JP3266830B2 - Work equipment steering system - Google Patents
Work equipment steering systemInfo
- Publication number
- JP3266830B2 JP3266830B2 JP19108197A JP19108197A JP3266830B2 JP 3266830 B2 JP3266830 B2 JP 3266830B2 JP 19108197 A JP19108197 A JP 19108197A JP 19108197 A JP19108197 A JP 19108197A JP 3266830 B2 JP3266830 B2 JP 3266830B2
- Authority
- JP
- Japan
- Prior art keywords
- turning
- transmission
- traveling
- speed
- continuously variable
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Arrangement Or Mounting Of Control Devices For Change-Speed Gearing (AREA)
- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
- Control Of Transmission Device (AREA)
Description
【0001】[0001]
【発明の属する技術分野】本発明は、左右の走行装置へ
の伝動系に走行変速用の無段変速装置と第2変速装置と
を直列に接続する状態で介装してあるコンバインなど作
業機の操向装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a working machine such as a combine machine in which a continuously variable transmission for traveling and a second transmission are connected in series to a transmission system for left and right traveling devices in series. To a steering device.
【0002】[0002]
【従来の技術】この種の作業機の操向装置として、本発
明者は、旋回操作具が直進位置にあるとき前記第1無段
変速装置と同調して作動するとともに旋回操作具の旋回
操作量の増大に伴って減速作動する旋回用の無段変速装
置を設け、前記旋回操作具の旋回操作に基づいて左右の
走行装置のうち旋回内側のものの走行変速用の無段変速
装置への連動を断つとともに旋回内側の走行装置を前記
旋回用の無段変速装置に連動させる旋回連動手段を設け
たものを先に考えた。この作業機の操向装置によるとき
は、旋回内側の走行装置を旋回用の無段変速装置により
無段階に減速作動させることができるので、旋回半径を
自由に選択でき、しかも、直進走行時には、走行変速用
の無段変速装置及び第2変速装置を介して左右の走行装
置をともに駆動するので、例えば、左右の走行装置のそ
れぞれに対して無段変速装置を設けて左右の走行装置を
各別に駆動する場合に比較して、直進性能を優れたもの
にできるといった利点を有する。ところが、この種の作
業機の操向装置は未だ開発途上にあって、実施化にあた
っては、次のような問題を解決する必要がある。2. Description of the Related Art As a steering device for a working machine of this type, the inventor of the present invention operates in synchronism with the first continuously variable transmission when the turning operation tool is in a straight-ahead position and operates the turning operation of the turning operation tool. A continuously variable transmission for turning that decelerates with an increase in the amount is provided, and interlocked with the continuously variable transmission for traveling during traveling of the left and right traveling devices based on the turning operation of the turning operation tool. And a turning interlock means for interlocking the traveling device inside the turning with the continuously variable transmission for turning is considered first. When using the steering device of this work machine, the traveling device inside the turning can be steplessly decelerated by the continuously variable transmission for turning, so that the turning radius can be freely selected, and when traveling straight ahead, Since both the left and right traveling devices are driven via the continuously variable transmission for traveling speed change and the second transmission, for example, a continuously variable transmission is provided for each of the left and right traveling devices, and the left and right traveling devices are each There is an advantage that the straight running performance can be improved as compared with the case of driving separately. However, this type of working machine steering device is still under development, and it is necessary to solve the following problems when implementing it.
【0003】[0003]
【発明が解決しようとする課題】すなわち、第2変速装
置が高速伝動状態にあるときに走行変速用の無段変速装
置又は第2変速装置による第1走行装置駆動部と旋回用
の無段変速装置による第2走行装置駆動部とが等速回転
するように走行変速用の無段変速装置と旋回用の無段変
速装置との同調関係を設定して、高速走行状態での旋回
開始時における旋回内側の走行装置の走行速度を旋回外
側の走行装置の走行速度と等しくさせて直進走行から旋
回への移行を円滑に行わせるのである。しかし、そうす
ると、第2変速装置が低速伝動状態にあるときの第2走
行装置駆動部の回転速度が、第1走行装置駆動部の回転
速度よりも大となるから、第2変速装置を低速伝動状態
にさせての低速走行において旋回する際、旋回初期にお
ける旋回内側の走行装置の走行速度が旋回外側の走行装
置の走行速度よりも大きく、意に反して反対方向に旋回
してしまう。That is, when the second transmission is in a high-speed transmission state, the continuously variable transmission for traveling transmission or the first traveling device drive unit by the second transmission and the continuously variable transmission for turning. The synchronous relationship between the continuously variable transmission for traveling and the continuously variable transmission for turning is set so that the second traveling device drive unit of the device rotates at a constant speed. The traveling speed of the traveling device inside the turning is made equal to the traveling speed of the traveling device outside the turning so that the transition from straight running to turning can be smoothly performed. However, in this case, the rotation speed of the second traveling device drive unit when the second transmission device is in the low speed transmission state becomes higher than the rotation speed of the first travel device drive unit, and thus the second transmission device is driven at a low speed. When the vehicle turns at low speed with the state, the traveling speed of the traveling device inside the turning in the initial stage of the revolution is higher than the traveling speed of the traveling device outside the turning, and conversely turns in the opposite direction.
【0004】本発明の目的は、旋回操作性を改善する点
にある。[0004] An object of the present invention is to improve turning operability.
【0005】[0005]
【課題を解決するための手段】請求項1に係る本第1発
明の特徴、作用、効果は次の通りである。The features, functions and effects of the first aspect of the present invention are as follows.
【0006】〔特徴〕左右の走行装置への伝動系に走行
変速用の無段変速装置と第2変速装置とを直列に接続す
る状態で介装してある作業機において、旋回操作具が直
進位置にあるとき前記走行変速用の第1無段変速装置と
同調して作動するとともに旋回操作具の旋回操作量の増
大に伴って減速作動する旋回用の無段変速装置を設け、
前記旋回操作具の旋回操作に基づいて左右の走行装置の
うち旋回内側のものの走行変速用の無段変速装置への連
動を断つとともに旋回内側の走行装置を前記旋回用の無
段変速装置に連動させる旋回連動手段を設け、前記第2
変速装置の変速状態に基づいて第2変速装置が低速伝動
状態にあるほど旋回操作具の操作に基づく旋回用の無段
変速装置の作動量を小にすることにより走行変速用の無
段変速装置又は第2変速装置による第1走行装置駆動部
と旋回用の無段変速装置による第2走行装置駆動部とが
等速回転するように旋回操作具と旋回用の無段変速装置
との連動関係を補正する補正手段を設けてある点にあ
る。[Characteristics] In a working machine in which a continuously variable transmission for traveling and a second transmission are connected in series to a transmission system for left and right traveling devices in a state of being connected in series, a turning operation tool moves straight. A continuously variable transmission for turning that operates in synchronization with the first continuously variable transmission for traveling when in the position and decelerates with an increase in the amount of turning operation of the turning operation tool;
Based on the turning operation of the turning operation tool, interlocking of the left and right traveling devices with the continuously variable transmission for traveling speed change is performed on the inside of the turning and interlocking the traveling device inside the turning with the continuously variable transmission for turning. Turning interlock means for causing the second
The continuously variable transmission for traveling speed change by reducing the operation amount of the continuously variable transmission for turning based on the operation of the turning operation tool as the second transmission is in the low-speed transmission state based on the shift state of the transmission. Or, the interlocking relationship between the turning operation tool and the continuously variable transmission for turning such that the first traveling device drive unit of the second transmission and the second traveling device drive unit of the continuously variable transmission for rotation rotate at a constant speed. Is provided with a correcting means for correcting.
【0007】〔作用〕本第1発明によるときは、旋回操
作具が直進位置にあるとき前記走行変速用の無段変速装
置と同調して作動するとともに旋回操作具の旋回操作量
の増大に伴って減速作動する旋回用の無段変速装置を設
け、前記旋回操作具の旋回操作に基づいて左右の走行装
置のうち旋回内側のものの走行変速用の無段変速装置へ
の連動を断つとともに旋回内側の走行装置を前記旋回用
の無段変速装置に連動させる旋回連動手段を設けてあっ
て、旋回内側の走行装置を旋回用の無段変速装置により
無段階に減速作動させることができるので、旋回半径を
自由に選択でき、しかも、直進走行時には、走行変速用
の無段変速装置及び第2変速装置を介して左右の走行装
置をともに駆動するので、例えば、左右の走行装置のそ
れぞれに対して無段変速装置を設けて左右の走行装置を
各別に駆動する場合に比較して、直進性能を優れたもの
にできる。According to the first aspect of the present invention, when the turning operation tool is in the straight-ahead position, it operates in synchronism with the continuously variable transmission for traveling speed change, and with an increase in the amount of turning operation of the turning operation tool. A stepless speed change device for turning that performs deceleration operation is provided. Based on the turning operation of the turning operation tool, the interlocking of the left and right traveling devices to the continuously variable speed change device for traveling speed change is performed while the inside of the turning device is turned off. Is provided with a turning interlocking means for interlocking the traveling device with the continuously variable transmission for turning, and the traveling device inside the turning can be steplessly decelerated by the continuously variable transmission for turning. The radius can be freely selected, and when traveling straight ahead, both the left and right traveling devices are driven via the continuously variable transmission and the second transmission for traveling speed change. Nothing The left and right traveling devices are provided with a transmission as compared to the case of driving the respective other, it can be provided with excellent straightness performance.
