JP5592829B2 - Agricultural machine gear transmission - Google Patents

Agricultural machine gear transmission Download PDF

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JP5592829B2
JP5592829B2 JP2011078546A JP2011078546A JP5592829B2 JP 5592829 B2 JP5592829 B2 JP 5592829B2 JP 2011078546 A JP2011078546 A JP 2011078546A JP 2011078546 A JP2011078546 A JP 2011078546A JP 5592829 B2 JP5592829 B2 JP 5592829B2
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裕治 加藤
正慈 大久保
吉郎 高尾
山中　　之史
孝広 内
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Kubota Corp
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Description

本発明は、エンジン駆動力を入力する入力軸と、前記入力軸によって駆動されて前後進に無段変速可能な油圧式無段変速機と、前記入力軸の駆動力と前記油圧式無段変速機の出力とを合成して合成駆動力を出力する遊星伝動部と、走行装置に出力する出力回転体とを設けた農作業機の変速伝動装置に関する。 The present invention includes an input shaft for inputting engine driving force, a hydraulic continuously variable transmission driven by the input shaft and capable of continuously variable forward and backward, the driving force of the input shaft and the hydraulic continuously variable transmission. The present invention relates to a transmission transmission device for an agricultural working machine provided with a planetary transmission unit that synthesizes the output of the machine and outputs a combined driving force, and an output rotating body that outputs to a traveling device.

従来、たとえば特許文献１に記載された変速伝動装置があった。特許文献１に記載されたものでは、エンジンから前後輪に動力伝達する伝動系に、油圧式無段変速装置、遊星歯車機構及び２つの油圧クラッチを設け、２つの油圧クラッチの一方が接続されることにより、エンジンの出力が油圧式無段変速装置によって変速された後に前後輪に伝達され、２つの油圧クラッチの他方が接続されることにより、油圧式無段変速装置の出力が遊星歯車装置に入力されて遊星歯車装置がエンジンの出力と油圧式無段変速装置の出力とを合成して合成駆動力を出力し、この合成駆動力が前後輪に伝達される。すなわち、２つの油圧クラッチを切換えることにより、ＨＳＴモードの駆動系（ＨＳＴモード伝動）を現出させて前後輪を駆動したり、ＨＭＴモードの駆動系（ＨＭＴモード伝動）を現出させて前後輪を駆動したりできるものである。   Conventionally, for example, there has been a speed change transmission device described in Patent Document 1. In the one described in Patent Document 1, a hydraulic continuously variable transmission, a planetary gear mechanism, and two hydraulic clutches are provided in a transmission system that transmits power from the engine to the front and rear wheels, and one of the two hydraulic clutches is connected. Thus, the output of the engine is transmitted to the front and rear wheels after being shifted by the hydraulic continuously variable transmission, and the other of the two hydraulic clutches is connected, whereby the output of the hydraulic continuously variable transmission is transmitted to the planetary gear unit. When input, the planetary gear unit combines the output of the engine and the output of the hydraulic continuously variable transmission to output a combined driving force, and this combined driving force is transmitted to the front and rear wheels. That is, by switching the two hydraulic clutches, the HST mode drive system (HST mode transmission) appears to drive the front and rear wheels, or the HMT mode drive system (HMT mode transmission) appears to the front and rear wheels. Can be driven.

特開２００１−１０８０６１号公報JP 2001-108061 A

ＨＳＴモード伝動での変速伝動が行なわれる場合、遊星伝動部の遊星ギヤが自転するなど、遊星伝動部にサンギヤと遊星ギヤの相対回転や遊星ギヤとリングギヤの相対回転が発生しても、遊星伝動部から出力回転体への出力が発生しなければよいのであるが、サンギヤと遊星ギヤの相対回転や遊星ギヤとリングギヤの相対回転が発生すると、その相対回転による動力ロスが発生する。   Even if the planetary gear rotates relative to the planetary gear such as the sun gear and the planetary gear, or the planetary gear and the ring gear rotate relative to each other, such as when the HST mode transmission is changed, the planetary gear rotates. However, if relative rotation between the sun gear and the planetary gear or relative rotation between the planetary gear and the ring gear occurs, a power loss due to the relative rotation occurs.

本発明の目的は、ＨＭＴモード伝動によってもＨＳＴモード伝動によっても走行装置に伝動できるものでありながら、ＨＳＴモード伝動での動力ロスを抑制できる農作業機の変速伝動装置を提供することにある。 An object of the present invention is to provide a speed change transmission device for an agricultural machine capable of suppressing power loss in HST mode transmission while being capable of being transmitted to a traveling device by either HMT mode transmission or HST mode transmission.

本第１発明は、エンジン駆動力を入力する入力軸と、前記入力軸によって駆動されて前後進に無段変速可能な油圧式無段変速機と、前記入力軸の駆動力と前記油圧式無段変速機の出力とを合成して合成駆動力を出力する遊星伝動部と、走行装置に出力する出力回転体とを設けた農作業機の変速伝動装置において、
前記入力軸の駆動力と前記油圧式無段変速機の出力とが前記遊星伝動部によって合成され、前記遊星伝動部による合成駆動力が前記出力回転体に伝達されるＨＭＴモード伝動を現出するように、前記遊星伝動部を前記入力軸と前記油圧式無段変速機のモータ軸と前記出力回転体とに連動させる合成伝動状態と、
前記油圧式無段変速機の出力が単独で前記出力回転体に伝達されるＨＳＴモード伝動を現出するように、かつ、ＨＳＴモード伝動を現出する状態で、前記遊星伝動部を構成するサンギヤと遊星ギヤとリングギヤを前記油圧式無段変速機のモータ軸と一体回転させるように、前記遊星伝動部の前記入力軸に対する連動を絶ちながら前記遊星伝動部と前記油圧式無段変速機のモータ軸を連動させ、かつ前記油圧式無段変速機のモータ軸と前記出力回転体を連動させた単独伝動状態とに切換え操作自在な伝動切換えクラッチ機構を設けてあり、
前進の高速側における変速域において、前記合成伝動状態となり、前進の低速側における変速域及び後進の変速域において、前記単独伝動状態となるように構成されている。 The first aspect of the invention includes an input shaft for inputting engine driving force, a hydraulic continuously variable transmission that is driven by the input shaft and is capable of continuously variable forward and backward, and the driving force of the input shaft and the hydraulic In a transmission device for a farming machine provided with a planetary transmission unit that combines the output of a step transmission and outputs a combined driving force, and an output rotating body that outputs to a traveling device,
The driving force of the input shaft and the output of the hydraulic continuously variable transmission are combined by the planetary transmission unit, and the combined driving force by the planetary transmission unit is transmitted to the output rotating body to produce an HMT mode transmission. Thus, a combined transmission state in which the planetary transmission unit is interlocked with the input shaft, the motor shaft of the hydraulic continuously variable transmission, and the output rotating body,
A sun gear that constitutes the planetary transmission unit in such a manner that an HST mode transmission in which an output of the hydraulic continuously variable transmission is independently transmitted to the output rotating body appears, and an HST mode transmission appears. And the planetary transmission section and the motor of the hydraulic continuously variable transmission while the planetary transmission section is not linked to the input shaft so that the planetary gear and the ring gear rotate together with the motor shaft of the hydraulic continuously variable transmission. by linking the shaft, and Ri Oh provided the hydraulic CVT single transmission state and freely switching operation of transmission switching clutch mechanism motor shaft by interlocking the output rotary member,
In the shift range in the high-speed side of the forward, becomes the synthetic transmission state, in the transmission region and the reverse shift range in the low-speed side of the forward, that is configured to be the single transmission state.

本第１発明の構成によると、伝動切換えクラッチ機構が合成伝動状態に切り換え操作されると、伝動切換えクラッチ機構は、遊星伝動部を入力軸と油圧無段変速機のモータ軸と出力回転体とに連動させ、入力軸によって入力されるエンジン駆動力と油圧無段変速機の出力とが遊星伝動部によって合成され、遊星伝動部によって出力される合成駆動力が出力回転体に伝達されて出力回転体から走行装置に出力されるＨＭＴモード伝動を現出させる。伝動切換えクラッチ機構が単独伝動状態に切り換え操作されると、伝動切換えクラッチ機構は油圧式無段変速機のモータ軸と出力回転体を連動させ、入力軸によって入力されるエンジン駆動力が油圧式無段変速機によって変速され、油圧式無段変速によって出力される変速駆動力が出力回転体に伝達されて出力回転体から走行装置に出力されるＨＳＴモード伝動を現出させる。伝動切換えクラッチ機構は、ＨＳＴモード伝動を現出する状態では、遊星伝動部の入力軸に対する連動を絶ちながら遊星伝動部と油圧式無段変速機のモータ軸とを連動させて遊星伝動部のサンギヤと遊星ギヤとリングギヤを油圧無段変速機のモータ軸と一体回転させるから、遊星伝動部のサンギヤと遊星ギヤの相対回転及び遊星ギヤとリングギヤの相対回転が発生しない。   According to the configuration of the first aspect of the present invention, when the transmission switching clutch mechanism is switched to the combined transmission state, the transmission switching clutch mechanism includes the planetary transmission unit as the input shaft, the motor shaft of the hydraulic continuously variable transmission, the output rotating body, The engine driving force input by the input shaft and the output of the hydraulic continuously variable transmission are combined by the planetary transmission unit, and the combined driving force output by the planetary transmission unit is transmitted to the output rotating body for output rotation. The HMT mode transmission output from the body to the traveling device appears. When the transmission switching clutch mechanism is switched to the single transmission state, the transmission switching clutch mechanism interlocks the motor shaft of the hydraulic continuously variable transmission with the output rotating body, and the engine driving force input by the input shaft is hydraulic. The speed change driving force that is shifted by the step transmission and output by the hydraulic stepless transmission is transmitted to the output rotating body, and the HST mode transmission that is output from the output rotating body to the traveling device appears. In the state where the HST mode transmission appears, the transmission switching clutch mechanism is configured such that the planetary transmission unit and the motor shaft of the hydraulic continuously variable transmission are interlocked while the planetary transmission unit is disconnected from the input shaft. Since the planetary gear and the ring gear are rotated together with the motor shaft of the hydraulic continuously variable transmission, the relative rotation between the sun gear and the planetary gear and the relative rotation between the planetary gear and the ring gear do not occur.

