JP2003267255A - Traveling and transmission device of combine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To controllably change a turning radius allowed to act by a traveling transmission case in a turning action during the traveling of a combine. <P>SOLUTION: This traveling transmission case 4 comprises a gear interlocking mechanism capable of steplessly and continuously performing the turning modes of a mild turning, a brake turning, and a spin turning by a turning clutch 2 and a differential gear device 3 through an auxiliary transmission part 1. The case 4 also comprises a turn control means 6 capable of changing the turning radius corresponding to the operating angle of a steering operation device 5 for continuously performing the turning mode by a tilting operation according to the switching of the gears of the auxiliary transmission part 1 and an alternate control means 7 capable of switching the turning radius corresponding to the operating angle of the steering operation device 5 to pulsation state alternately between a large state and a small state. <P>COPYRIGHT: (C)2003,JPO

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】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.

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

【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.

【符号の説明】[Explanation of symbols]

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)

【特許請求の範囲】[Claims] 【請求項１】 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。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. 【請求項２】 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。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.