【0008】その上、前記第2変速装置の変速状態に基
づいて第2変速装置が低速伝動状態にあるほど旋回操作
具の操作に基づく旋回用の無段変速装置の作動量を小に
するように旋回操作具と旋回用の無段変速装置との連動
関係を補正する補正手段を設けることにより走行変速用
の無段変速装置又は第2変速装置による第1走行装置駆
動部と旋回用の無段変速装置による第2走行装置駆動部
とが等速回転するようにしてあるから、低速走行状態で
の旋回時に意に反して反対方向に旋回することを確実に
防止できることはもちろん、第2変速装置の変速状態に
かかわらず、つまり、高速走行、低速走行にかかわら
ず、旋回開始時における旋回内側の走行装置の走行速度
を旋回外側の走行装置の走行速度と等しくさせて直進走
行から旋回への移行を円滑に行わせることができる。In addition, based on the shift state of the second transmission, the operation amount of the continuously variable transmission for turning based on the operation of the turning operation tool is reduced as the second transmission is in the low-speed transmission state. A correction means for correcting the interlocking relationship between the turning operation tool and the continuously variable transmission for turning is provided to the drive unit for driving the first traveling device by the continuously variable transmission for traveling speed change or the second transmission and to the driving device for turning. Since the drive unit of the second traveling device by the stepped transmission is rotated at a constant speed, it is possible to surely prevent the vehicle from turning in the opposite direction when turning in the low-speed running state. Regardless of the shift state of the device, that is, regardless of whether the vehicle is traveling at high speed or low speed, the traveling speed of the traveling device on the inside of the turn at the start of turning is made equal to the traveling speed of the traveling device on the outside of the revolution to change from straight traveling to turning. Migration It can be carried out smoothly.
【0009】〔効果〕従って、本第1発明によれば、高
速走行、低速走行のいずれの場合であっても、旋回内側
の走行装置を旋回用の無段変速装置で減速駆動させての
旋回を円滑に行えるようになった。[Effects] Therefore, according to the first aspect of the present invention, in either case of high-speed running or low-speed running, the turning device in which the traveling device inside the turning is decelerated by the continuously variable transmission for turning is turned. Can be performed smoothly.
【0010】[0010]
【発明の実施の形態】コンバインは、図1に示すよう
に、左右一対のクローラ式の走行装置1を備えた自走機
体に脱穀装置2と操縦部3を搭載し、自走機体の前部に
刈取部4を昇降操作自在に連結して構成されている。前
記刈取部4は、植立穀稈を引き起こす引起し装置5、引
き起こされた植立穀稈の株元を切断するバリカン型の切
断装置6、刈取穀稈を前記脱穀装置2のフィードチェー
ン2Aに搬送供給する供給装置7を備えている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG. 1, a combine includes a self-propelled body equipped with a pair of left and right crawler-type traveling units 1, a threshing device 2 and a control unit 3, and a front part of the self-propelled body. The mowing part 4 is connected so as to be able to move up and down freely. The cutting unit 4 includes a raising device 5 for raising the planted grain culm, a clipper-type cutting device 6 for cutting the root of the raised planted grain culm, and a cut chain culm to the feed chain 2A of the threshing device 2. The apparatus is provided with a supply device 7 for conveying and supplying.
【0011】前記自走機体に搭載したエンジン8から左
右の走行装置1への伝動系は、図2に示すように、可変
容量型の油圧ポンプ9Pとそれにより発生される圧油で
駆動される油圧モータ9Mとからなる前後進切り換え自
在な走行変速用の静油圧式の無段変速装置9と、同様に
可変容量型の油圧ポンプ10Pとそれにより発生される
圧油で駆動される油圧モータ10Mとからなる前後進切
り換え自在な旋回用の静油圧式の無段変速装置10と
を、両油圧ポンプ9P,10Pがエンジン8によりベル
ト伝動装置11を介して駆動される状態に設け、前記走
行装置1の車軸1Aを軸支するミッションケース12内
に、走行変速用の油圧モータ9Mに連動する高低2段切
り換え自在なギヤ式の副変速装置13と、この副変速装
置13に常時連動するセンターギヤ14と、前記旋回用
の油圧モータ10Mに中継ギヤ15L,15Rそれぞれ
を介して常時連動する左右一対のサイドギヤ16L,1
6Rと、前記左右の車軸1Aのそれぞれに常時ギヤ連動
する左右一対のシフト部材17L,17Rとを設け、シ
フト部材17L,17Rをセンターギヤ14側のセンタ
ー位置にシフトさせることでシフト部材17L,17R
をセンターギヤ14に連動させる左右一対の爪クラッチ
18L,18Rと、シフト部材17L,17Rを対応す
るサイドギヤ16L,16R側のサイド位置にシフトさ
せることでシフト部材17L,17Rを対応するサイド
ギヤ16L,16Rに連動させる左右一対の摩擦クラッ
チ19L,19Rを設けて構成されている。そして、前
記副変速装置13が、本発明でいうところの左右の走行
装置1への伝動系に走行変速用の無段変速装置9と直列
に介装した第2変速装置であり、センターギヤ14が、
本発明でいうところの第2変速装置(副変速装置13)
による第1走行装置駆動部であり、サイドギヤ16L,
16Rが、本発明でいうところの旋回用の無段変速装置
10による第2走行装置駆動部である。As shown in FIG. 2, the transmission system from the engine 8 mounted on the self-propelled body to the left and right traveling devices 1 is driven by a variable displacement hydraulic pump 9P and pressure oil generated by the hydraulic pump 9P. A hydrostatic continuously variable transmission 9 for traveling speed changeable between forward and backward, comprising a hydraulic motor 9M, a variable displacement hydraulic pump 10P, and a hydraulic motor 10M driven by pressure oil generated thereby. A hydrostatic continuously variable transmission 10 for turning, which is switchable between forward and backward, provided in a state where both hydraulic pumps 9P, 10P are driven by an engine 8 via a belt transmission 11; In a transmission case 12 that supports one axle 1A, a gear-type auxiliary transmission 13 that can be switched between high and low in two stages that is interlocked with a hydraulic motor 9M for traveling speed change, and is always interlocked with the auxiliary transmission 13. A center gear 14, the hydraulic motor 10M to the relay gear 15L for the swing, a pair of right and left interlocking constantly via respective 15R side gears 16L, 1
6R and a pair of left and right shift members 17L and 17R that are always gear-coupled to each of the left and right axles 1A. The shift members 17L and 17R are shifted to the center position on the side of the center gear 14 by shifting the shift members 17L and 17R.
The shift members 17L, 17R are shifted to the corresponding side gears 16L, 16R side by shifting the shift members 17L, 17R to the corresponding side gears 16L, 16R by shifting the shift members 17L, 17R to the corresponding side gears 16L, 16R. And a pair of left and right friction clutches 19L and 19R that are interlocked with each other. The auxiliary transmission 13 is a second transmission that is interposed in series with the continuously variable transmission 9 for traveling speed change in the transmission system to the left and right traveling devices 1 according to the present invention, and includes a center gear 14. But,
Second transmission (sub-transmission 13) in the present invention
Is a first traveling device drive unit by the side gear 16L,
Reference numeral 16 </ b> R denotes a second traveling device drive unit using the continuously variable transmission 10 for turning according to the present invention.
【0012】前記副変速装置13は、走行変速用の油圧
モータ9Mの出力軸9Aにギヤ20,21対を介して連
動するカウンター軸22に小径の低速伝動ギヤ23Lと
大径の高速伝動ギヤ23Hとを回転のみ自在に装着し、
前記中継ギヤ15L,15Rの軸24に回転のみ自在に
装着したスリーブ25に、前記低速伝動ギヤ23Lに常
時連動する大径の低速受動ギヤ26Lと高速伝動ギヤ2
3Hに常時連動する小径の高速受動ギヤ26Hとを一体
回転する状態に装着し、前記カウンター軸22に、低速
伝動ギヤ23Lにのみ連動する低速位置と高速伝動ギヤ
23Hにのみ連動する高速位置とにシフト操作自在なシ
フト部材27をスプライン嵌合させて構成されている。
つまり、シフト部材27を低速伝動ギヤ23Lに連動さ
せることによりカウンター軸22からスリーブ25に低
速伝動し、シフト部材27を高速伝動ギヤ23Hに連動
させることによりカウンター軸22からスリーブ25に
高速伝動するようになっている。The sub-transmission 13 is provided with a small-diameter low-speed transmission gear 23L and a large-diameter high-speed transmission gear 23H on a counter shaft 22 interlocked with an output shaft 9A of a traveling speed hydraulic motor 9M via a pair of gears 20 and 21. And freely rotate only,
A large-diameter low-speed passive gear 26L and a high-speed transmission gear 2, which are always linked to the low-speed transmission gear 23L, are mounted on a sleeve 25 rotatably mounted only on the shaft 24 of the relay gears 15L and 15R.
A small-diameter high-speed passive gear 26H constantly linked to 3H is mounted so as to rotate integrally, and the counter shaft 22 is set to a low-speed position linked only to the low-speed transmission gear 23L and a high-speed position linked only to the high-speed transmission gear 23H. The shift member 27 which can be shifted is spline-fitted.
That is, the low speed transmission from the counter shaft 22 to the sleeve 25 is performed by linking the shift member 27 to the low speed transmission gear 23L, and the high speed transmission is performed from the counter shaft 22 to the sleeve 25 by linking the shift member 27 to the high speed transmission gear 23H. It has become.
【0013】そして、前記センターギヤ14を低速受動
ギヤ26Lに噛み合わせることにより副変速装置13に
センターギヤ14を連動させている。The center gear 14 is linked to the auxiliary transmission 13 by meshing the center gear 14 with the low-speed passive gear 26L.
【0014】前記摩擦クラッチ19L,19Rは、スプ
リング28L,28Rにより切り付勢されており、シフ
ト部材17L,17Rがセンター位置に位置するときに
は、爪クラッチ18L,18Rのみが入り作動し、シフ
ト部材17L,17Rがサイド位置に位置しているとき
には、摩擦クラッチ19L,19Rのみが入り作動する
ようになっている。The friction clutches 19L and 19R are urged by springs 28L and 28R. When the shift members 17L and 17R are located at the center positions, only the pawl clutches 18L and 18R are engaged and the shift members 17L and 17R are operated. , 17R are located at the side positions, only the friction clutches 19L, 19R are engaged.
【0015】なお、前記スリーブ25には、駐車ブレー
キ29の軸29Aに装着のギヤ30に連動する駐車用ギ
ヤ31が一体回転する状態に装着されている。The sleeve 25 is provided with a parking gear 31 interlocking with a gear 30 mounted on a shaft 29A of a parking brake 29 so as to rotate integrally therewith.