従って、高速出力の場合、ＨＭＴモード伝動を現出させて、遊星伝動部による合成駆動力によって走行装置を駆動できるとともに油圧式無段変速機の変速操作によって走行速度を変速することができ、低速出力の場合、ＨＳＴモード伝動を現出させて、油圧式無段変速機による出力によって走行装置を駆動できるとともに油圧式無段変速機の変速操作によって走行速度を変速することができるものでありながら、ＨＳＴモード伝動の場合、遊星伝動部にサンギヤ、遊星ギヤ及びリングギヤの相対回転が発生する場合に生じる動力ロスの発生を回避して、走行装置を効率よく駆動できる。   Therefore, in the case of high-speed output, the HMT mode transmission can be made to appear and the traveling device can be driven by the combined driving force by the planetary transmission unit, and the traveling speed can be changed by the speed change operation of the hydraulic continuously variable transmission. In the case of the output, the HST mode transmission is made to appear, the travel device can be driven by the output from the hydraulic continuously variable transmission, and the travel speed can be changed by the speed change operation of the hydraulic continuously variable transmission. In the case of the HST mode transmission, it is possible to efficiently drive the traveling device by avoiding the generation of power loss that occurs when the sun gear, the planet gear, and the ring gear rotate relative to the planetary transmission unit.

本第２発明は、前記遊星伝動部のサンギヤと前記油圧式無段変速機のモータ軸とを一体回転自在に連動するよう構成して、
前記遊星伝動部のキャリヤを前記入力軸に対する連動入り状態と連動切り状態に切換える入力側クラッチ機構を備えて、
前記油圧式無段変速機のモータ軸の前記出力回転体に対する連動を絶ちながら前記遊星伝動部のリングギヤと前記出力回転体を一体回転自在に連動させる第１伝動状態と、前記油圧式無段変速機のモータ軸を前記遊星伝動部のリングギヤ及び前記出力回転体に一体回転自在に連動させる第２伝動状態とを択一的に現出する出力側クラッチ機構を備えて、前記伝動切換えクラッチ機構を構成してある。 In the second aspect of the invention, the sun gear of the planetary transmission unit and the motor shaft of the hydraulic continuously variable transmission are configured to be interlocked so as to be integrally rotatable,
An input-side clutch mechanism that switches the carrier of the planetary transmission unit between an interlocking state and an interlocking off state with respect to the input shaft;
A first transmission state in which the ring gear of the planetary transmission unit and the output rotating body are interlocked so as to be integrally rotatable while the interlocking of the motor shaft of the hydraulic continuously variable transmission with the output rotating body is interrupted; and the hydraulic continuously variable transmission An output-side clutch mechanism that alternatively displays a second transmission state in which the motor shaft of the machine is linked to the ring gear of the planetary transmission unit and the output rotating body so as to be integrally rotatable, and the transmission switching clutch mechanism It is configured.

本第２発明の構成によると、入力側クラッチ機構によって遊星伝動部のキャリヤを入力軸に対する連動入り状態に切り換えることにより、出力側クラッチ機構を第１伝動状態に切り換えると、出力側クラッチ機構が油圧式無段変速機のモータ軸の出力回転体に対する連動を絶ちながら遊星伝動部のリングギヤと出力回転体とを一体回転自在に連動されることにより、ＨＭＴモード伝動が現出される。入力側クラッチ機構によって遊星伝動部のキャリヤを入力軸に対する連動切り状態に切り換えることにより、出力側クラッチ機構を第２伝動状態に切り換えると、出力側クラッチ機構が油圧式無段変速機のモータ軸を遊星伝動部のリングギヤ及び出力回転体に一体回転自在に連動させることにより、ＨＳＴモード伝動が現出され、かつ遊星伝動部のサンギヤ、遊星ギヤ及びリングギヤがモータ軸と一体回転する。   According to the configuration of the second aspect of the invention, when the output side clutch mechanism is switched to the first transmission state by switching the carrier of the planetary transmission portion to the interlocked state with respect to the input shaft by the input side clutch mechanism, the output side clutch mechanism is hydraulically operated. The HMT mode transmission is realized by interlocking the ring gear of the planetary transmission unit and the output rotating body so as to be integrally rotatable while disconnecting the motor shaft of the type continuously variable transmission from the output rotating body. When the output side clutch mechanism is switched to the second transmission state by switching the carrier of the planetary transmission unit to the interlocking cut state with respect to the input shaft by the input side clutch mechanism, the output side clutch mechanism causes the motor shaft of the hydraulic continuously variable transmission to move. By interlocking with the ring gear and the output rotator of the planetary transmission unit so as to be integrally rotatable, the HST mode transmission appears, and the sun gear, planetary gear and ring gear of the planetary transmission unit rotate together with the motor shaft.

従って、ＨＭＴモード伝動によってもＨＳＴモード伝動によって走行装置を駆動できるとともにＨＳＴモード伝動での駆動を効率よくできる変速伝動装置を、遊星伝動部の入力側に入力側クラッチ機構を設け、遊星伝動部の出力側に出力側クラッチ機構を設けるだけで構造簡単に得ることができる。   Therefore, a speed change transmission device that can drive the traveling device by HST mode transmission and efficiently drive by HST mode transmission is provided with an input side clutch mechanism on the input side of the planetary transmission unit, and the planetary transmission unit The structure can be obtained simply by providing the output side clutch mechanism on the output side.

本第３発明は、前記出力側クラッチ機構を、前記遊星伝動部のリングギヤと前記出力回転体とを連動状態に維持しながら、前記遊星伝動部のサンギヤと前記出力回転体とを連動入り状態と連動切り状態に切換えるように構成してある。   In the third aspect of the present invention, the output side clutch mechanism maintains the ring gear of the planetary transmission unit and the output rotator in an interlocked state, and the sun gear of the planetary transmission unit and the output rotator are in an interlocked state. It is configured to switch to the interlocking cut-off state.

本第３発明の構成によると、サンギヤと出力回転体を連動入り状態と連動切り状態に切換えるだけの構造簡単なクラッチ機構に出力側クラッチ機構を構成することにより、ＨＭＴモード伝動と、サンギヤ、遊星ギヤ及びリングギヤがモータ軸と一体回転するＨＳＴモード伝動とに切換えることができる。   According to the configuration of the third aspect of the present invention, the output side clutch mechanism is configured as a simple clutch mechanism that only switches the sun gear and the output rotating body between the interlocked state and the interlocked disengaged state. It is possible to switch to HST mode transmission in which the gear and ring gear rotate together with the motor shaft.

従って、ＨＳＴモード伝動においてサンギヤ、遊星ギヤ及びリングギヤがモータ軸と一体回転する変速伝動装置を出力側クラッチ機構の面から構造簡単に得ることができる。   Therefore, a transmission transmission device in which the sun gear, the planetary gear, and the ring gear rotate integrally with the motor shaft in the HST mode transmission can be easily obtained from the surface of the output side clutch mechanism.

コンバインの全体を示す側面図である。It is a side view which shows the whole combine. 伝動構造を示す概略正面図である。It is a schematic front view which shows a transmission structure. ＨＭＴモード伝動での変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the speed change transmission apparatus in HMT mode transmission. ＨＳＴモード伝動での変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the speed change transmission apparatus in HST mode transmission. 入力側クラッチ機構及び出力側クラッチ機構の操作状態と、伝動切換えクラッチ機構の操作状態と、変速伝動装置の伝動形態との関係を示す説明図である。It is explanatory drawing which shows the relationship between the operation state of an input side clutch mechanism and an output side clutch mechanism, the operation state of a transmission switching clutch mechanism, and the transmission form of a transmission gearbox. 油圧式無段変速機の変速状態と変速伝動装置の出力速度との関係を示す説明図である。It is explanatory drawing which shows the relationship between the speed change state of a hydraulic continuously variable transmission, and the output speed of a speed change transmission apparatus. 変速操作装置を示すブロック図である。It is a block diagram which shows a speed change operation apparatus. 第１の別実施構造を備えた変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the speed change transmission apparatus provided with the 1st another implementation structure. 第２の別実施構造を備えた変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the speed change transmission apparatus provided with the 2nd another implementation structure. 第３の別実施構造を備えた変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the speed change transmission apparatus provided with the 3rd another implementation structure. 第４の別実施構造を備えた変速伝動装置を示す縦断正面図である。It is a vertical front view which shows the transmission gear mechanism provided with the 4th another implementation structure.

以下、図面に基づいて、本発明に係る変速伝動装置をコンバインに装備した場合について説明する。
図１に示すように、コンバインは、左右一対のクローラ式の走行装置１，１によって自走するように構成され、かつ乗用型の運転部２を装備された走行機体と、走行機体の機体フレーム３の前部に連結された刈取り部４と、機体フレーム３の後部側に刈取り部４の後方に配置して設けられた脱穀装置５と、機体フレーム３の後部側に脱穀装置５の横側方に配置して設けられた穀粒タンク６とを備えて構成してあり、稲、麦などの収穫作業を行う。 Hereinafter, based on the drawings, a description will be given of a case in which a transmission according to the present invention is installed in a combine.
As shown in FIG. 1, a combine is configured to be self-propelled by a pair of left and right crawler type traveling devices 1, 1, and is equipped with a riding type driving unit 2, and a body frame of the traveling body 3, a cutting part 4 connected to the front part of the machine frame 3, a threshing device 5 provided behind the cutting part 4 on the rear side of the machine body frame 3, and a lateral side of the threshing apparatus 5 on the rear side of the machine body frame 3. And a grain tank 6 arranged and provided on the side, and harvesting rice, wheat and the like.

