制御手段7を
設けたことを特徴とする請求項1記載のコンバイン等の
走行伝動装置。2. A gear interlocking mechanism capable of continuously executing each of the turning modes of mild turning, brake turning, and spin turning by means of the turning clutch 2 and the differential gear device 3 via the auxiliary transmission unit 1 in a continuously variable manner. In the traveling mission case 4, the turning radius corresponding to the operation angle of the steering operation tool 5 for continuously executing the respective turning modes by the tilting operation is set to a large value.
The traveling transmission device for a combine or the like according to claim 1, further comprising: an alternate control means (7) capable of alternately switching to a pulsating state.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002072251A JP2003267255A (en) | 2002-03-15 | 2002-03-15 | Traveling and transmission device of combine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002072251A JP2003267255A (en) | 2002-03-15 | 2002-03-15 | Traveling and transmission device of combine |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2003267255A true JP2003267255A (en) | 2003-09-25 |
Family
ID=29202297
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2002072251A Pending JP2003267255A (en) | 2002-03-15 | 2002-03-15 | Traveling and transmission device of combine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2003267255A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005137316A (en) * | 2003-11-10 | 2005-06-02 | Iseki & Co Ltd | Working vehicle |
JP2005145154A (en) * | 2003-11-12 | 2005-06-09 | Iseki & Co Ltd | Transmission mechanism of traveling device |
JP2005225270A (en) * | 2004-02-10 | 2005-08-25 | Iseki & Co Ltd | Steering device of agricultural work vehicle |
JP2005319965A (en) * | 2004-05-11 | 2005-11-17 | Iseki & Co Ltd | Travel transmission |
-
2002
- 2002-03-15 JP JP2002072251A patent/JP2003267255A/en active Pending
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005137316A (en) * | 2003-11-10 | 2005-06-02 | Iseki & Co Ltd | Working vehicle |
JP2005145154A (en) * | 2003-11-12 | 2005-06-09 | Iseki & Co Ltd | Transmission mechanism of traveling device |
JP4609624B2 (en) * | 2003-11-12 | 2011-01-12 | 井関農機株式会社 | Combine |
JP2005225270A (en) * | 2004-02-10 | 2005-08-25 | Iseki & Co Ltd | Steering device of agricultural work vehicle |
JP4513350B2 (en) * | 2004-02-10 | 2010-07-28 | 井関農機株式会社 | Combine |
JP2005319965A (en) * | 2004-05-11 | 2005-11-17 | Iseki & Co Ltd | Travel transmission |
JP4604547B2 (en) * | 2004-05-11 | 2011-01-05 | 井関農機株式会社 | Travel gear |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP2003267255A (en) | Traveling and transmission device of combine | |
JP3618255B2 (en) | Driving transmission structure of work vehicle | |
JP2001328557A (en) | Traveling device for working vehicle and the like | |
JP2000198461A (en) | Transmission | |
JPH10274317A (en) | Hst type transmission device | |
JP3695364B2 (en) | Traveling device | |
JPH09315337A (en) | Steering device of work vehicle | |
JP3944925B2 (en) | Vehicle power transmission device | |
JP2007076476A (en) | Combine | |
JP4449957B2 (en) | Combine | |
JP2004224297A (en) | Travel transmission structure of working vehicle | |
JP5149500B2 (en) | Work vehicle transmission | |
JP4413169B2 (en) | Agricultural vehicle power transmission | |
JP3658910B2 (en) | Combine driving mission | |
JP4009694B2 (en) | Combine drive transmission | |
JP2003341545A (en) | Traveling transmission device for combine harvester and the like | |
JP4475006B2 (en) | Combine | |
JP4548579B2 (en) | Combine | |
JP2003274707A (en) | Directional control device of combine harvester, etc. | |
JP3265698B2 (en) | Steering device such as combine | |
JPH09142334A (en) | Running device for combine | |
JP3963833B2 (en) | Driving transmission structure of work vehicle | |
JP2001241516A (en) | Driving gear for working vehicle | |
JP2003291848A (en) | Working vehicle | |
JP2003034263A (en) | Traveling power transmission device |