【0016】前記シフト部材17L,17Rは、図16
に示すように、油圧アクチュエータ32の左右のピスト
ン32L,32Rにより各別に駆動されるシフター33
L,33Rでシフト操作されるものである。The shift members 17L and 17R are arranged as shown in FIG.
As shown in the figure, shifters 33 driven separately by left and right pistons 32L, 32R of the hydraulic actuator 32, respectively.
The shift operation is performed with L and 33R.
【0017】前記両無段変速装置9,10及び副変速装
置13に対する操作装置は、図3に示すように、主変速
レバー34と旋回操作具であるところの左右揺動自在な
旋回レバー35と副変速レバー36とを設け、これら主
変速レバー34と旋回レバー35の操作に基づいて両無
段変速装置9,10を操作するとともに、副変速レバー
36の操作に基づいて副変速装置13及び旋回用の無段
変速装置10を操作する連係操作手段を設けて構成され
ている。As shown in FIG. 3, an operating device for the two continuously variable transmissions 9, 10 and the auxiliary transmission 13 includes a main transmission lever 34 and a swing lever 35 which is a swing operation tool and can swing left and right. A sub-transmission lever 36 is provided to operate both the continuously variable transmissions 9 and 10 based on the operation of the main transmission lever 34 and the turning lever 35, and to operate the sub-transmission 13 and the turning transmission based on the operation of the sub-transmission lever 36. And a linkage operating means for operating the continuously variable transmission 10 for use in the vehicle.
【0018】前記連係操作手段は、主変速レバー34の
操作に連動して走行変速用の油圧ポンプ9Pにおける容
量変更用のトラニオン軸(以下、変速用トラニオン軸と
称する。)9aを作動させる主変速用プッシュプルワイ
ヤ37を設け、前記旋回レバー35に旋回用レリーズワ
イヤ38を介して連動するとともに同調ロッド39を介
して前記変速用トラニオン軸9aに連動しかつ旋回用プ
ッシュプルワイヤ41を介して旋回用の油圧ポンプ10
Pにおける容量変更用のトラニオン軸(以下旋回用トラ
ニオン軸と称する。)10aに連動していて、前記旋回
レバー35が「直進」の位置にある状態において両無段
変速装置9,10を同調させる同調手段40を設け、こ
の同調手段40から旋回用プッシュプルワイヤ41を介
して旋回用トラニオン軸10aに伝達される操作量を補
正ワイヤ42を介して伝達される副変速装置13の変速
状態で補正して、副変速装置13が低速伝動状態にある
とき及び高速伝動状態にあるときのいずれにおいても旋
回レバー35が「直進」の位置にあるとセンターギヤ1
4とサイドギヤ16L,16Rとを等速にするように同
調状態を補正する補正手段43を設けて構成されてい
る。The linkage operation means operates a main transmission for actuating a trunnion shaft (hereinafter referred to as a transmission trunnion shaft) 9a for changing the capacity of the traveling speed hydraulic pump 9P in conjunction with the operation of the main transmission lever 34. A push-pull wire 37 is provided, which is interlocked with the swivel lever 35 via a release wire 38 for swivel, and is also interlocked with a trunnion shaft 9a for shifting via a tuning rod 39 and swivel via a push-pull wire 41 for swivel. Hydraulic pump 10
The continuously variable transmissions 9 and 10 are synchronized with each other in a state in which the turning lever 35 is in a “straight-ahead” position in conjunction with a trunnion shaft (hereinafter, referred to as a turning trunnion shaft) 10 a for changing the capacity at P. A tuning means 40 is provided, and the operation amount transmitted from the tuning means 40 to the turning trunnion shaft 10a via the turning push-pull wire 41 is corrected by the shift state of the auxiliary transmission 13 transmitted via the correcting wire 42. When the turning lever 35 is in the "straight forward" position both when the auxiliary transmission 13 is in the low-speed transmission state and in the high-speed transmission state, the center gear 1
4 and the side gears 16L and 16R are provided with a correction means 43 for correcting the tuning state so as to have the same speed.
【0019】前記同調手段40は、旋回レバー35が
「直進」の位置にありかつ副変速装置13が高速伝動状
態にあるときにセンターギヤ14とサイドギヤ16L,
16Rとが同方向に同回転数で回転するように両無段変
速装置9,10の同調関係を設定し、かつ、副変速装置
13が高速伝動状態にあるときの旋回レバー35の最大
操作位置への旋回操作の伴うサイドギヤ16L,16R
のセンターギヤ14とは逆方向への回転数がセンターギ
ヤ14の回転数となるように両無段変速装置9,10を
関連付ける手段である。具体的には、図4〜図14に示
すように、同調ロッド39の作動に連動して第1軸芯P
1周りに揺動する揺動アーム44を設け、この揺動アー
ム44の揺動に連動して直線径路に沿って往復移動する
棒状のスライド部材45を設け、このスライド部材45
に、先端に前記旋回用プッシュプルワイヤ41を止着す
るとともにガイドローラ47を回転自在に支持した揺動
レバー46を第1軸芯P1と平行な第2軸芯P2周りに
揺動自在に取付け、前記ガイドローラ47を移動案内す
るガイドレール48を固定部に第2軸芯P2と平行な第
3軸芯P3周りに揺動自在に取付け、このガイドレール
48に旋回用レリーズワイヤ38により引き操作されて
ガイドレール48を揺動させる引き操作アーム49を固
着して構成されている。When the turning lever 35 is in the "straight forward" position and the auxiliary transmission 13 is in the high-speed transmission state, the synchronizing means 40 controls the center gear 14 and the side gear 16L,
16R is rotated in the same direction at the same rotational speed, the synchronizing relationship between the two continuously variable transmissions 9 and 10 is set, and the maximum operating position of the turning lever 35 when the auxiliary transmission 13 is in the high-speed transmission state. Gears 16L and 16R with turning operation
Is a means for associating the two continuously variable transmissions 9 and 10 such that the rotation speed in the direction opposite to that of the center gear 14 becomes the rotation speed of the center gear 14. Specifically, as shown in FIGS. 4 to 14, the first axis P
A swing arm 44 swinging around the arm 1 is provided, and a rod-shaped slide member 45 reciprocating along a linear path in conjunction with the swing of the swing arm 44 is provided.
In addition, the swing push-pull wire 41 is fixed to the tip and a swing lever 46 rotatably supporting the guide roller 47 is swingably mounted around a second axis P2 parallel to the first axis P1. A guide rail 48 for moving and guiding the guide roller 47 is swingably mounted on a fixed portion around a third axis P3 parallel to the second axis P2, and a pulling operation is performed on the guide rail 48 by a release wire 38 for rotation. Then, a pull operation arm 49 for swinging the guide rail 48 is fixed.
【0020】そして、変速用トラニオン軸9aが変速中
立位置Nにあると、図8に示すように、ガイドローラ4
7がガイドレール48のうち第3軸芯P3に位置し、変
速用トラニオン軸9aが前進域Fにあると、図7に示す
ように、ガイドローラ47がガイドレール48のうち第
3軸芯P3の一方側の部分に位置し、変速用トラニオン
軸9aが後進域Rにあると、図9に示すように、ガイド
ローラ47がガイドレール48のうち第3軸芯P3の他
方側の部分に位置するようにスライド部材45とガイド
レール48との位置関係が設定されている。When the gearshift trunnion shaft 9a is at the gearshift neutral position N, as shown in FIG.
7 is located on the third shaft center P3 of the guide rail 48 and the transmission trunnion shaft 9a is in the forward movement range F, the guide roller 47 is moved to the third shaft center P3 of the guide rail 48 as shown in FIG. When the transmission trunnion shaft 9a is located in the reverse region R, the guide roller 47 is located at the other side of the third rail P3 of the guide rail 48, as shown in FIG. The positional relationship between the slide member 45 and the guide rail 48 is set so as to perform the operation.
【0021】かつ、前記ガイドレール48は、第3軸芯
P3周りに揺動することにより、ガイドローラ47、つ
まりは、揺動レバー46を揺動させて旋回用プッシュプ
ルワイヤ41を作動させることにより旋回用トラニオン
軸10aを操作するものであって、旋回用レリーズワイ
ヤ38による引き操作により、スライド部材45と平行
な姿勢よりも一方側端を一側に位置させる第1傾斜姿勢
から平行な姿勢よりも一方側端を他側に位置させる第2
傾斜姿勢にまでスプリング50による付勢力に抗して揺
動操作されるようになっており、平行な姿勢が揺動レバ
ー46を変速中立姿勢に位置させて旋回用トラニオン軸
10aを変速中立位置Nに位置させる位置に設定されて
いる。詳述すると、図7,図10,図11に示すよう
に、ガイドローラ47が一方側に位置する状態で第1傾
斜姿勢と平行な姿勢とのあいだの姿勢に位置することに
より揺動レバー46を前進姿勢に位置させ、平行な姿勢
に位置することにより揺動レバー46を変速中立姿勢に
位置させ、平行な姿勢と第2傾斜姿勢とのあいだの姿勢
に位置することにより揺動レバー46を後進姿勢に位置
させる一方、図9,図12,図13に示すように、ガイ
ドローラ47が他方側に位置する状態で第1傾斜姿勢と
平行な姿勢とのあいだの姿勢に位置することにより揺動
レバー46を後進姿勢に位置させ、平行な姿勢に位置す
ることにより揺動レバー46を変速中立姿勢に位置さ
せ、平行な姿勢と第2傾斜姿勢とのあいだの姿勢に位置
することにより揺動レバー46を前進姿勢に位置させる
ものである。Further, the guide rail 48 swings around the third axis P3 to swing the guide roller 47, that is, the swing lever 46, to operate the turning push-pull wire 41. The pulling operation by the turning release wire 38 causes the turning end of the turning trunnion shaft 10a to be moved from the first inclined position in which one end is positioned closer to one side than the position in parallel with the slide member 45. The second side of which one end is located on the other side
The swinging operation is performed to the inclined posture against the urging force of the spring 50, and the parallel posture is such that the swing lever 46 is positioned at the neutral position for shifting and the turning trunnion shaft 10 a is moved to the neutral position N for shifting. It is set to the position to be located at. More specifically, as shown in FIGS. 7, 10, and 11, when the guide roller 47 is positioned on one side and in a posture between the first inclined posture and a posture parallel to the first inclined posture, the swing lever 46 is moved. Is positioned in the forward posture, and by positioning the rocking lever 46 in the parallel posture, the rocking lever 46 is positioned in the neutral position for shifting. By positioning the rocking lever 46 in the posture between the parallel posture and the second inclined posture, the rocking lever 46 is moved. 9, 12, and 13, the guide roller 47 is swung by being in a posture between the first inclined posture and a posture parallel to the first inclined posture in a state in which the guide roller 47 is located on the other side, as shown in FIGS. The moving lever 46 is positioned in the reverse position, and is positioned in the parallel position, whereby the rocking lever 46 is positioned in the neutral position for shifting, and is rocked by being positioned between the parallel position and the second inclined position. Lever 4 The one in which is positioned in a forward posture.