すなわち、刈取り部４は、機体フレーム３の前部から前方向きに上下揺動自在に延出する刈取り部フレーム４ａを備え、この刈取り部フレーム４ａが昇降シリンダ７によって揺動操作されることにより、刈取り部４の前端部に設けられた分草具４ｂが地面近くに下降した下降作業位置と、分草具４ｂが地面から高く上昇した上昇非作業位置とに昇降する。刈取り部４を下降作業位置に下降させて走行機体を走行させると、刈取り部４は、分草具４ｂによって刈取対象の植立穀稈を引起し経路に導入し、引起し経路に導入した植立穀稈を引起し装置４ｃによって引起しながらバリカン型の刈取装置４ｄによって刈取り、刈取り穀稈を供給装置４ｅによって脱穀装置５に供給する。脱穀装置５は、供給装置４ｅからの刈取り穀稈の株元側を脱穀フィードチェーン５ａによって挟持して機体後方向きに搬送し、刈取り穀稈の穂先側を扱室（図示せず）に供給して脱穀処理し、脱穀穀粒を穀粒タンク６に送り込む。   That is, the cutting unit 4 includes a cutting unit frame 4a that extends from the front portion of the body frame 3 so as to be able to swing up and down in the forward direction. The weeding tool 4b provided at the front end of the mowing unit 4 moves up and down to a lowering work position where the weeding tool 4b is lowered near the ground, and a rising non-working position where the weeding tool 4b is raised from the ground. When the mowing unit 4 is lowered to the lowering work position and the traveling machine body is run, the mowing unit 4 causes the planted culm to be harvested by the weeding tool 4b to be introduced into the path, and the planting that has been induced and introduced into the path. While raising the standing cereal and raising it by the device 4c, it is cut by the clipper type reaping device 4d, and the chopped cereal is supplied to the threshing device 5 by the supply device 4e. The threshing device 5 sandwiches the stock side of the harvested cereal meal from the supply device 4e by the threshing feed chain 5a and conveys it toward the rear of the machine body, and supplies the tip side of the harvested cereal meal to the handling room (not shown). The threshing process is performed, and the threshing grain is fed into the grain tank 6.

運転部２に備えられた運転座席２ａの下方にエンジン８を設け、エンジン８が出力する駆動力を、機体フレーム３の前端部に設けたミッションケース１１を備えた伝動構造１０によって左右一対の走行装置１，１に伝達するように構成してある。   The engine 8 is provided below the driver seat 2 a provided in the driving unit 2, and the driving force output from the engine 8 is driven by a pair of left and right traveling by the transmission structure 10 including the transmission case 11 provided at the front end of the body frame 3. It is configured to transmit to the devices 1 and 1.

図２は、伝動構造１０の概略構造を示す正面図である。この図に示すように、伝動構造１０は、エンジン８の出力軸８ａからのエンジン駆動力を、伝動ベルト１２ａが備えられた伝動機構１２を介してミッションケース１１の上端部の横側に設けられた変速伝動装置２０に入力し、この変速伝動装置２０の出力を、ミッションケース１１に内装された走行ミッション１３に入力して走行ミッション１３が備える左右一対の操向クラッチ機構１４，１４の左側の操向クラッチ機構１４から左側の走行装置１の駆動軸１ａに伝達し、右側の操向クラッチ機構１４から右側の走行装置１の駆動軸１ａに伝達する。   FIG. 2 is a front view showing a schematic structure of the transmission structure 10. As shown in this figure, the transmission structure 10 is provided with the engine driving force from the output shaft 8a of the engine 8 on the lateral side of the upper end portion of the transmission case 11 via the transmission mechanism 12 provided with the transmission belt 12a. Input to the transmission transmission device 20 and the output of the transmission transmission device 20 is input to the traveling mission 13 housed in the mission case 11 to the left of the pair of left and right steering clutch mechanisms 14, 14 provided in the traveling mission 13. The power is transmitted from the steering clutch mechanism 14 to the drive shaft 1a of the left traveling device 1, and is transmitted from the right steering clutch mechanism 14 to the drive shaft 1a of the right traveling device 1.

伝動構造１０は、ミッションケース１１に内装された刈取りミッション１５を備え、変速伝動装置２０の出力を、刈取りミッション１５に入力して刈取り出力軸１６から刈取り部４の駆動軸４ｆに伝達する。   The transmission structure 10 includes a cutting mission 15 incorporated in the mission case 11, and the output of the transmission 20 is input to the cutting mission 15 and transmitted from the cutting output shaft 16 to the drive shaft 4 f of the cutting unit 4.

変速伝動装置２０について説明する。
図３，４に示すように、変速伝動装置２０は、ミッションケース１１の上端側に横側部が連結される変速ケース２１を備えた遊星変速部２０Ａと、変速ケース２１のミッションケース１１に連結する側とは反対側の横側部にケーシング３１が連結された油圧式無段変速機３０とを備えて構成してある。 The transmission 20 will be described.
As shown in FIGS. 3 and 4, the transmission 20 is connected to the planetary transmission unit 20 </ b> A including a transmission case 21 having a lateral side connected to the upper end side of the transmission case 11, and to the transmission case 11 of the transmission case 21. And a hydraulic continuously variable transmission 30 having a casing 31 connected to the lateral side opposite to the side to be operated.

変速ケース２１は、遊星伝動部４０及び伝動機構５０を収容する主ケース部２１ａと、入力軸２２及び伝動軸２３と油圧式無段変速機３０の連結部を収容し、かつ変速ケース２１とケーシング３１のポートブロック３４を連結する連結ケース部２１ｂとを備えて構成してある。変速ケース２１は、主ケース部２１ａの出力回転体２４が位置する下部側面の横外側に膨出形成された膨出部分２１ｃでミッションケース１１に連結される。連結ケース部２１ｂの走行機体上下方向での大きさが主ケース部２１ａの走行機体上下方向での大きさよりも小になっている。主ケース部２１ａを、機体前後方向視での縦断面形状が縦長形状となるように形成し、ケーシング３１を、機体前後方向視での縦断面形状が縦長形状となるように形成し、遊星変速部２０Ａと油圧式無段変速機３０が機体横方向に並びながら、変速伝動装置２０全体としての機体横方向幅が小となり、変速伝動装置２０は、横外側に突出しないように走行機体の左右方向ではコンパクトな状態でミッションケース１１の横側部に連結されている。さらに、ケーシング３１の下部側面には下端側ほど機体内側に傾斜する傾斜面３１Ａが形成され、この傾斜面３１Ａにモータ軸３３ａのベアリングを支持する膨出部３１Ｂが形成されて、変速伝動装置２０の更なるコンパクト化が図られている。また、ケーシング３１の上面には上向きにオイルフィルタ２０Ｆが配置され、オイルフィルタ２０Ｆの横外側への突出を回避して更なるコンパクトが図られている。   The transmission case 21 houses a main case portion 21a that accommodates the planetary transmission unit 40 and the transmission mechanism 50, a coupling portion between the input shaft 22, the transmission shaft 23, and the hydraulic continuously variable transmission 30, and the transmission case 21 and the casing. The connection case part 21b which connects the 31 port blocks 34 is provided. The transmission case 21 is connected to the transmission case 11 at a bulging portion 21c that is bulged outwardly on the lateral side of the lower side surface where the output rotating body 24 of the main case portion 21a is located. The size of the connecting case portion 21b in the vertical direction of the traveling machine body is smaller than the size of the main case portion 21a in the vertical direction of the traveling machine body. The main case portion 21a is formed so that the longitudinal cross-sectional shape when viewed in the longitudinal direction of the fuselage is a longitudinally long shape, and the casing 31 is formed such that the longitudinal sectional shape when viewed in the longitudinal direction of the aircraft is longitudinally elongated. While the portion 20A and the hydraulic continuously variable transmission 30 are arranged in the lateral direction of the vehicle body, the lateral width of the vehicle body as a whole of the transmission transmission device 20 becomes small, and the transmission transmission device 20 does not protrude laterally outward so The direction is connected to the lateral side of the mission case 11 in a compact state. Further, the lower side surface of the casing 31 is formed with an inclined surface 31A inclined toward the inner side of the machine body at the lower end side, and a bulging portion 31B for supporting the bearing of the motor shaft 33a is formed on the inclined surface 31A. Is being made more compact. In addition, an oil filter 20F is disposed on the upper surface of the casing 31 so as to avoid protrusion of the oil filter 20F to the lateral outer side, thereby achieving further compactness.

遊星変速部２０Ａは、変速ケース２１の上端側に回転自在に支持された機体横向きの入力軸２２と、変速ケース２１の下端側に入力軸２２と平行又はほぼ平行に回転自在に支持された伝動軸２３及び回転軸型の出力回転体２４と、伝動軸２３に支持された遊星伝動部４０と、入力軸２２と遊星伝動部４０のキャリヤ４１とに亘って設けた伝動機構５０とを備えている。   The planetary transmission unit 20A includes a laterally-facing input shaft 22 that is rotatably supported on the upper end side of the transmission case 21, and a transmission that is rotatably supported in parallel or substantially parallel to the input shaft 22 on the lower end side of the transmission case 21. A shaft 23 and a rotary shaft type output rotor 24; a planetary transmission unit 40 supported by the transmission shaft 23; and a transmission mechanism 50 provided across the input shaft 22 and the carrier 41 of the planetary transmission unit 40. Yes.

入力軸２２は、油圧式無段変速機３０のポンプ軸３２ａに対して同軸芯状に並ぶよう配置されている。入力軸２２は、変速ケース２１から横外側に突出している側で伝動機構１２を介してエンジン８の出力軸８ａに連結するように構成され、エンジン８に連結される側とは反対側でジョイント２２ａを介して油圧式無段変速機３０のポンプ軸３２ａに一体回転自在に連結されており、伝動機構１２を介してエンジン駆動力を入力し、エンジン駆動力によって駆動されて油圧式無段変速機３０の油圧ポンプ３２を駆動する。   The input shaft 22 is arranged so as to be aligned coaxially with the pump shaft 32 a of the hydraulic continuously variable transmission 30. The input shaft 22 is configured to be coupled to the output shaft 8a of the engine 8 via the transmission mechanism 12 on the side projecting laterally outward from the transmission case 21, and the joint on the opposite side to the side coupled to the engine 8 The hydraulic continuously variable transmission 30a is connected to the pump shaft 32a of the hydraulic continuously variable transmission 30 so as to be freely rotatable. The engine driving force is input via the transmission mechanism 12, and the hydraulic continuously variable transmission is driven by the engine driving force. The hydraulic pump 32 of the machine 30 is driven.

出力回転体２４は、油圧式無段変速機３０に対して入力軸２２のエンジン連結側が位置する側と同じ側に油圧式無段変速機３０のモータ軸３３ａと同軸芯状に並ぶように配置されている。出力回転体２４は、変速ケース２１から横外側に突出している側で走行ミッション１１の入力部に連動するよう構成されており、遊星伝動部４０及び油圧式無段変速機３０からの駆動力を走行ミッション１３を介して左右一対の走行装置１，１に出力する。   The output rotating body 24 is arranged on the same side as the side where the engine connection side of the input shaft 22 is located with respect to the hydraulic continuously variable transmission 30 so as to be aligned coaxially with the motor shaft 33a of the hydraulic continuously variable transmission 30. Has been. The output rotator 24 is configured to be interlocked with the input portion of the traveling mission 11 on the side projecting laterally outward from the speed change case 21, and receives the driving force from the planetary transmission portion 40 and the hydraulic continuously variable transmission 30. Output to the pair of left and right traveling devices 1, 1 via the traveling mission 13.

油圧式無段変速機３０は、ケーシング３１の上端側にポンプ軸３２ａが回転自在に支持されている油圧ポンプ３２と、ケーシング３１の下端側にモータ軸３３ａが回転自在に支持されている油圧モータ３３とを備えて構成してある。油圧ポンプ３２は、可変容量形のアキシャルプランジャポンプによって構成し、油圧モータ３３は、アキシャルプランジャモータによって構成してある。油圧モータ３３は、油圧ポンプ３２によって吐出され、ポートブロック３４の内部に形成された油路を介して供給される圧油によって駆動される。油圧式無段変速機３０には、ポンプ軸３２ａの端部に装備されたチャージポンプ９０によって補充用の作動油が供給される。チャージポンプ９０は、ポンプ軸３２ａに一体回転自在に取り付けられたロータ９０ａ、及びケーシング３１に脱着自在に連結されたポンプケーシング９０ｂを備えている。   The hydraulic continuously variable transmission 30 includes a hydraulic pump 32 in which a pump shaft 32a is rotatably supported on an upper end side of a casing 31, and a hydraulic motor in which a motor shaft 33a is rotatably supported on a lower end side of the casing 31. 33. The hydraulic pump 32 is constituted by a variable displacement axial plunger pump, and the hydraulic motor 33 is constituted by an axial plunger motor. The hydraulic motor 33 is driven by pressure oil that is discharged by the hydraulic pump 32 and supplied through an oil passage formed inside the port block 34. The hydraulic continuously variable transmission 30 is supplied with supplementary hydraulic fluid by a charge pump 90 provided at the end of the pump shaft 32a. The charge pump 90 includes a rotor 90a that is attached to the pump shaft 32a so as to be integrally rotatable, and a pump casing 90b that is detachably connected to the casing 31.

したがって、油圧式無段変速機３０は、油圧ポンプ３２が備える斜板３２ｂの角度変更操作が行なわれることにより、前進伝動状態と後進伝動状態と中立状態とに切り換わる。油圧式無段変速機３０は、前進伝動状態に切換え操作されると、入力軸２２からポンプ軸３２ａに伝達されるエンジン駆動力を前進駆動力に変換してモータ軸３３ａから出力し、後進伝動状態に切換え操作されると、入力軸２２からポンプ軸３２ａに伝達されるエンジン駆動力を後進駆動力に変換してモータ軸３３ａから出力し、前進伝動状態と後進伝動状態のいずれにおいても、エンジン駆動力を無段階に変速して出力する。油圧式無段変速機３０は、中立状態に切換え操作されると、モータ軸３３ａからの出力を停止する。   Therefore, the hydraulic continuously variable transmission 30 is switched to the forward transmission state, the reverse transmission state, and the neutral state by performing an angle changing operation of the swash plate 32b included in the hydraulic pump 32. When the hydraulic continuously variable transmission 30 is operated to switch to the forward transmission state, the engine driving force transmitted from the input shaft 22 to the pump shaft 32a is converted into the forward driving force and output from the motor shaft 33a for reverse transmission. When the operation is switched to the state, the engine driving force transmitted from the input shaft 22 to the pump shaft 32a is converted into the reverse driving force and output from the motor shaft 33a, and the engine is driven in both the forward transmission state and the reverse transmission state. The driving force is steplessly shifted and output. When the hydraulic continuously variable transmission 30 is switched to the neutral state, the output from the motor shaft 33a is stopped.

遊星伝動部４０は、油圧式無段変速機３０に対して入力軸２２のエンジン連結側が位置する側と同じ側に、モータ軸３３ａと出力回転体２４の間に位置する状態で配置されている。遊星伝動部４０は、伝動軸２３に支持されるサンギヤ４２と、サンギヤ４２に噛合う複数個の遊星ギヤ４３と、各遊星ギヤ４３に噛合うリングギヤ４４と、複数個の遊星ギヤ４３を回転自在に支持するキャリヤ４１とを備えている。キャリヤ４１は、遊星ギヤ４３を延出端部で回転自在に支持するアーム部４１ａと、複数本のアーム部４１ａの基端側が連結している筒軸部４１ｂとを備え、筒軸部４１ｂで伝動軸２３にベアリングを介して回転自在に支持されている。   The planetary transmission unit 40 is disposed on the same side as the side where the engine connection side of the input shaft 22 is positioned with respect to the hydraulic continuously variable transmission 30 and is positioned between the motor shaft 33 a and the output rotating body 24. . The planetary transmission unit 40 is configured to freely rotate a sun gear 42 supported by the transmission shaft 23, a plurality of planetary gears 43 that mesh with the sun gear 42, a ring gear 44 that meshes with each planetary gear 43, and a plurality of planetary gears 43. And a carrier 41 to be supported. The carrier 41 includes an arm portion 41a that rotatably supports the planetary gear 43 at the extended end portion, and a cylindrical shaft portion 41b to which the base end sides of the plurality of arm portions 41a are connected. The transmission shaft 23 is rotatably supported via a bearing.

伝動軸２３とモータ軸３３ａとは、ジョイント２３ａを介して一体回転自在に連結し、伝動軸２３とサンギヤ４２とは、スプライン構造を介して一体回転自在に連結しており、サンギヤ４２は、モータ軸３３ａに対して一体回転自在に連動している。   The transmission shaft 23 and the motor shaft 33a are connected so as to be integrally rotatable via a joint 23a, and the transmission shaft 23 and the sun gear 42 are connected so as to be integrally rotatable via a spline structure. The shaft 33a is interlocked with the shaft 33a so as to be integrally rotatable.

リングギヤ４４と出力回転体２４とは、伝動軸２３に対してこれの軸芯方向に並んで相対回転自在に外嵌した環状の遊星側連動体２６及び環状の出力側連動体２７によって一体回転自在に連動している。すなわち、遊星側連動体２６は、遊星側連動体２６の外周部から放射状にかつ一体回転自在に延出する複数本の係合アーム部２６ａを備えている。複数本の係合アーム部２６ａは、リングギヤ４４の複数箇所に係合しており、遊星側連動体２６は、リングギヤ４４に対して一体回転自在に連動している。出力側連動体２７は、遊星側連動体２６に対して係合爪２７ａによって一体回転自在に係合し、出力回転体２４に対してスプライン構造によって一体回転自在に係合しており、遊星側連動体２６と出力回転体２４とを一体回転自在に連結している。遊星側連動体２６は、伝動軸２３にベアリングを介して相対回転自在に支持されている。出力側連動体２７は、変速ケース２１にベアリングを介して回転自在に支持されている。   The ring gear 44 and the output rotating body 24 are integrally rotatable by an annular planetary interlocking body 26 and an annular output side interlocking body 27 that are externally fitted to the transmission shaft 23 so as to be relatively rotatable side by side in the axial direction. It is linked to. That is, the planetary interlocking body 26 includes a plurality of engagement arm portions 26 a that extend radially and integrally from the outer peripheral portion of the planetary interlocking body 26. The plurality of engagement arm portions 26 a are engaged with a plurality of locations of the ring gear 44, and the planetary interlocking body 26 is interlocked with the ring gear 44 so as to be integrally rotatable. The output-side interlocking body 27 is engaged with the planetary-side interlocking body 26 so as to be integrally rotatable with an engaging claw 27a, and is integrally engaged with the output rotating body 24 with a spline structure. The interlocking body 26 and the output rotating body 24 are connected so as to be rotatable together. The planetary interlocking body 26 is supported on the transmission shaft 23 through a bearing so as to be relatively rotatable. The output side interlocking body 27 is rotatably supported by the transmission case 21 via a bearing.

伝動機構５０は、キャリヤ４１の筒軸部４１ｂに一体回転自在に設けられたキャリヤ４１の入力ギヤ４１ｃに噛合う状態で入力軸２２にニードルベアリングを介して相対回転自在に支持された伝動ギヤ５２と、伝動ギヤ５２と入力軸２２に亘って設けた入力側クラッチ機構５５とを備えて構成してある。   The transmission mechanism 50 is a transmission gear 52 that is supported on the input shaft 22 through a needle bearing so as to be relatively rotatable while meshing with an input gear 41c of the carrier 41 that is provided rotatably on the cylindrical shaft portion 41b of the carrier 41. And an input side clutch mechanism 55 provided across the transmission gear 52 and the input shaft 22.

入力側クラッチ機構５５は、入力軸２２に一体回転及び摺動操作自在に支持されたクラッチ体５６と、クラッチ体５６の一端側と伝動ギヤ５２の横側部とに亘って設けたクラッチ機構本体５７とを備えて構成してある。クラッチ体５６は、クラッチ体５６の端部に内嵌された油圧ピストン５８によって摺動操作される。クラッチ機構本体５７は、クラッチ体５６に設けた噛合い爪と伝動ギヤ５２に設けた噛合い爪とが係脱することによって入り状態と切り状態に切り換わるように噛合いクラッチに構成してある。   The input-side clutch mechanism 55 includes a clutch body 56 that is supported on the input shaft 22 so as to be integrally rotatable and slidable, and a clutch mechanism main body provided across one end side of the clutch body 56 and the lateral side portion of the transmission gear 52. 57. The clutch body 56 is slid and operated by a hydraulic piston 58 fitted in the end of the clutch body 56. The clutch mechanism main body 57 is configured as a meshing clutch so that the engagement claw provided on the clutch body 56 and the engagement claw provided on the transmission gear 52 are engaged and disengaged to switch between the on state and the off state. .