【0022】従って、今、主変速レバー34が変速中立
位置Nに位置し、旋回レバー35が「直進」の位置に位
置していると、図8に示すように、変速用トラニオン軸
9aが変速中立位置Nに位置して走行変速用の油圧モー
タ9Mが停止しているとともに、ガイドレール48が第
1傾斜姿勢にあるものの、ガイドローラ47が第3軸芯
P3位置にあって揺動レバー46が変速中立姿勢に位置
していることで旋回トラニオン軸10aが変速中立位置
Nに位置して旋回用の油圧モータ10Mも停止してい
る。この状態で主変速レバー34を前進域Fに操作する
と、図7に示すように、変速用トラニオン軸9aがその
主変速レバー34の操作位置に相当する前進域Fの変速
位置に操作されて走行変速用の油圧モータ9Mが主変速
レバー34の操作位置に応じた回転数で前進回転すると
ともに、ガイドローラ47がガイドレール48の一方側
の部分に移動することで揺動レバー46が前進側に揺動
操作されることにより旋回用トラニオン軸10aが主変
速レバー34の操作位置に相当する前進域Fの変速位置
に操作されて旋回用の油圧モータ10Mが主変速レバー
34の操作位置に応じた、つまり、走行変速用の油圧モ
ータ9Mの回転数に比例した回転数で前進回転する。他
方、前記の状態で主変速レバー34を後進域Rに操作す
ると、図9に示すように、変速用トラニオン軸9aがそ
の主変速レバー34の操作位置に相当する後進域Rの変
速位置に操作されて走行変速用の油圧モータ9Mが主変
速レバー34の操作位置に応じた回転数で後進回転する
とともに、ガイドローラ47がガイドレール48の他方
側の部分に移動することで揺動レバー46が後進側に揺
動操作されることにより旋回用トラニオン軸10aが主
変速レバー34の操作位置に相当する後進域Rの変速位
置に操作されて旋回用の油圧モータ10Mが操作位置に
応じた、つまり、走行変速用の油圧モータ9Mの回転数
に比例した回転数で後進回転する。また、主変速レバー
34が変速中立位置Nに位置している状態で旋回レバー
35を「左」や「右」に倒す、つまり、旋回操作する
と、図14の(イ)(ロ)(ハ)に示すように、ガイド
レール48が揺動操作されるものの、ガイドローラ37
が第3軸芯P3にあって移動しないことにより揺動レバ
ー46が変速中立姿勢に維持されて、旋回操作にかかわ
らず、旋回用トラニオン軸10aは変速中立位置に維持
され旋回用の油圧モータ10Mは停止維持される。そし
て、主変速レバー34が前進域Fに操作された前進走行
状態で旋回レバー35を「左」や「右」に旋回操作する
と、図7,図10,図11に示すように、ガイドレール
48が引き揺動操作され、このガイドレール48の引き
揺動操作により、揺動レバー46が変速中立姿勢に操作
されるまでは、旋回トラニオン軸10aが前進域Fで減
速側に操作されることにより旋回用の油圧モータ10M
が無段階に減速されて旋回レバー35の操作位置に応じ
た回転数で前進回転し、揺動レバー46が変速中立姿勢
に操作されると、旋回用トラニオン軸10aが変速中立
位置Nに操作されることにより旋回用の油圧モータ10
Mが停止し、揺動レバー46が変速中立姿勢を越えて操
作されると、旋回用トラニオン軸10aが後進域Rで増
速側に操作されることにより旋回用の油圧モータ10M
が無段階に増速されて旋回レバー35の操作位置に応じ
た回転数で後進回転する。そして、旋回レバー35を
「直進」の位置に戻すと、ガイドレール48が第1傾斜
姿勢に復帰して、旋回用の油圧モータ10Mが元の回転
数で前進回転することになる。他方、主変速レバー34
が後進域Rに操作された後進走行状態で旋回レバー35
を「左」や「右」に旋回操作すると、図9,図12,図
13に示すように、ガイドレール48が引き揺動操作さ
れ、このガイドレール48の引き揺動操作により、揺動
レバー46が変速中立姿勢に操作されるまでは、旋回ト
ラニオン軸10aが後進域Rで減速側に操作されること
により旋回用の油圧モータ10Mが無段階に減速されて
旋回レバー35の操作位置に応じた回転数で後進回転
し、揺動レバー46が変速中立姿勢に操作されると、旋
回用トラニオン軸10aが変速中立位置Nに操作される
ことにより旋回用の油圧モータ10Mが停止し、揺動レ
バー46が変速中立姿勢を越えて操作されると、旋回用
トラニオン軸10aが前進域Fで増速側に操作されるこ
とにより旋回用の油圧モータ10Mが無段階に増速され
て旋回レバー35の操作位置に応じた回転数で前進回転
する。そして、旋回レバー35を「直進」の位置に戻す
と、ガイドレール48が第1傾斜姿勢に復帰して、旋回
用の油圧モータ10Mが元の回転数で後進回転すること
になる。Therefore, if the main shift lever 34 is now located at the shift neutral position N and the turning lever 35 is located at the "straight forward" position, the gear shifting trunnion shaft 9a is shifted as shown in FIG. While the hydraulic motor 9M for traveling speed is stopped at the neutral position N and the guide rail 48 is in the first inclined posture, the guide roller 47 is in the third shaft center P3 position and the swing lever 46 is Is located in the shift neutral position, the turning trunnion shaft 10a is located at the shift neutral position N, and the turning hydraulic motor 10M is also stopped. When the main shift lever 34 is operated in the forward range F in this state, the traveling trunnion shaft 9a is operated to the shift position in the forward range F corresponding to the operated position of the main shift lever 34 as shown in FIG. The shift hydraulic motor 9M rotates forward at a rotation speed corresponding to the operation position of the main shift lever 34, and the guide roller 47 moves to one side of the guide rail 48, so that the swing lever 46 moves forward. When the swinging operation is performed, the turning trunnion shaft 10a is operated to the shift position in the forward range F corresponding to the operating position of the main shift lever 34, and the turning hydraulic motor 10M is operated in accordance with the operating position of the main shift lever 34. That is, it rotates forward at a rotation speed proportional to the rotation speed of the traveling speed hydraulic motor 9M. On the other hand, when the main transmission lever 34 is operated in the reverse range R in the above state, the transmission trunnion shaft 9a is moved to the reverse position R corresponding to the operation position of the main transmission lever 34 as shown in FIG. As a result, the traveling speed hydraulic motor 9M reversely rotates at a rotation speed corresponding to the operation position of the main speed change lever 34, and the swing lever 46 is moved by the guide roller 47 moving to the other side of the guide rail 48. By being swung to the reverse side, the turning trunnion shaft 10a is operated to the shift position in the reverse region R corresponding to the operating position of the main shift lever 34, and the turning hydraulic motor 10M corresponds to the operating position, that is, The reverse rotation is performed at a rotation speed proportional to the rotation speed of the traveling speed hydraulic motor 9M. In addition, when the turning lever 35 is tilted to the left or right while the main shift lever 34 is located at the shift neutral position N, that is, when the turning operation is performed, (a), (b), and (c) of FIG. As shown in FIG. 7, although the guide rail 48 is operated to swing, the guide roller 37
Is in the third shaft center P3 and does not move, so that the swing lever 46 is maintained in the neutral position for shifting, and the turning trunnion shaft 10a is maintained in the neutral position for shifting and the hydraulic motor 10M for turning regardless of the turning operation. Is stopped and maintained. Then, when the turning lever 35 is turned to the left or right in the forward running state in which the main shift lever 34 is operated in the forward range F, the guide rail 48 is turned as shown in FIGS. The swinging trunnion shaft 10a is operated to the deceleration side in the forward range F until the swinging lever 46 is operated to the neutral position for shifting by the swinging operation of the guide rail 48. Hydraulic motor for turning 10M
When the swing lever 46 is operated to the neutral position for shifting, the turning trunnion shaft 10a is operated to the neutral position N for shifting. The hydraulic motor 10 for turning
When the swing lever 46 is operated beyond the neutral position for shifting, the turning trunnion shaft 10a is operated to the speed increasing side in the reverse region R, and the turning hydraulic motor 10M is operated.
Is steplessly increased, and reversely rotates at a rotation speed corresponding to the operation position of the turning lever 35. Then, when the turning lever 35 is returned to the "straight forward" position, the guide rail 48 returns to the first inclined posture, and the turning hydraulic motor 10M rotates forward at the original rotation speed. On the other hand, the main shift lever 34
Is operated in the reverse range R and the turning lever 35
When the is turned to the left or right, the guide rail 48 is pulled and rocked as shown in FIGS. 9, 12, and 13, and the rocking lever is Until 46 is operated to the neutral position for shifting, the turning hydraulic motor 10M is steplessly decelerated by operating the turning trunnion shaft 10a to the deceleration side in the reverse region R, and according to the operating position of the turning lever 35. When the swing lever 46 is operated to the neutral position for shifting and the swinging trunnion shaft 10a is operated to the neutral position N for shifting, the hydraulic motor 10M for swing is stopped, and the swing is rotated. When the lever 46 is operated beyond the shift neutral position, the turning hydraulic motor 10M is steplessly increased in speed by operating the turning trunnion shaft 10a to the speed increasing side in the forward movement range F, and the turning lever 35 is turned on. of To move forward rotated at a rotational speed corresponding to the work position. Then, when the turning lever 35 is returned to the "straight forward" position, the guide rail 48 returns to the first inclined posture, and the turning hydraulic motor 10M rotates backward at the original rotation speed.
【0023】旋回用の油圧モータ10Mの走行変速用の
油圧モータ9Mに比例した回転数は、旋回レバー35が
「直進」の位置に位置し、かつ、前記副変速装置13が
高速伝動状態にあるときに、センターギヤ14の回転数
とサイドギヤ16L,16Rの回転数とを同じにさせる
回転数に設定されている。The rotational speed of the turning hydraulic motor 10M in proportion to the traveling speed hydraulic motor 9M is such that the turning lever 35 is located at the "straight forward" position and the auxiliary transmission 13 is in a high-speed transmission state. At times, the rotation speed of the center gear 14 and the rotation speeds of the side gears 16L and 16R are set to the same rotation speed.
【0024】前記旋回レバー35の旋回操作で旋回用レ
リーズワイヤ38を介してガイドレール48を引き操作
する手段は、図15の(イ)(ロ)(ハ)に示すよう
に、旋回レバー35を揺動自在に支持するブラケット5
1に二本の操作アーム52L,52Rを旋回レバー35
の揺動軸芯P4周りに各別に揺動自在に取付け、前記旋
回レバー35の下部に、旋回レバー35の「左」への揺
動に伴い左の操作アーム52Lを中立位置から左回り揺
動させるとともに旋回レバー35の「右」への揺動に伴
い右の操作アーム52Rを中立位置から右回り揺動させ
る操作ピン53を付設し、前記ブラケット51に、左の
操作アーム52Lの中立位置からの右回り揺動及び右の
操作アーム52Rの中立位置からの左回り揺動を規制す
る位置決めピン54を取付け、両操作アーム52L,5
2Rにわたり両操作アーム52L,52Rを中立位置に
揺動付勢するスプリング55を設け、旋回用レリーズワ
イヤ38のインナーワイヤ38aの端部を左の操作アー
ム52Lに止着し、旋回用レリーズワイヤ38のアウタ
ーワイヤ38bの端部を右の操作アーム52Rに止着し
て構成されている。すなわち、旋回レバー35は前記ス
プリング55により「直進」の位置に揺動付勢されてお
り、旋回レバー35を「左」に倒し揺動操作することに
より、左の操作アーム52Lをスプリング55の付勢力
に抗して左回り揺動させることでインナーワイヤ38a
を引き操作してレリーズワイヤ38を引き作動させるこ
とでガイドレール48を揺動させ、旋回レバー35を
「右」に倒し揺動操作することにより、右の操作アーム
52Rをスプリング55の付勢力に抗して右回り揺動さ
せることでアウターワイヤ38bの端部をインナーワイ
ヤ38aの端部から遠ざけてレリーズワイヤ38を引き
作動させることでガイドレール48を揺動させるように
なっている。The means for pulling the guide rail 48 through the turning release wire 38 by the turning operation of the turning lever 35, as shown in FIGS. Bracket 5 for swinging support
The two operating arms 52L, 52R are pivoted to one
Are pivotally mounted around the pivot axis P4, respectively, and below the pivot lever 35, the left operation arm 52L pivots counterclockwise from the neutral position as the pivot lever 35 pivots to the left. At the same time, an operating pin 53 is provided for swinging the right operating arm 52R clockwise from the neutral position in accordance with the swinging of the turning lever 35 to the “right”, and the bracket 51 is attached to the bracket 51 from the neutral position of the left operating arm 52L. A positioning pin 54 for restricting the clockwise swing of the right arm and the clockwise swing of the right operating arm 52R from the neutral position is attached.
A spring 55 is provided to urge the two operation arms 52L, 52R to the neutral position over 2R, and the end of the inner wire 38a of the release release wire 38 is fixed to the left operation arm 52L. Of the outer wire 38b is fixed to the right operation arm 52R. That is, the swing lever 35 is urged to swing to the “straight-ahead” position by the spring 55, and the swing lever 35 is tilted to the left to swing the left operating arm 52 </ b> L with the spring 55. By swinging counterclockwise against the power, the inner wire 38a
By pulling the release wire 38 to pull the release rail 38, the guide rail 48 is rocked, and the swing lever 35 is tilted to the right to perform the rocking operation, so that the right operation arm 52R is biased by the spring 55. By oscillating clockwise, the end of the outer wire 38b is moved away from the end of the inner wire 38a, and the release wire 38 is pulled to actuate the guide rail 48.
【0025】前記補正手段43は、図17の(イ)
(ロ),図18に示すように、前記副変速装置13の変
速状態に応じて旋回用トラニオン軸10aの作動レバー
10bへの旋回用プッシュプルワイヤ41の取付け位置
を作動レバー10bの長手方向で変更することにより、
走行変速用の油圧モータ9Mの回転数が同じであっても
副変速装置13による変速でセンターギヤ14の回転数
が変わってサイドギヤ16L,16Rの回転数と異なる
ことを防止する手段であって、副変速レバー36により
副変速操作ワイヤ56を介して操作される副変速装置1
3の操作レバー36aの低位置Lから高位置Hへの揺動
で前記旋回用プッシュプルワイヤ41の作動レバー10
bへの取付けピン41aを旋回用トラニオン軸10aか
ら遠い第1位置PLから近い第2位置PHにスプリング
57による付勢力に抗して引っ張り移動させるように補
正ワイヤ42を設けて構成されている。前記第1位置P
Lは、旋回レバー35が「直進」の位置にある状態で副
変速装置13が低速伝動状態に切り換えられていると
き、センターギヤ14の回転数とサイドギヤ16L,1
6Rの回転数とを等しくさせるように作動レバー10b
に旋回用プッシュプルワイヤ41を連係させる位置であ
り、第2位置PHは、旋回レバーが「直進」の位置にあ
る状態で副変速装置13が高速伝動状態に切り換えられ
ているとき、センターギヤ14の回転数とサイドギヤ1
6L,16Rの回転数とを等しくさせるように作動レバ
ー10bに旋回用プッシュプルワイヤ41を連係させる
位置である。つまり、旋回レバー35が「直進」の位置
にある状態で主変速レバー34を操作した際、副変速装
置13が高速伝動状態にあると、その主変速レバー34
の操作量に対する作動レバー10bの揺動量を多くして
旋回用の油圧モータ10Mの回転数を多くすることでセ
ンターギヤ14の回転数とサイドギヤ16L,16Rの
回転数とを等しくさせ、副変速装置13が低速伝動状態
にあると、主変速レバー34の操作量に対する作動レバ
ー10bの揺動量を少なくして旋回用の油圧モータ10
Mの回転数を少なくすることでセンターギヤ14の回転
数とサイドギヤ16L,16Rの回転数とを等しくさせ
るようになっている。The correcting means 43 is provided as shown in FIG.
(B) As shown in FIG. 18, the mounting position of the push-pull wire 41 for turning to the operating lever 10 b of the turning trunnion shaft 10 a is determined in the longitudinal direction of the operating lever 10 b according to the shift state of the auxiliary transmission 13. By making changes,
Means for preventing the rotational speed of the center gear 14 from changing due to the shift by the auxiliary transmission device 13 and differing from the rotational speeds of the side gears 16L and 16R even if the rotational speed of the traveling speed hydraulic motor 9M is the same. The auxiliary transmission 1 operated by the auxiliary transmission lever 36 via the auxiliary transmission operation wire 56
The swing of the operating lever 36a from the low position L to the high position H of the third operating lever 36a causes the operating lever 10 of the push-pull wire 41 for turning.
A correction wire 42 is provided so as to pull the attachment pin 41a to the second position PH from a first position PL far from the turning trunnion shaft 10a to a second position PH near the turning trunnion shaft 10a against the urging force of the spring 57. The first position P
L indicates the number of rotations of the center gear 14 and the side gears 16L, 1 when the sub-transmission 13 is switched to the low-speed transmission state while the turning lever 35 is in the “straight forward” position.
Operating lever 10b so as to make the rotation speed equal to that of 6R.
The second position PH is a position where the auxiliary transmission 13 is switched to the high-speed transmission state with the turning lever in the “straight-ahead” position. Speed and side gear 1
This is a position where the turning push-pull wire 41 is linked to the operating lever 10b so as to make the rotation speeds of 6L and 16R equal. That is, when the main transmission lever 34 is operated in a state where the turning lever 35 is in the “straight forward” position and the sub transmission 13 is in the high-speed transmission state, the main transmission lever 34 is operated.
The rotational speed of the hydraulic motor 10M for turning is increased by increasing the swing amount of the operating lever 10b with respect to the operation amount of, so that the rotational speed of the center gear 14 and the rotational speeds of the side gears 16L and 16R are equalized, and the auxiliary transmission 13 is in the low-speed transmission state, the swing amount of the operating lever 10b with respect to the operation amount of the main shift lever 34 is reduced, and the hydraulic motor 10 for turning is reduced.
By reducing the rotation speed of M, the rotation speed of the center gear 14 and the rotation speeds of the side gears 16L and 16R are made equal.