入力側クラッチ機構５０は、クラッチ機構本体５７が入り状態に切換え操作されることにより、入力軸２２と伝動ギヤ５２を一体回転自在に連動させるように入り状態に切換え操作され、遊星伝動部４０のキャリヤ４１を入力軸２２に対する連動入り状態に切り換える。   The input-side clutch mechanism 50 is switched to the input state so that the input shaft 22 and the transmission gear 52 are interlocked so as to be integrally rotatable when the clutch mechanism main body 57 is switched to the engaged state. The carrier 41 is switched to the interlocked state with respect to the input shaft 22.

入力側クラッチ機構５０は、クラッチ機構本体５７が切り状態に切換え操作されることにより、入力軸２２と伝動ギヤ５２の連動を絶つように切り状態に切換え操作され、遊星伝動部４０のキャリヤ４１を入力軸２２に対する連動切り状態に切り換える。   The input-side clutch mechanism 50 is switched to the disconnected state so that the input shaft 22 and the transmission gear 52 are disengaged when the clutch mechanism main body 57 is switched to the disconnected state, and the carrier 41 of the planetary transmission unit 40 is moved. Switch to the interlocking cut off state for the input shaft 22.

したがって、遊星伝動部４０は、入力側クラッチ機構５０が入り状態に切換え操作されることにより、入力軸２２のエンジン連結側と無段変速機連結側との間に位置する部位から入力軸２２の駆動力を伝動機構５０を介してキャリヤ４１に入力する。遊星伝動部４０は、入力側クラッチ機構５０が切り状態に切換え操作されることにより、入力軸２２に対する連動を絶たれた状態になる。   Therefore, the planetary transmission unit 40 is switched from the portion located between the engine connecting side and the continuously variable transmission connecting side of the input shaft 22 by switching the input side clutch mechanism 50 to the on state. A driving force is input to the carrier 41 via the transmission mechanism 50. The planetary transmission unit 40 is disconnected from the input shaft 22 when the input side clutch mechanism 50 is switched to the disengaged state.

遊星伝動部４０のサンギヤ４２と遊星側連動体２６とに亘り、伝動軸２３に外嵌されたクラッチ体６１を備えた出力側クラッチ機構６０を設けてある。   An output side clutch mechanism 60 having a clutch body 61 fitted on the transmission shaft 23 is provided across the sun gear 42 of the planetary transmission unit 40 and the planetary side interlocking body 26.

クラッチ体６１は、クラッチ体６１の内周側に形成してある油室に圧油が供給されることにより、入り付勢ばね６２に抗してサンギヤ４２に向けて摺動操作されて切り位置に切り換わり、油室から圧油が排出されることにより、入り付勢ばね６２によって遊星側連動体２６に向けて摺動操作されて入り位置に切り換わる。クラッチ体６１は、入り位置に切り換わると、クラッチ体６１に設けてあるクラッチ爪６１ａと遊星側連動体２６に設けてあるクラッチ爪とが係合して、遊星側連動体２６に対して一体回転自在に連結する。クラッチ体６１は、サンギヤ４２に対して係合爪６１ｂによって一体回転自在に係合した状態を維持しながら摺動操作され、サンギヤ４２に対する係合状態を維持しながら入り位置になる。クラッチ体６１は、切り位置に切り換わると、クラッチ爪６１ａによる遊星側連動体２６に対する係合を解除する。   The clutch body 61 is slidably operated toward the sun gear 42 against the energizing spring 62 when pressure oil is supplied to an oil chamber formed on the inner peripheral side of the clutch body 61, so that the clutch body 61 is in the cut position. When the pressure oil is discharged from the oil chamber, the urging spring 62 is slid toward the planetary interlocking body 26 to switch to the entry position. When the clutch body 61 is switched to the entering position, the clutch pawl 61 a provided on the clutch body 61 and the clutch pawl provided on the planetary interlocking body 26 are engaged with each other, so that the clutch body 61 is integrated with the planetary interlocking body 26. Connect freely. The clutch body 61 is slid while maintaining a state in which the clutch body 61 is engaged with the sun gear 42 by the engaging claws 61b so as to be integrally rotatable. When the clutch body 61 is switched to the disengagement position, the clutch pawl 61a is disengaged from the planetary interlocking body 26.

したがって、出力側クラッチ機構６０は、クラッチ体６１が切り位置に切換え操作されることにより、サンギヤ４２と遊星側連動体２６の連動を絶つことで、モータ軸３３ａの出力回転体２４に対する連動を絶ち、この状態において遊星伝動部４０のリングギヤ４４と出力回転体２４が一体回転自在に連動する第１伝動状態を現出し、遊星伝動部４０の合成駆動力の出力回転体２４からの出力を可能にする。   Therefore, the output-side clutch mechanism 60 disconnects the sun gear 42 and the planetary-side interlocking body 26 from being interlocked by switching the clutch body 61 to the disengagement position, thereby disconnecting the motor shaft 33a from the output rotating body 24. In this state, the first transmission state in which the ring gear 44 of the planetary transmission unit 40 and the output rotator 24 are interlocked so as to be integrally rotatable appears, and the combined driving force of the planetary transmission unit 40 can be output from the output rotator 24. To do.

出力側クラッチ機構６０は、クラッチ体６１が入り位置に切換え操作されることにより、サンギヤ４２と遊星側連動体２６を一体回転自在に連動させることで、モータ軸３３ａを出力回転体２４に一体回転自在に連動させる第２伝動状態を現出し、油圧無段変速機３０による出力の出力回転体２４からの出力を可能し、かつ、サンギヤ４２と伝動軸２３が一体回転自在に連動し、リングギヤ４４と遊星側連動体２６が一体回転自在に連動していることにより、遊星ギヤ４３の自転が発生しないように、サンギヤ４２と遊星ギヤ４３とリングギヤ４４がモータ軸３３ａと一体回転することを可能にする。   The output side clutch mechanism 60 rotates the motor shaft 33a integrally with the output rotating body 24 by interlocking the sun gear 42 and the planetary side interlocking body 26 so that the clutch body 61 is switched to the entering position. The second transmission state to be freely interlocked appears, the output of the output by the hydraulic continuously variable transmission 30 can be output from the output rotating body 24, and the sun gear 42 and the transmission shaft 23 are interlocked so as to be integrally rotatable. And the planetary-side interlocking body 26 are interlocked so as to be rotatable together, so that the sun gear 42, the planetary gear 43, and the ring gear 44 can rotate together with the motor shaft 33a so that the planetary gear 43 does not rotate. To do.

出力側クラッチ機構６０は、遊星伝動部４０のリングギヤ４４と出力回転体２４とを連動状態に維持しながら、遊星伝動部４０のサンギヤ４３と出力回転体２４とを連動入り状態と連動切り状態に切換える。   The output-side clutch mechanism 60 keeps the ring gear 44 of the planetary transmission unit 40 and the output rotating body 24 in an interlocked state, while the sun gear 43 and the output rotating body 24 of the planetary transmission unit 40 are in an interlocked on state and an interlocked off state. Switch.

したがって、遊星伝動部４０は、入力側クラッチ機構５５が入り状態に切換え操作され、出力側クラッチ機構６０が切り状態に切換え操作されることにより、入力軸２２の駆動力を伝動機構５０を介してキャリヤ４１に入力し、油圧無段変速機３０のモータ軸３３ａからの出力を伝動軸２３を介してサンギヤ４２に入力し、入力軸２２の駆動力と油圧無段変速機３０の出力とを合成して合成駆動力を発生させ、発生させた合成駆動力をリングギヤ４４から遊星側連動体２６及び出力側連動体２７を介して出力回転体２４に出力する。   Therefore, in the planetary transmission unit 40, the input side clutch mechanism 55 is switched to the on state and the output side clutch mechanism 60 is switched to the off state, so that the driving force of the input shaft 22 is transmitted via the transmission mechanism 50. Input to the carrier 41, the output from the motor shaft 33a of the hydraulic continuously variable transmission 30 is input to the sun gear 42 via the transmission shaft 23, and the driving force of the input shaft 22 and the output of the hydraulic continuously variable transmission 30 are combined. Then, a combined driving force is generated, and the generated combined driving force is output from the ring gear 44 to the output rotating body 24 via the planetary side interlocking body 26 and the output side interlocking body 27.

入力側クラッチ機構５５及び出力側クラッチ機構６０を備えて、伝動切換えクラッチ機構７０を構成してある。伝動切換えクラッチ機構７０は、入力側クラッチ機構５５及び出力側クラッキ機構６０が切換え操作されることにより、単独伝動状態と合成伝動状態とに切り換わる。   An input side clutch mechanism 55 and an output side clutch mechanism 60 are provided to constitute a transmission switching clutch mechanism 70. The transmission switching clutch mechanism 70 is switched between the single transmission state and the combined transmission state when the input side clutch mechanism 55 and the output side crack mechanism 60 are switched.

図５は、入力側クラッチ機構５５及び出力側クラッチ機構６０の操作状態と、伝動切換えクラッチ機構７０の操作状態と、変速伝動装置２０の伝動形態との関係を示す説明図である。図５に示す「切」は、入力側クラッチ機構５５及び出力側クラッチ機構６０の切り状態を示し、「入」は、入力側クラッチ機構５５及び出力側クラッチ機構６０の入り状態を示す。この図に示すように、伝動切換えクラッチ機構７０は、入力側クラッチ機構５５が切り状態に切換え操作され、出力側クラッチ機構６０が入り状態に切換え操作されると、単独伝動状態に切り換わり、入力側クラッチ機構５５が入り状態に切換え操作され、出力側クラッチ機構６０が切り状態に切換え操作されると、合成伝動状態に切り換わる。   FIG. 5 is an explanatory diagram showing the relationship between the operation state of the input side clutch mechanism 55 and the output side clutch mechanism 60, the operation state of the transmission switching clutch mechanism 70, and the transmission mode of the speed change transmission device 20. “OFF” shown in FIG. 5 indicates the disengaged state of the input side clutch mechanism 55 and the output side clutch mechanism 60, and “ON” indicates the engaged state of the input side clutch mechanism 55 and the output side clutch mechanism 60. As shown in this figure, the transmission switching clutch mechanism 70 is switched to the single transmission state when the input side clutch mechanism 55 is switched to the disengaged state and the output side clutch mechanism 60 is switched to the on state. When the side clutch mechanism 55 is switched to the engaged state and the output side clutch mechanism 60 is switched to the disconnected state, the combined transmission state is switched.