【0026】そして、図19,図20に示すように、セ
ンターギヤ14の前進最大回転数と後進最大回転数とは
等しい回転数に設定されており、副変速装置13が高速
伝動状態にあるときのサイドギヤ16L,16Rの前進
最大回転数及び後進最大回転数のそれぞれは、副変速装
置13が高速伝動状態にあるときのセンターギヤ14の
前進最大回転数及び後進最大回転数と等しい回転数に設
定され、副変速装置13が低速伝動状態にあるときのサ
イドギヤ16L,16Rの前進最大回転数及び後進最大
回転数のそれぞれは、副変速装置13が低速伝動状態に
あるときのセンターギヤ14の前進最大回転数及び後進
最大回転数と等しい回転数に設定されている。As shown in FIGS. 19 and 20, when the maximum forward rotation speed and the maximum reverse rotation speed of the center gear 14 are set to be equal to each other and the subtransmission 13 is in a high speed transmission state. The maximum forward rotation speed and the maximum reverse rotation speed of the side gears 16L and 16R are set to be equal to the maximum forward rotation speed and the maximum reverse rotation speed of the center gear 14 when the auxiliary transmission 13 is in the high-speed transmission state. The maximum forward rotation speed and the maximum reverse rotation speed of the side gears 16L and 16R when the auxiliary transmission 13 is in the low-speed transmission state are determined by the maximum forward rotation of the center gear 14 when the auxiliary transmission 13 is in the low-speed transmission state. The rotation speed is set to be equal to the rotation speed and the maximum reverse rotation speed.
【0027】前記油圧アクチュエータ32は、図16に
示すように、シフト部材17L,17Rをセンター位置
に位置させる姿勢に両シフタ33L,33Rを位置させ
る直進作動状態と、左のシフト部材17Lのみをサイド
位置に位置させる姿勢に左のシフタ33Lを位置させる
左旋回作動状態と、右のシフト部材17Rのみをサイド
位置に位置させる姿勢に右のシフタ33Rを位置させる
右旋回作動状態とに操作弁58を介して切り換え操作さ
れるものであって、操作弁58は、制御装置59によ
り、旋回スイッチ60で旋回レバー35が「直進」の位
置に位置することが検出されているときには油圧アクチ
ュエータ32を直進作動状態にさせる「直進」の位置に
あり、旋回スイッチ60で旋回レバー35が「左」旋回
位置に位置することが検出されているときには油圧アク
チュエータ35を左旋回作動状態にさせる「左旋回」位
置にあり、旋回スイッチ60で旋回レバー35が「右」
旋回位置に位置することが検出されているときには油圧
アクチュエータ35を右旋回作動状態にさせる「右旋
回」位置にあるように操作される。つまり、操作弁58
は旋回レバー35の操作状態に応じて操作される。そし
て、旋回スイッチ60、シフト部材17L,17R、摩
擦クラッチ19L,19R、油圧アクチュエータ32、
シフター33L,33R、操作弁58、制御装置59か
ら、旋回レバー35の旋回操作に基づいて左右の走行装
置1のうち旋回内側のものの走行変速用の無段変速装置
9への連動を断つとともに旋回内側の走行装置1を旋回
用の無段変速装置10に連動させる旋回連動手段が構成
されている。前記旋回スイッチ60は、図15に示すよ
うに、旋回レバー35の「左」旋回位置への旋回操作に
伴い旋回レバー35に連設の操作アーム60aにより押
圧されて左旋回スイッチ部をオンさせ、旋回レバーの
「右」旋回位置への旋回操作に伴い前記操作アーム60
aにより押圧されて右旋回スイッチ部をオンさせるもの
である。As shown in FIG. 16, the hydraulic actuator 32 has a linear operation state in which both shifters 33L and 33R are positioned in a position where the shift members 17L and 17R are positioned at the center position, and only the left shift member 17L is The operation valve 58 is in a left turning operation state in which the left shifter 33L is positioned in the position where the right shift member 33R is positioned in the side position in which only the right shift member 17R is positioned in the side position. The control valve 59 controls the hydraulic actuator 32 to move straight when the control device 59 detects that the turning lever 35 is at the “straight” position by the turning switch 60. In the "straight ahead" position to be activated, the swivel lever 35 is in the "left" swivel position by the swivel switch 60. Cause the hydraulic actuator 35 to the left turning operation state when it is detected is in the "left turn" position, in turn switch 60 pivot lever 35 is "right"
When it is detected that the hydraulic actuator 35 is located at the turning position, the hydraulic actuator 35 is operated so as to be at the "right turning" position for bringing the hydraulic actuator 35 into the right turning operation state. That is, the operation valve 58
Is operated in accordance with the operation state of the turning lever 35. Then, the turning switch 60, the shift members 17L and 17R, the friction clutches 19L and 19R, the hydraulic actuator 32,
From the shifters 33L, 33R, the operation valve 58, and the control device 59, based on the turning operation of the turning lever 35, the interlocking of the left and right traveling devices 1 with the continuously variable transmission 9 for traveling speed change is performed while turning. Turning interlocking means for interlocking the inner traveling device 1 with the turning continuously variable transmission 10 is configured. As shown in FIG. 15, the turning switch 60 is pressed by an operation arm 60 a connected to the turning lever 35 in accordance with the turning operation of the turning lever 35 to the “left” turning position, and turns on the left turning switch unit. With the turning operation of the turning lever to the “right” turning position, the operation arm 60 is moved.
a to turn on the right turning switch unit.
【0028】従って、旋回レバー35を「直進」の位置
に操作してシフト部材17L,17Rをともにセンター
位置に位置させることにより、センターギヤ14、爪ク
ラッチ18L,18R、シフト部材17L,17Rを介
して走行変速用の無段変速装置9で左右の走行装置1を
駆動することになり、これにより、左右の走行装置1を
同方向に等速作動させての直進走行状態を得ることがで
き、この状態で走行変速用の無段変速装置9を主変速レ
バー34で操作することにより、直進前進走行状態での
無段変速及び中立停止、直進後進走行状態での無段変速
を行え、副変速装置13を副変速レバー36で操作する
ことにより、走行速度の高低二段切り換えを行えるので
ある。Therefore, by operating the turning lever 35 to the "straight forward" position to position both the shift members 17L and 17R at the center position, the center gear 14, the pawl clutches 18L and 18R, and the shift members 17L and 17R are interposed. In this way, the left and right traveling devices 1 are driven by the continuously variable transmission 9 for traveling speed change, whereby it is possible to obtain a straight traveling state by operating the left and right traveling devices 1 at the same speed in the same direction. In this state, by operating the continuously variable transmission 9 for traveling speed change with the main transmission lever 34, continuously variable transmission and neutral stop in the straight forward traveling state and continuously variable transmission in the straight forward traveling state can be performed. By operating the device 13 with the auxiliary transmission lever 36, the traveling speed can be switched between high and low.
【0029】そして、図19,図20中の太い実線a,
bで示すように、副変速装置13を高速伝動状態に切り
換えての移動用の直進前進高速走行状態や副変速装置1
3を低速伝動状態に切り換えての作業用の直進前進低速
走行状態において、旋回レバー35を「左」に旋回操作
すると、左のシフト部材17Lがサイド位置に位置し
て、右の走行装置1は前記のように走行変速用の無段変
速装置9で前進駆動される一方、左の中継ギヤ15L、
左のサイドギヤ16L、左の摩擦クラッチ19L、左の
シフト部材17Lを介して旋回用の無段変速装置10で
左の走行装置1が駆動されることになり、旋回レバー3
5の「左」への操作量を増大させるに伴って旋回用の無
段変速装置10による前進駆動速度が次第に減速され、
これに伴う左右の走行装置1の速度差で左を旋回内側と
する前進緩旋回を行えるのであり、旋回レバー35の
「左」への操作量をなおも増大させて旋回用の無段変速
装置10を変速中立状態にすることにより、左の走行装
置1を停止させて左を旋回内側とする前進左信地旋回
(前進左ピボットターン)を行えるのであり、旋回レバ
ー35を「左」の最大操作位置にまで操作すると、旋回
用の無段変速装置10による後進駆動速度が増速される
ことで左の走行装置1を前進走行する右の走行装置1と
等しい速さで後進走行させての左超信地旋回(左スピン
ターン)を行えるのである。なお、図19中の太い実線
cは、前進高速走行する右の走行装置1の走行速度を示
し、図20中の太い実線dは、前進低速走行する右の走
行装置1の走行速度を示す。The thick solid lines a and b in FIGS.
As shown by b, when the sub-transmission 13 is switched to the high-speed transmission state, the vehicle is traveling straight forward at high speed and the sub-transmission
When the turning lever 35 is turned to the "left" in the straight forward forward low-speed running state for work with the 3 being switched to the low-speed transmission state, the left shift member 17L is located at the side position, and the right running device 1 As described above, while being driven forward by the continuously variable transmission 9 for traveling speed change, the left relay gear 15L,
The left traveling device 1 is driven by the turning continuously variable transmission 10 via the left side gear 16L, the left friction clutch 19L, and the left shift member 17L.
5, the forward drive speed of the continuously variable transmission 10 for turning is gradually reduced with an increase in the operation amount to the "left" of 5,
With the speed difference between the left and right traveling devices 1 accompanying this, a forward slow turning with the left turning inside can be performed, and the operation amount of the turning lever 35 to the “left” is still increased, so that the continuously variable transmission for turning. By setting 10 to the neutral position for shifting, the left traveling device 1 is stopped, and a forward left pivot turn (forward left pivot turn) with the left turning inside can be performed, and the turning lever 35 is set to the maximum left position. When the vehicle is operated to the operation position, the reverse drive speed of the continuously variable transmission 10 for turning is increased, so that the left traveling device 1 travels backward at the same speed as the right traveling device 1 traveling forward. You can make a left spin turn (left spin turn). Note that a thick solid line c in FIG. 19 indicates the traveling speed of the right traveling device 1 traveling forward and high speed, and a thick solid line d in FIG. 20 indicates the traveling speed of the right traveling device 1 traveling forward and low speed.