図３は、ＨＭＴモード伝動での変速伝動装置２０を示す縦断正面図である。この図に示すように、伝動切換えクラッチ機構７０は、合成伝動状態に切り換わると、入力軸２２の駆動力と油圧式無段変速機３０の出力とが遊星伝動部４０によって合成され、遊星伝動部４０による合成駆動力が出力回転体２４に伝達されるＨＭＴモード伝動を変速伝動装置２０に現出させる。変速伝動装置２０は、ＨＭＴモード伝動の状態になると、入力軸２２に入力されたエンジン駆動力を油圧式無段変速機３０及び遊星伝動部４０の両方によって変速し、変速後の駆動力をリングギヤ４４から出力回転体２４に伝達して出力回転体２４から左右一対の走行装置１，１に伝達する。   FIG. 3 is a longitudinal front view showing the transmission 20 in HMT mode transmission. As shown in this figure, when the transmission switching clutch mechanism 70 is switched to the combined transmission state, the driving force of the input shaft 22 and the output of the hydraulic continuously variable transmission 30 are combined by the planetary transmission unit 40, and the planetary transmission is performed. HMT mode transmission in which the combined driving force by the unit 40 is transmitted to the output rotator 24 is caused to appear on the transmission 20. When in the HMT mode transmission state, the transmission 20 shifts the engine driving force input to the input shaft 22 by both the hydraulic continuously variable transmission 30 and the planetary transmission unit 40, and transmits the driving force after the shift to the ring gear. 44 from the output rotator 24 to the pair of left and right traveling devices 1, 1.

図４は、ＨＳＴモード伝動での変速伝動装置２０を示す縦断正面図である。この図に示すように、伝動切換えクラッチ機構７０は、単独伝動状態に切り換わると、油圧式無段変速機３０の出力が遊星伝動部４０による変速を受けないで単独で出力回転体２４に伝達されるＨＳＴモード伝動を変速伝動装置２０に現出させる。変速伝動装置２０は、ＨＳＴモード伝動の状態になると、エンジン駆動力を、油圧式無段変速機３０と遊星伝動部４０のうちの遊星伝動部４０による変速を行なわず、油圧式無段変速機３０だけによる変速を行い、変速後の駆動力をモータ軸３３ａから伝動軸２３、サンギヤ４２、クラッチ体６１、遊星側連動体２６及び出力側連動体２７を介して出力回転体２４に伝達し、出力回転体２４から左右一対の走行装置１，１に伝達する。   FIG. 4 is a longitudinal front view showing the transmission 20 in the HST mode transmission. As shown in this figure, when the transmission switching clutch mechanism 70 switches to the single transmission state, the output of the hydraulic continuously variable transmission 30 is not transmitted to the planetary transmission unit 40 alone and is transmitted to the output rotating body 24 alone. The HST mode transmission to be performed is made to appear on the transmission 20. When in the HST mode transmission state, the transmission 20 is not shifted by the planetary transmission unit 40 of the hydraulic continuously variable transmission 30 and the planetary transmission unit 40, and the hydraulic continuously variable transmission 30, the driving force after the shift is transmitted from the motor shaft 33a to the output rotating body 24 via the transmission shaft 23, the sun gear 42, the clutch body 61, the planetary side interlocking body 26 and the output side interlocking body 27, This is transmitted from the output rotating body 24 to the pair of left and right traveling devices 1, 1.

伝動切換えクラッチ機構７０は、変速伝動装置２０をＨＳＴモード伝動の状態に操作した場合、入力軸２２から遊星伝動部４０のキャリヤ４１への伝動が絶たれた状態にあり、サンギヤ４２が伝動軸２３を介してモータ軸３３ａに一体回転自在に連動された状態にあり、リングギヤ４４が遊星側連動体２６、クラッチ体６１、サンギヤ４２及び伝動軸２３を介してモータ軸３３ａに一体回転自在に連動された状態にあることから、遊星伝動部４０のサンギヤ４２、遊星ギヤ４３及びリングギヤ４４をモータ軸３３ａと一体回転するよう操作することになり、変速伝動装置２０は、ＨＳＴモード伝動を現出する状態に操作された場合、遊星ギヤ４３の自転を発生させず、すなわちサンギヤ４２と遊星ギヤ４３の相対回転及び遊星ギヤ４３とリングギヤ４４の相対回転を発生させずに、油圧無段変速機３０のモータ軸３３ａの出力を出力回転体２４に伝達する。   The transmission switching clutch mechanism 70 is in a state where transmission from the input shaft 22 to the carrier 41 of the planetary transmission unit 40 is cut off when the transmission 20 is operated in the HST mode transmission state, and the sun gear 42 is in the transmission shaft 23. The ring gear 44 is linked to the motor shaft 33a via the planetary side linkage body 26, the clutch body 61, the sun gear 42 and the transmission shaft 23 so as to be integrally rotatable. Therefore, the sun gear 42, the planetary gear 43 and the ring gear 44 of the planetary transmission unit 40 are operated so as to rotate integrally with the motor shaft 33a, and the transmission 20 is in a state in which the HST mode transmission appears. The planetary gear 43 does not rotate, that is, the relative rotation of the sun gear 42 and the planetary gear 43 and the planetary gear 43 and the Without causing relative rotation of the gear 44, for transmitting the output of the motor shaft 33a of the hydraulic continuously variable transmission 30 to the output rotor 24.

図６は、エンジン８が設定の一定速度の駆動力を出力するようにアクセルセットされた状態における油圧式無段変速機３０の変速状態と変速伝動装置２０の出力回転体２４による出力速度との関係を示す説明図である。図６の横軸は、油圧式無段変速機３０の変速状態を示し、「ｎ」は、油圧式無段変速機３０の中立位置を示し、「−ｍａｘ」は、油圧式無段変速機３０の後進伝動状態での最高速位置を示し、「＋ｍａｘ」は、油圧式無段変速機３０の前進伝動状態での最高速位置を示す。図６の縦軸は、出力回転体２４による出力速度を示す。図６に示す実線Ｒ及び実線ＦＬは、入力側クラッチ機構５５が切り状態に、出力側クラッチ機構６０が入り状態に操作された場合、すなわち変速伝動装置２０がＨＳＴモード伝動の状態に操作された場合における出力速度の変化を示す。図６に示す実線ＦＨは、入力側クラッチ機構５５が入り状態に、出力側クラッチ機構６０が切り状態に操作された場合、すなわち変速伝動装置２０がＨＭＴモード伝動の状態に操作された場合における出力速度の変化を示す。   FIG. 6 shows the state of the shift of the hydraulic continuously variable transmission 30 and the output speed of the output rotating body 24 of the transmission transmission 20 in a state where the engine 8 is accelerator-set so as to output a driving force at a set constant speed. It is explanatory drawing which shows a relationship. The horizontal axis in FIG. 6 indicates the shift state of the hydraulic continuously variable transmission 30, “n” indicates the neutral position of the hydraulic continuously variable transmission 30, and “−max” indicates the hydraulic continuously variable transmission. 30 indicates the highest speed position in the reverse transmission state, and “+ max” indicates the highest speed position in the forward transmission state of the hydraulic continuously variable transmission 30. The vertical axis in FIG. 6 indicates the output speed by the output rotating body 24. The solid line R and the solid line FL shown in FIG. 6 are operated when the input side clutch mechanism 55 is operated in the disengaged state and the output side clutch mechanism 60 is operated in the on state, that is, the transmission transmission 20 is operated in the HST mode transmission state. The change of the output speed in a case is shown. A solid line FH shown in FIG. 6 indicates an output when the input side clutch mechanism 55 is operated in the engaged state and the output side clutch mechanism 60 is operated in the disengaged state, that is, when the transmission transmission 20 is operated in the HMT mode transmission state. Indicates the change in speed.

実線Ｒ及び実線ＦＬで示すように、入力側クラッチ機構５５が切り状態に維持され、出力側クラッチ機構６０が入り状態に維持された状態において、油圧式無段変速機３０が後進伝動状態の最高速位置「−ｍａｘ」に操作されると、出力速度が後進の最高速度「ＲＶＨ」になる。油圧式無段変速機３０が後進伝動状態の最高速位置「−ｍａｘ」から中立位置「ｎ」に向けて変速操作されるに伴い、後進の出力速度が無段階に減速していく。油圧式無段変速機３０が中立位置「ｎ」に至ると、出力速度が零「０」になる。油圧式無段変速機３０が中立位置「ｎ」から前進伝動状態の最高速位置「＋ｍａｘ」に向けて変速操作されるに伴い、前進の出力速度が無段階に増速していく。油圧式無段変速機３０が前進伝動状態の最高速位置「＋ｍａｘ」に至ると、出力速度が前進の中間速度「ＦＶＭ」になる。   As indicated by the solid line R and the solid line FL, when the input side clutch mechanism 55 is maintained in the disengaged state and the output side clutch mechanism 60 is maintained in the on state, the hydraulic continuously variable transmission 30 is in the most reverse transmission state. When the high speed position “−max” is operated, the output speed becomes the reverse maximum speed “RVH”. As the hydraulic continuously variable transmission 30 is shifted from the highest speed position “−max” in the reverse transmission state toward the neutral position “n”, the reverse output speed is continuously reduced. When the hydraulic continuously variable transmission 30 reaches the neutral position “n”, the output speed becomes zero “0”. As the hydraulic continuously variable transmission 30 is shifted from the neutral position “n” toward the highest speed position “+ max” in the forward transmission state, the forward output speed increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the output speed becomes the forward intermediate speed “FVM”.

実線ＦＨで示すように、油圧式無段変速機３０が前進伝動状態の最高速位置「＋ｍａｘ」に至ると、入力側クラッチ機構５５が切り状態から入り状態に切換え制御され、出力側クラッチ機構６０が入り状態から切り状態に切換え制御され、入力側クラッチ機構５５が入り状態に維持され、出力側クラッチ機構６０が切り状態に維持された状態において、油圧式無段変速機３０が前進伝動状態の最高速位置「＋ｍａｘ」から後進伝動状態の最高速位置「−ｍａｘ」に向けて変速操作されるに伴い、前進の出力速度が無段階に増速していく。油圧式無段変速機３０が後進伝動状態の最高速位置「＋ｍａｘ」に至ると、前進の出力速度が最高速度「ＦＶＨ」になる。   As indicated by the solid line FH, when the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the input side clutch mechanism 55 is controlled to be switched from the disengaged state to the on state, and the output side clutch mechanism 60 is controlled. Is switched from the on state to the off state, the input side clutch mechanism 55 is maintained in the on state, and the output side clutch mechanism 60 is maintained in the disengaged state, the hydraulic continuously variable transmission 30 is in the forward transmission state. As a speed change operation is performed from the highest speed position “+ max” to the highest speed position “−max” in the reverse transmission state, the forward output speed increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the reverse transmission state, the forward output speed becomes the maximum speed “FVH”.

図６に示す「Ｎ」は、実線ＦＨを油圧式無段変速機３０の前進側の最高速位置「＋ｍａｘ」を超えて出力回転が零「０」となる点まで延長したときの横軸の値を示す。油圧式無段変速機３０の前進側の最高速位置「＋ｍａｘ」の横軸の値を１とすると、Ｎ＝１．６〜２．２となる。つまり、Ｎ＝１．６〜２．２となるように、油圧式無段変速機３０における油圧ポンプ３２及び油圧モータ３３の容量、並びに遊星伝動部４０の伝動ギヤ比を設定してある。   “N” shown in FIG. 6 indicates the horizontal axis when the solid line FH is extended beyond the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 to a point where the output rotation becomes zero “0”. Indicates the value. When the value of the horizontal axis of the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 is 1, N = 1.6 to 2.2. That is, the capacities of the hydraulic pump 32 and the hydraulic motor 33 in the hydraulic continuously variable transmission 30 and the transmission gear ratio of the planetary transmission unit 40 are set so that N = 1.6 to 2.2.

図７は、変速伝動装置２０を変速操作する変速操作装置７１を示すブロック図である。この図に示すように、変速操作装置７１は、油圧式無段変速機３０の変速操作部３０ａ、入力側クラッチ機構５５及び出力側クラッチ機構６０の操作部５５ａ，６０ａに連係された制御装置７２と、制御装置７２に連係された変速検出センサ７３、エンジン回転数センサ７４、変速機出力回転数センサ７５及び出力回転数センサ７６とを備えている。   FIG. 7 is a block diagram showing a speed change operation device 71 that changes the speed of the speed change transmission device 20. As shown in this figure, the speed change operation device 71 is a control device 72 linked to the speed change operation portion 30a of the hydraulic continuously variable transmission 30, the input side clutch mechanism 55, and the operation portions 55a and 60a of the output side clutch mechanism 60. And a shift detection sensor 73, an engine speed sensor 74, a transmission output speed sensor 75, and an output speed sensor 76 linked to the control device 72.

変速操作部３０ａは、油圧式無断変速機３０における油圧ポンプ３２の斜板３２ｂの角度変更操作を行なう電動アクチュエータ又は油圧アクチュエータによって構成してある。入力側クラッチ機構５５の操作部５５ａは、入力軸２２の内部に形成された操作油路を介して油圧ピストン５８に接続された操作弁によって構成してあり、油圧ピストン５８を操作してクラッチ体５６を摺動操作することにより、入力側クラッチ機構５５を切り換え操作する。出力側クラッチ機構６０の操作部６０ａは、伝動軸２３の内部に形成された操作油路を介してクラッチ体６１の油室に接続された操作弁によって構成してあり、クラッチ体６１の油室に対する操作油の供給及び排出を行なうことにより、クラッチ体６１を摺動操作して出力側クラッチ機構６０を切り換え操作する。   The shift operation unit 30a is configured by an electric actuator or a hydraulic actuator that performs an angle changing operation of the swash plate 32b of the hydraulic pump 32 in the hydraulic continuously variable transmission 30. The operation portion 55a of the input side clutch mechanism 55 is constituted by an operation valve connected to the hydraulic piston 58 via an operation oil passage formed inside the input shaft 22, and the clutch body is operated by operating the hydraulic piston 58. By sliding operation 56, the input side clutch mechanism 55 is switched. The operation portion 60 a of the output side clutch mechanism 60 is configured by an operation valve connected to the oil chamber of the clutch body 61 via an operation oil passage formed inside the transmission shaft 23. By supplying and discharging the operating oil, the clutch body 61 is slid and the output side clutch mechanism 60 is switched.

変速検出センサ７３は、変速レバー７７の操作位置を検出し、この検出結果を制御装置７２に出力する。エンジン回転数センサ７４は、エンジン８の回転数を検出し、この検出結果を制御装置７２に出力する。変速機出力回転数センサ７５は、油圧式無段変速機３０の出力回転数を検出し、この検出結果を制御装置７２に出力する。出力回転数センサ７６は、変速伝動装置２０の出力回転数を検出し、この検出結果を制御装置７２に出力する。   The shift detection sensor 73 detects the operation position of the shift lever 77 and outputs the detection result to the control device 72. The engine speed sensor 74 detects the speed of the engine 8 and outputs the detection result to the control device 72. The transmission output rotation speed sensor 75 detects the output rotation speed of the hydraulic continuously variable transmission 30 and outputs the detection result to the control device 72. The output speed sensor 76 detects the output speed of the transmission 20 and outputs the detection result to the controller 72.

制御装置７２は、マイクロコンピュータを利用して構成してあり、変速制御手段７８を備えている。変速制御手段７８は、変速検出センサ７３及び変速機出力回転数センサ７５による検出情報を基に、油圧式無段変速機３０の変速状態が変速レバー７７の操作位置に対応したものになるように、変速操作部３０ａを操作して油圧式無段変速機３０を変速制御する。   The control device 72 is configured using a microcomputer and includes a shift control means 78. The shift control means 78 is configured so that the shift state of the hydraulic continuously variable transmission 30 corresponds to the operation position of the shift lever 77 based on detection information from the shift detection sensor 73 and the transmission output rotation speed sensor 75. Then, the shift control unit 30a is operated to control the shift of the hydraulic continuously variable transmission 30.

変速制御手段７８は、油圧式無段変速機３０を変速制御するに加え、エンジン回転数センサ７４による検出情報を基に、アクセルセットされたエンジン８の回転数を検出し、この検出結果、変速検出センサ７３、変速機出力回転数センサ７５及び出力回転数センサ７６による検出情報を基に、図５，６に示す如く変速伝動装置２０がＨＳＴモード伝動及びＨＭＴモード伝動を現出して伝動するように、操作部５５ａ及び操作部６０ａを操作して入力側クラッチ機構５５及び出力側クラッチ機構６０を所定のタイミングで切り換え制御する。   The shift control means 78 detects the rotational speed of the accelerator-set engine 8 on the basis of information detected by the engine rotational speed sensor 74 in addition to controlling the shift of the hydraulic continuously variable transmission 30, Based on the detection information by the detection sensor 73, the transmission output speed sensor 75, and the output speed sensor 76, as shown in FIGS. 5 and 6, the speed change transmission device 20 appears to transmit the HST mode transmission and the HMT mode transmission. Further, the input side clutch mechanism 55 and the output side clutch mechanism 60 are controlled to be switched at a predetermined timing by operating the operation unit 55a and the operation unit 60a.

〔別実施構造〕
図８は、第１の別実施構造を備えた変速伝動装置２０を示す縦断正面図である。この図に示すように、第１の別実施構造を備えた変速伝動装置２０では、油圧式無段変速機３０を、可変容量型の油圧ポンプ３２と可変容量型の油圧モータ３３を備えて構成してある。 [Another implementation structure]
FIG. 8 is a longitudinal front view showing the transmission device 20 having the first different embodiment structure. As shown in the figure, in the transmission 20 having the first different implementation structure, the hydraulic continuously variable transmission 30 includes a variable displacement hydraulic pump 32 and a variable displacement hydraulic motor 33. It is.

図９は、第２の別実施構造を備えた変速伝動装置２０を示す縦断正面図である。この図に示すように、第２の別実施構造を備えた変速伝動装置２０では、出力側クラッチ機構６０を、伝動軸２３に一体回転自在に設けた支持体６３と遊星側連動体２６に設けたクラッチボディ部とに亘って設けた多板式の摩擦クラッチ部６４を備えて、摩擦式のクラッチ機構に構成してある。この出力側クラッチ機構６０は、摩擦クラッチ部６４がサンギヤ４２に支持された油圧ピストン６５によって入り状態と切り状態に切換え操作されることにより、モータ軸３３ａと出力回転体２４を連動入り状態と連動切る状態に切換え操作する。   FIG. 9 is a longitudinal front view showing the transmission 20 having the second alternative structure. As shown in this figure, in the transmission 20 having the second alternative structure, the output-side clutch mechanism 60 is provided on the support body 63 and the planetary-side interlocking body 26 that are provided to rotate integrally with the transmission shaft 23. A multi-plate friction clutch portion 64 provided over the clutch body portion is provided to constitute a friction clutch mechanism. In the output side clutch mechanism 60, when the friction clutch portion 64 is switched between the on state and the off state by the hydraulic piston 65 supported by the sun gear 42, the motor shaft 33a and the output rotating body 24 are interlocked with the interlocked on state. Switch to the cut-off state.

図１０は、第３の別実施構造を備えた変速伝動装置２０を示す縦断正面図である。この図に示すように、第３の別実施構造を備えた変速伝動装置２０では、入力側クラッチ機構５５を、入力側連動ギヤ５２に一体回転自在に設けた支持部と入力軸２２に一体回転自在に設けたクラッチボディ部５９ａとに亘って設けた多板式の摩擦クラッチ部５９を備えて、摩擦式のクラッチ機構に構成してある。この入力側クラッチ機構５５は、摩擦クラッチ部５９がクラッチボディ部５９ａに内装された油圧ピストン５９ｂによって入り状態と切り状態に切換え操作されることにより、入力軸２２と入力側連動ギヤ５２を連動入り状態と連動切る状態に切換え操作する。   FIG. 10 is a longitudinal sectional front view showing the transmission device 20 having the third alternative embodiment structure. As shown in this figure, in the transmission 20 having the third alternative embodiment structure, the input side clutch mechanism 55 is integrally rotated with the input shaft 22 and the support portion provided so as to be integrally rotatable with the input side interlocking gear 52. A multi-plate friction clutch portion 59 provided over a freely provided clutch body portion 59a is provided to constitute a friction clutch mechanism. In this input side clutch mechanism 55, the input clutch 22 and the input side interlocking gear 52 are interlocked when the friction clutch part 59 is switched between the on state and the off state by a hydraulic piston 59b built in the clutch body part 59a. Switch to the state that is linked to the state.