【0030】また、図19,図20中の太い実線e,f
で示すように、前記の移動用の直進前進高速走行状態や
作業用の直進前進低速走行状態において、旋回レバー3
5を「右」に旋回操作すると、右のシフト部材17Rが
サイド位置に位置して、左の走行装置1は前記のように
走行変速用の無段変速装置9で前進駆動される一方、右
の中継ギヤ15R、右のサイドギヤ16R、右の摩擦ク
ラッチ19R、右のシフト部材17Rを介して旋回用の
無段変速装置10で右の走行装置1が駆動されることに
なり、旋回レバー35の「右」への操作量を増大させる
に伴って旋回用の無段変速装置10による前進駆動速度
が次第に減速され、これに伴う左右の走行装置1の速度
差で右を旋回内側とする前進緩旋回を行えるのであり、
旋回レバー35の「右」への操作量をなおも増大させて
旋回用の無段変速装置10を変速中立状態にすることに
より、右の走行装置1を停止させて右を旋回内側とする
前進右信地旋回(前進右ピボットターン)を行えるので
あり、旋回レバー35を「右」の最大操作位置にまで操
作すると、旋回用の無段変速装置10による後進駆動速
度が増速されることで右の走行装置1を前進走行する左
の走行装置1と等しい速さで後進走行させての右超信地
旋回(右スピンターン)を行えるのである。なお、図1
9中の太い実線gは、前進高速走行する左の走行装置1
の走行速度を示し、図20中の太い実線hは、前進低速
走行する左の走行装置1の走行速度を示す。The thick solid lines e and f in FIGS.
As shown by the arrow, in the above-described traveling straight forward high-speed traveling state for work and the straight traveling forward low-speed traveling state for work,
5, the right shift member 17R is located at the side position, and the left traveling device 1 is driven forward by the continuously variable transmission 9 for traveling speed, while the right traveling member 17R is moved to the right position. The right traveling device 1 is driven by the continuously variable transmission 10 for turning via the relay gear 15R, the right side gear 16R, the right friction clutch 19R, and the right shift member 17R. As the operation amount to the “right” is increased, the forward drive speed of the continuously variable transmission 10 for turning is gradually reduced, and the speed difference between the left and right traveling devices 1 is accompanied by the slow forward driving with the right turning inside. You can make a turn,
By further increasing the operation amount of the turning lever 35 to the “right” to bring the continuously variable transmission 10 for turning into the neutral state of shifting, the right traveling device 1 is stopped and the right is turned inside the turning. A right pivot turn (forward right pivot turn) can be performed. When the turning lever 35 is operated to the maximum operation position of “right”, the reverse drive speed of the continuously variable transmission 10 for turning is increased. It is possible to perform a right super pivot turn (right spin turn) by moving the right traveling device 1 backward and traveling at the same speed as the left traveling device 1 traveling forward. FIG.
9, a thick solid line g indicates the left traveling device 1 traveling forward and at high speed.
The thick solid line h in FIG. 20 indicates the traveling speed of the left traveling device 1 traveling forward and at low speed.
【0031】他方、図19,図20中の太い破線i,j
で示すように、副変速装置13を高速伝動状態に切り換
えての移動用の直進後進高速走行状態や副変速装置13
を低速伝動状態に切り換えての作業用の直進後進低速走
行状態において、旋回レバー35を「左」に旋回操作す
ると、左のシフト部材17Lがサイド位置に位置して、
右の走行装置1は前記のように走行変速用の無段変速装
置9で後進駆動される一方、左の中継ギヤ15L、左の
サイドギヤ16L、左の摩擦クラッチ19L、左のシフ
ト部材17Lを介して旋回用の無段変速装置10で左の
走行装置1が駆動されることになり、旋回レバー35の
「左」への操作量を増大させるに伴って旋回用の無段変
速装置10による後進駆動速度が次第に減速され、これ
に伴う左右の走行装置1の速度差で左を旋回内側とする
後進緩旋回を行えるのであり、旋回レバー35の「左」
への操作量をなおも増大させて旋回用の無段変速装置1
0を変速中立状態にすることにより、左の走行装置1を
停止させて左を旋回内側とする後進左信地旋回(後進左
ピボットターン)を行えるのであり、旋回レバー35を
「左」の最大操作位置にまで操作すると、旋回用の無段
変速装置10による前進駆動速度が増速されることで左
の走行装置1を後進走行する右の走行装置1と等しい速
さで前進走行させての左超信地旋回(左スピンターン)
を行えるのである。なお、図19中の太い破線kは、後
進高速走行する右の走行装置1の走行速度を示し、図2
0中の太い破線mは、後進低速走行する右の走行装置1
の走行速度を示す。On the other hand, the thick broken lines i and j in FIGS.
As shown by the arrow, the sub-transmission 13 is switched to the high-speed transmission state, and the vehicle is traveling straight forward and backward at a high speed.
When the turning lever 35 is turned to the “left” in a working straight-ahead low-speed running state while switching to the low-speed transmission state, the left shift member 17L is located at the side position,
The right traveling device 1 is driven backward by the continuously variable transmission 9 for traveling speed change, as described above, while being driven via the left relay gear 15L, the left side gear 16L, the left friction clutch 19L, and the left shift member 17L. The traveling device 1 on the left is driven by the continuously variable transmission 10 for turning, and the reverse drive by the continuously variable transmission 10 for turning is performed with an increase in the operation amount of the turning lever 35 to the left. The drive speed is gradually reduced, and the speed difference between the left and right traveling devices 1 can cause a slow reverse turning with the left turning inside.
Continuously variable transmission 1 for turning by further increasing the operation amount to
By setting 0 to the shift neutral state, it is possible to stop the left traveling device 1 and perform a reverse left pivot turn (reverse left pivot turn) with the left turning inside, and set the turning lever 35 to the maximum left position. When the vehicle is operated to the operation position, the forward drive speed of the continuously variable transmission 10 for turning is increased, so that the left traveling device 1 travels forward at the same speed as the right traveling device 1 traveling backward. Turn left super turn (left spin turn)
You can do it. Note that a thick broken line k in FIG. 19 indicates the traveling speed of the right traveling device 1 that travels at a high speed in the reverse direction.
A thick broken line m in 0 indicates the right traveling device 1 that travels backward at low speed.
Shows the running speed of the vehicle.
【0032】また、図19,図20中の太い破線n,p
で示すように、前記の移動用の直進後進高速走行状態や
作業用の直進後進低速走行状態において、旋回レバー3
5を「右」に旋回操作すると、右のシフト部材17Rが
サイド位置に位置して、左の走行装置1は前記のように
走行変速用の無段変速装置9で後進駆動される一方、右
の中継ギヤ15R、右のサイドギヤ16R、右の摩擦ク
ラッチ19R、右のシフト部材17Rを介して旋回用の
無段変速装置10で右の走行装置1が駆動されることに
なり、旋回レバー35の「右」への操作量を増大させる
に伴って旋回用の無段変速装置10による後進駆動速度
が次第に減速され、これに伴う左右の走行装置1の速度
差で右を旋回内側とする後進緩旋回を行えるのであり、
旋回レバー35の「右」への操作量をなおも増大させて
旋回用の無段変速装置10を変速中立状態にすることに
より、右の走行装置1を停止させて右を旋回内側とする
後進右信地旋回(後進右ピボットターン)を行えるので
あり、旋回レバー35を「右」の最大操作位置にまで操
作すると、旋回用の無段変速装置10による前進駆動速
度が増速されることで右の走行装置1を後進走行する左
の走行装置1と等しい速さで前進走行させての右超信地
旋回(右スピンターン)を行えるのである。なお、図1
9中の太い実線qは、後進高速走行する左の走行装置1
の走行速度を示し、図20中の太い実線rは、後進低速
走行する左の走行装置1の走行速度を示す。The thick broken lines n and p in FIGS.
As shown by the arrow, in the above-mentioned traveling straight backward high-speed traveling state for work or the straight traveling backward low-speed traveling state for work,
When the vehicle 5 is turned to the right, the right shift member 17R is located at the side position, and the left traveling device 1 is driven backward by the continuously variable transmission 9 for traveling speed, while The right traveling device 1 is driven by the continuously variable transmission 10 for turning via the relay gear 15R, the right side gear 16R, the right friction clutch 19R, and the right shift member 17R. As the amount of operation to the “right” is increased, the reverse drive speed of the continuously variable transmission 10 for turning is gradually reduced, and the speed difference between the left and right traveling devices 1 causes the right side to turn inside the vehicle slowly. You can make a turn,
The amount of operation of the turning lever 35 to the “right” is still increased, and the continuously variable transmission 10 for turning is brought into the neutral state for shifting, so that the right traveling device 1 is stopped and the right is turned inside the reverse. A right pivot turn (reverse right pivot turn) can be performed. When the turning lever 35 is operated to the maximum operation position of “right”, the forward drive speed of the continuously variable transmission 10 for turning is increased. It is possible to perform a right super pivot turn (right spin turn) by running the right traveling device 1 forward at the same speed as the left traveling device 1 traveling backward. FIG.
9, a thick solid line q indicates the traveling device 1 on the left that travels at a high speed in reverse.
The thick solid line r in FIG. 20 indicates the traveling speed of the left traveling device 1 that travels backward at low speed.
【0033】かつ、前記連係操作手段は、図14の
(イ)(ロ)(ハ)に示すように、前記旋回レバー35
の旋回操作のうち正転減速操作(前進走行時における前
進速度減速操作及び後進走行時における後進速度減速操
作)に伴い旋回用の無段変速装置10が変速中立状態に
なったときに引き操作アーム49に連動するシャフト7
0に付設の押し具71に接当して操作抵抗を増大させる
とともに、引き続く旋回レバー35の逆転増速操作(前
進走行時における後進速度増速操作及び後進走行時にお
ける前進速度増速操作)に伴い引き操作アーム49で押
されて圧縮されることによりその操作量の増大に伴い操
作抵抗を増大させる圧縮スプリング72を備えている。
前記シャフト70は、圧縮スプリング72に挿通して圧
縮スプリング72の変形ガイドを兼用するものである。As shown in FIGS. 14 (a), (b) and (c), the link operation means is provided with the turning lever 35.