図１１は、第４の別実施構造を備えた変速伝動装置２０を示す縦断正面図である。この図に示すように、第４の別実施構造を備えた変速伝動装置２０では、出力側クラッチ機構６０を、伝動側２３に一体回転自在に設けた支持部６６と出力側連動体２７に一体回転自在に連結されたクラッチボディ６７ａとに亘って設けた多板式の摩擦クラッチ部６７を備えて、摩擦式のクラッチ機構に構成してある。この出力側クラッチ機構６０は、摩擦クラッチ部６７がクラッチボディ６７ａに内装された油圧ピストン６７ｂによって入り状態と切り状態に切換え操作されることにより、モータ軸３３ａと出力回転体２４を連動入り状態と連動切り状態に切換え操作する。   FIG. 11 is a longitudinal front view showing a transmission 20 having a fourth alternative structure. As shown in this figure, in the transmission device 20 having the fourth alternative embodiment structure, the output-side clutch mechanism 60 is integrated with the support portion 66 and the output-side interlocking body 27 that are provided so as to be integrally rotatable on the transmission side 23. A multi-plate friction clutch portion 67 provided over a rotatable clutch body 67a is provided to constitute a friction clutch mechanism. In the output side clutch mechanism 60, the friction clutch portion 67 is switched between an on state and a disengaged state by a hydraulic piston 67b built in the clutch body 67a, whereby the motor shaft 33a and the output rotating body 24 are brought into an interlocked engaged state. Switch to the linked cut-off state.

第４の別実施構造を備えた変速伝動装置２０では、リングギヤ４４とモータ軸３３ａとを連動入り状態と連動切り状態に切換え自在な摩擦クラッチ機構７９を備え、ＨＳＴモード伝動においてサンギヤ４２、遊星ギヤ４３及びリングギヤ４４がモータ軸３３ａと一体回転する状態と、ＨＳＴモード伝動においてリングギヤ４４が回転自在な状態とに切換え自在になっている。   The transmission 20 having the fourth alternative structure includes a friction clutch mechanism 79 that allows the ring gear 44 and the motor shaft 33a to be switched between an interlocked state and an interlocked off state. In the HST mode transmission, the sun gear 42 and the planetary gears are provided. 43 and the ring gear 44 can be switched between a state of rotating integrally with the motor shaft 33a and a state of rotating the ring gear 44 in the HST mode transmission.

〔別実施例〕
（１）上記した実施例では、入力軸２２の駆動力を遊星伝動部４０のキャリヤ４１に入力し、遊星伝動部４０のリングギヤ４４の駆動力を出力回転体２４に伝達するよう構成した例を示したが、入力軸２２の駆動力を遊星伝動部４０のリングギヤ４４に入力し、遊星伝動部４０のキャリヤ４１の駆動力を出力回転体２４に伝達するよう構成して実施してもよい。 [Another Example]
(1) In the above embodiment, the driving force of the input shaft 22 is input to the carrier 41 of the planetary transmission unit 40, and the driving force of the ring gear 44 of the planetary transmission unit 40 is transmitted to the output rotating body 24. Although shown, the driving force of the input shaft 22 may be input to the ring gear 44 of the planetary transmission unit 40 and the driving force of the carrier 41 of the planetary transmission unit 40 may be transmitted to the output rotor 24.

（２）上記した実施例では、入力軸２２をポンプ軸３２ａと別体に形成してポンプ軸３２ａにジョイント２２ａを介して連結し、伝動軸２３をモータ軸３３ａと別体に形成してモータ軸３３ａにジョイント２３ａを介して連結した例を示したが、入力軸２２をポンプ軸３２ａに一体形成し、伝動軸２３をモータ軸３３ａに一体形成して実施してもよい。 (2) In the above-described embodiment, the input shaft 22 is formed separately from the pump shaft 32a and connected to the pump shaft 32a via the joint 22a, and the transmission shaft 23 is formed separately from the motor shaft 33a. Although an example in which the shaft 33a is connected via the joint 23a is shown, the input shaft 22 may be integrally formed with the pump shaft 32a, and the transmission shaft 23 may be integrally formed with the motor shaft 33a.

本発明は、コンバインの他、田植機、運搬車など各種の車両に利用できる。   The present invention can be used for various vehicles such as a rice transplanter and a transporter in addition to a combine.

１ 走行装置
２２ 入力軸
２４ 出力回転体
３０ 油圧式無段変速機
３３ａ モータ軸
４０ 遊星伝動部
４１ キャリヤ
４２ サンギヤ
４３ 遊星ギヤ
４４ リングギヤ
５５ 入力側クラッチ機構
６０ 出力側クラッチ機構
７０ 伝動切換えクラッチ機構
DESCRIPTION OF SYMBOLS 1 Traveling device 22 Input shaft 24 Output rotary body 30 Hydraulic continuously variable transmission 33a Motor shaft 40 Planetary transmission part 41 Carrier 42 Sun gear 43 Planetary gear 44 Ring gear 55 Input side clutch mechanism 60 Output side clutch mechanism 70 Transmission switching clutch mechanism

Claims (3)

エンジン駆動力を入力する入力軸と、前記入力軸によって駆動されて前後進に無段変速可能な油圧式無段変速機と、前記入力軸の駆動力と前記油圧式無段変速機の出力とを合成して合成駆動力を出力する遊星伝動部と、走行装置に出力する出力回転体とを設けた農作業機の変速伝動装置であって、
前記入力軸の駆動力と前記油圧式無段変速機の出力とが前記遊星伝動部によって合成され、前記遊星伝動部による合成駆動力が前記出力回転体に伝達されるＨＭＴモード伝動を現出するように、前記遊星伝動部を前記入力軸と前記油圧式無段変速機のモータ軸と前記出力回転体とに連動させる合成伝動状態と、
前記油圧式無段変速機の出力が単独で前記出力回転体に伝達されるＨＳＴモード伝動を現出するように、かつ、ＨＳＴモード伝動を現出する状態で、前記遊星伝動部を構成するサンギヤと遊星ギヤとリングギヤを前記油圧式無段変速機のモータ軸と一体回転させるように、前記遊星伝動部の前記入力軸に対する連動を絶ちながら前記遊星伝動部と前記油圧式無段変速機のモータ軸を連動させ、かつ前記油圧式無段変速機のモータ軸と前記出力回転体を連動させた単独伝動状態とに切換え操作自在な伝動切換えクラッチ機構を設けてあり、
前進の高速側における変速域において、前記合成伝動状態となり、前進の低速側における変速域及び後進の変速域において、前記単独伝動状態となるように構成されている農作業機の変速伝動装置。 An input shaft for inputting engine driving force, a hydraulic continuously variable transmission driven by the input shaft and capable of continuously variable forward and backward, a driving force of the input shaft and an output of the hydraulic continuously variable transmission ; A transmission device for a farming machine provided with a planetary transmission unit that outputs a combined driving force and an output rotator that outputs to a traveling device,
The driving force of the input shaft and the output of the hydraulic continuously variable transmission are combined by the planetary transmission unit, and the combined driving force by the planetary transmission unit is transmitted to the output rotating body to produce an HMT mode transmission. Thus, a combined transmission state in which the planetary transmission unit is interlocked with the input shaft, the motor shaft of the hydraulic continuously variable transmission, and the output rotating body,
A sun gear that constitutes the planetary transmission unit in such a manner that an HST mode transmission in which an output of the hydraulic continuously variable transmission is independently transmitted to the output rotating body appears, and an HST mode transmission appears. And the planetary transmission section and the motor of the hydraulic continuously variable transmission while the planetary transmission section is not linked to the input shaft so that the planetary gear and the ring gear rotate together with the motor shaft of the hydraulic continuously variable transmission. by linking the shaft, and Ri Oh provided the hydraulic CVT single transmission state and freely switching operation of transmission switching clutch mechanism motor shaft by interlocking the output rotary member,
In the shift range in the high-speed side of the forward, the synthetic transmission state and becomes, in the transmission region and the reverse shift range in the low-speed side of the forward, the single transmission state become so constructed have that agricultural machine speed change transmission apparatus. 前記遊星伝動部のサンギヤと前記油圧式無段変速機のモータ軸とを一体回転自在に連動するよう構成して、
前記遊星伝動部のキャリヤを前記入力軸に対する連動入り状態と連動切り状態に切換える入力側クラッチ機構を備えて、
前記油圧式無段変速機のモータ軸の前記出力回転体に対する連動を絶ちながら前記遊星伝動部のリングギヤと前記出力回転体を一体回転自在に連動させる第１伝動状態と、前記油圧式無段変速機のモータ軸を前記遊星伝動部のリングギヤ及び前記出力回転体に一体回転自在に連動させる第２伝動状態とを択一的に現出する出力側クラッチ機構を備えて、前記伝動切換えクラッチ機構を構成してある請求項１記載の農作業機の変速伝動装置。 The sun gear of the planetary transmission unit and the motor shaft of the hydraulic continuously variable transmission are configured to interlock with each other so as to be integrally rotatable,
An input-side clutch mechanism that switches the carrier of the planetary transmission unit between an interlocking state and an interlocking off state with respect to the input shaft;
A first transmission state in which the ring gear of the planetary transmission unit and the output rotating body are interlocked so as to be integrally rotatable while the interlocking of the motor shaft of the hydraulic continuously variable transmission with the output rotating body is interrupted; and the hydraulic continuously variable transmission An output-side clutch mechanism that alternatively displays a second transmission state in which the motor shaft of the machine is linked to the ring gear of the planetary transmission unit and the output rotating body so as to be integrally rotatable, and the transmission switching clutch mechanism The transmission gear transmission for an agricultural machine according to claim 1 configured. 前記出力側クラッチ機構を、前記遊星伝動部のリングギヤと前記出力回転体とを連動状態に維持しながら、前記遊星伝動部のサンギヤと前記出力回転体とを連動入り状態と連動切り状態に切換えるように構成してある請求項２記載の農作業機の変速伝動装置。 The output-side clutch mechanism is configured to switch the sun gear of the planetary transmission unit and the output rotating body between the interlocking on state and the interlocking off state while maintaining the ring gear of the planetary transmission unit and the output rotating body in an interlocking state. The speed change transmission apparatus of the agricultural machine according to claim 2 configured as described above.
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