The pull operation arm when the continuously variable transmission 10 for turning is brought into the neutral state for shifting in accordance with the forward rotation deceleration operation (forward speed deceleration operation during forward traveling and reverse speed deceleration operation during reverse traveling) among the turning operations of Shaft 7 linked to 49
In addition to increasing the operating resistance by contacting the pusher 71 provided at 0, the reverse rotation speed increasing operation of the turning lever 35 (the reverse speed increasing operation during forward running and the forward speed increasing operation during reverse running) is performed. Accordingly, a compression spring 72 is provided which is pushed and compressed by the pull operation arm 49 to increase the operation resistance as the operation amount increases.
The shaft 70 is inserted into the compression spring 72 and also serves as a deformation guide for the compression spring 72.
【0034】このようにしてコンバインは、旋回レバー
35の「直進」位置への操作により左右の走行装置1を
ともに走行変速用の無段変速装置9で駆動させて直進走
行を行う一方、前記旋回レバー35の旋回操作域への旋
回操作により旋回内側の走行装置1を旋回用の無段変速
装置10で駆動させるとともに旋回レバー35の旋回操
作域への操作量の増大に伴い前記旋回用の無段変速装置
10を減速作動・中立状態・逆転増速作動させて各種形
態の旋回を行うように構成されている。In this way, the combine travels straight by driving the right and left traveling devices 1 by the continuously variable transmission 9 for traveling speed change by operating the turning lever 35 to the "straight ahead" position. The traveling device 1 on the inside of the turn is driven by the continuously variable transmission 10 for turning by turning operation of the lever 35 to the turning operation area, and with the increase in the amount of operation of the turning lever 35 to the turning operation area, the non-turning operation is performed. The speed change device 10 is configured to perform various forms of turning by performing a deceleration operation, a neutral state, and a reverse rotation acceleration operation.
【0035】そして、前記走行装置1への伝動系に連動
した、つまり、走行変速用の油圧モータ9Mの出力軸9
Aから分岐させた前記刈取部4への伝動系には、刈取部
4への伝動を断続する刈取クラッチ61と刈取変速装置
62とが介装されている。Further, the output shaft 9 of the hydraulic motor 9M for traveling speed is interlocked with the transmission system to the traveling device 1.
In the transmission system to the reaping unit 4 branched from A, a reaping clutch 61 and a reaping transmission 62 for intermittently transmitting power to the reaping unit 4 are interposed.
【0036】前記刈取クラッチ61は刈取変速装置62
をもって兼用構成されている。つまり、刈取変速装置6
2が非伝動状態にあることでクラッチ切りを現出し、刈
取変速装置62が変速伝動状態にあることでクラッチ入
りを現出するように構成されている。The reaping clutch 61 includes a reaping transmission 62.
Is also used. That is, the reaper transmission 6
When the transmission 2 is in the non-transmission state, the clutch is released, and when the cutting transmission 62 is in the transmission state, the clutch is engaged.
【0037】〔別実施形態〕上記実施の形態では、旋回
操作具35として旋回レバーを示したが、旋回操作具3
5はステアリングハンドルであっても良い。[Alternative Embodiment] In the above embodiment, the turning lever is shown as the turning operation tool 35.
Reference numeral 5 may be a steering handle.
【0038】上記実施の形態では、作業機としてコンバ
インを示したが、本発明は各種の作業機に適用すること
ができる。In the above embodiment, a combine is shown as a working machine, but the present invention can be applied to various working machines.
【0039】上記実施の形態では、走行装置1として、
クローラ式のものを示したが、走行装置1としては、三
つ以上の車輪を備えた多輪式のものであっても良い。In the above embodiment, the traveling device 1 is
Although the crawler type is shown, the traveling device 1 may be a multi-wheel type having three or more wheels.
【図1】コンバインの側面図FIG. 1 is a side view of a combine.
【図2】伝動系統図FIG. 2 Transmission system diagram
【図3】操作連係機構の系統図FIG. 3 is a system diagram of an operation linking mechanism.
【図4】同調手段の横断平面図FIG. 4 is a cross-sectional plan view of the tuning means.
【図5】同調手段の斜視図FIG. 5 is a perspective view of a tuning means.
【図6】同調手段の縦断正面図FIG. 6 is a longitudinal sectional front view of the tuning means.
【図7】走行変速用の無段変速装置を前進に切り換えた
状態の同調手段の縦断側面図FIG. 7 is a longitudinal sectional side view of the tuning means in a state in which the continuously variable transmission for traveling transmission is switched to forward.
【図8】走行変速用の無段変速装置を中立に切り換えた
状態の同調手段の縦断側面図FIG. 8 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling speed is switched to neutral.
【図9】走行変速用の無段変速装置を後進に切り換えた
状態の同調手段の縦断側面図FIG. 9 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling speed is switched to reverse.
【図10】走行変速用の無段変速装置を前進にかつ旋回
用の無段変速装置を中立に切り換えた状態の同調手段の
縦断側面図FIG. 10 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling is switched to the forward direction and the continuously variable transmission for turning is switched to the neutral position.
【図11】走行変速用の無段変速装置を前進にかつ旋回
用の無段変速装置を後進に切り換えた状態の同調手段の
縦断側面図FIG. 11 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling speed is switched to the forward direction and the continuously variable transmission for turning is switched to the reverse direction.
【図12】走行変速用の無段変速装置を後進にかつ旋回
用の無段変速装置を中立に切り換えた状態の同調手段の
縦断側面図FIG. 12 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling speed is switched to reverse and the continuously variable transmission for turning is switched to neutral.
【図13】走行変速用の無段変速装置を後進にかつ旋回
用の無段変速装置を後進に切り換えた状態の同調手段の
縦断側面図FIG. 13 is a longitudinal sectional side view of the tuning means in a state where the continuously variable transmission for traveling speed is switched to reverse and the continuously variable transmission for turning is switched to reverse.
【図14】引き操作アームの作動説明図FIG. 14 is an explanatory diagram of the operation of the pull operation arm.
【図15】引き操作手段の作動説明図FIG. 15 is an explanatory diagram of the operation of the pulling operation means.
【図16】シフト部材の操作系統図FIG. 16 is an operation system diagram of a shift member.
【図17】補正手段の作動説明図FIG. 17 is an explanatory diagram of the operation of the correction means.
【図18】補正手段の縦断面図FIG. 18 is a longitudinal sectional view of a correction unit.
【図19】高速走行状態での旋回操作量と旋回内側の走
行装置の速度との関係を示す説明図FIG. 19 is an explanatory diagram showing a relationship between a turning operation amount in a high-speed running state and a speed of a traveling device inside a turn.
【図20】低速走行状態での旋回操作量と旋回内側の走
行装置の速度との関係を示す説明図FIG. 20 is an explanatory diagram showing a relationship between a turning operation amount in a low-speed running state and a speed of a traveling device inside the turning;
1 走行装置 9 走行変速用の無段変速装置 10 旋回用の無段変速装置 13 走行変速用の第2変速装置 14 第1走行装置駆動部 16L,16R 第2走行装置駆動部 35 旋回操作具 REFERENCE SIGNS LIST 1 traveling device 9 stepless transmission for traveling speed change 10 continuously variable transmission for turning 13 second speed change device for traveling speed change 14 first traveling device driving unit 16L, 16R second traveling device driving unit 35 turning operation tool
Claims (1)
の無段変速装置と第2変速装置とを直列に接続する状態
で介装してある作業機において、旋回操作具が直進位置
にあるとき前記走行変速用の第1無段変速装置と同調し
て作動するとともに旋回操作具の旋回操作量の増大に伴
って減速作動する旋回用の無段変速装置を設け、前記旋
回操作具の旋回操作に基づいて左右の走行装置のうち旋
回内側のものの走行変速用の無段変速装置への連動を断
つとともに旋回内側の走行装置を前記旋回用の無段変速
装置に連動させる旋回連動手段を設け、前記第2変速装
置の変速状態に基づいて第2変速装置が低速伝動状態に
あるほど旋回操作具の操作に基づく旋回用の無段変速装
置の作動量を小にすることにより走行変速用の無段変速
装置又は第2変速装置による第1走行装置駆動部と旋回
用の無段変速装置による第2走行装置駆動部とが等速回
転するように旋回操作具と旋回用の無段変速装置との連
動関係を補正する補正手段を設けてある作業機の操向装
置。In a working machine in which a continuously variable transmission for traveling and a second transmission are connected in series to a transmission system for left and right traveling devices in a state of being connected in series, a turning operation tool is in a straight-forward position. And a stepless transmission for turning which operates in synchronization with the first continuously variable transmission for traveling speed and decelerates with an increase in the amount of turning operation of the turning operation tool is provided. Turning interlocking means for interrupting the interlocking of the inner left and right traveling devices to the continuously variable transmission for traveling shift based on the turning operation of the left and right and interlocking the inner traveling traveling device with the continuously variable transmission for turning. The traveling speed is reduced by reducing the operation amount of the continuously variable transmission for turning based on the operation of the turning operation tool as the second transmission is in the low-speed transmission state based on the transmission state of the second transmission. Continuously variable transmission or second transmission Correction for correcting the interlocking relationship between the turning operation tool and the continuously variable transmission for turning such that the first traveling device drive unit for driving and the second traveling device drive unit for the continuously variable transmission for turning rotate at the same speed. A steering device for a working machine provided with a means.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19108197A JP3266830B2 (en) | 1997-07-16 | 1997-07-16 | Work equipment steering system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19108197A JP3266830B2 (en) | 1997-07-16 | 1997-07-16 | Work equipment steering system |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH1134908A JPH1134908A (en) | 1999-02-09 |
JP3266830B2 true JP3266830B2 (en) | 2002-03-18 |
Family
ID=16268553
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19108197A Expired - Fee Related JP3266830B2 (en) | 1997-07-16 | 1997-07-16 | Work equipment steering system |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3266830B2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4070697B2 (en) * | 2003-09-30 | 2008-04-02 | 株式会社クボタ | Work vehicle turning control device |
JP4795835B2 (en) * | 2006-04-07 | 2011-10-19 | 本田技研工業株式会社 | Hydraulic drive vehicle |
-
1997
- 1997-07-16 JP JP19108197A patent/JP3266830B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH1134908A (en) | 1999-02-09 |
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