JP4372072B2

JP4372072B2 - Variable speed transmission

Info

Publication number: JP4372072B2
Application number: JP2005278251A
Authority: JP
Inventors: 実平岡
Original assignee: Kubota Corp
Current assignee: Kubota Corp
Priority date: 2005-09-26
Filing date: 2005-09-26
Publication date: 2009-11-25
Anticipated expiration: 2025-09-26
Also published as: JP2007085517A

Description

本発明は、エンジン駆動力が入力される無段変速装置、前記無段変速装置からの出力と、前記無段変速装置による変速作用を受けないエンジン駆動力とを第１遊星伝動機構、第２遊星伝動機構、第３遊星伝動機構によって合成する遊星伝動部、前記遊星伝動部から合成駆動力を入力するとともに第１クラッチ、第２クラッチ、第３クラッチ、第４クラッチを備えたクラッチ部、前記クラッチ部から入力する第４遊星伝動機構、前記第４遊星伝動機構のリングギヤに作用するブレーキを備え、前記無段変速装置が変速操作され、かつ、前記各クラッチ及び前記ブレーキが入り状態と切り状態に切り換え操作されることにより、無段変速装置の変速状態、各クラッチ及びブレーキの操作状態に対応した回転速度の出力を前記第４遊星伝動機構に連動された出力軸から出力する変速伝動装置に関する。 The present invention relates to a continuously variable transmission to which an engine driving force is input, an output from the continuously variable transmission, and an engine driving force that is not subjected to a shifting action by the continuously variable transmission. A planetary transmission mechanism, a planetary transmission unit to be combined by a third planetary transmission mechanism, a combined drive force from the planetary transmission unit and a clutch unit having a first clutch, a second clutch, a third clutch, a fourth clutch, A fourth planetary transmission mechanism that is input from a clutch unit; a brake that acts on a ring gear of the fourth planetary transmission mechanism; the continuously variable transmission is operated to change speed; and the clutches and the brakes are engaged and disengaged. To switch the output of the rotational speed corresponding to the operation state of the continuously variable transmission and each clutch and brake to the fourth planetary transmission mechanism. It relates to a shift transmission which is output from the output shaft.

上記の変速伝動装置として、従来、たとえば特許文献１に示されるものがあった。
特許文献１に示されるものでは、可変吐き出し静油圧ユニット４及び固定吐き出し静油圧ユニット６を備えたユニット（無段変速装置に相当）、第２遊星ギヤセット１０（第１遊星伝動機構に相当）、第１遊星ギヤセット９（第２遊星伝動機構に相当）、遊星ギヤセット２２（第３遊星伝動機構に相当）、カップリング２７（第1クラッチに相当）、カップリング３２（第２クラッチに相当）、カップリング３５（第３クラッチに相当）、カップリング３９（第４クラッチに相当）、第４遊星ギヤセット４１（第４遊星伝動機構に相当）、多板ディスクブレーキ４５（図１では４４、ブレーキに相当）を備えている。 Conventionally, for example, Japanese Patent Application Laid-Open No. H10-133707 discloses the above-described transmission gear transmission.
In what is shown in Patent Document 1, a unit (which corresponds to a continuously variable transmission) having a variable discharge hydrostatic unit 4 and a fixed discharge hydrostatic unit 6, a second planetary gear set 10 (corresponding to a first planetary transmission mechanism), A first planetary gear set 9 (corresponding to a second planetary transmission mechanism), a planetary gear set 22 (corresponding to a third planetary transmission mechanism), a coupling 27 (corresponding to a first clutch), a coupling 32 (corresponding to a second clutch), Coupling 35 (corresponding to the third clutch), coupling 39 (corresponding to the fourth clutch), fourth planetary gear set 41 (corresponding to the fourth planetary transmission mechanism), multi-disc disc brake 45 (44 in FIG. 1, 44) Equivalent).

この種の変速伝動装置では、第３遊星伝動機構のリングギヤに入力側回転部材が連動された第１クラッチと、第２遊星伝動機構及び第３遊星伝動機構のサンギヤギヤに入力側回転部材が連動された第２クラッチと、第1遊星伝動機構のキャリヤ、第２遊星伝動機構のリングギヤ、第３遊星伝動機構のキャリヤのそれぞれに入力側回転部材が連動された第３クラッチと、第1クラッチ及び第２クラッチの出力側回転部材に入力側回転部材が連動された第４クラッチとを備えて成るクラッチ部を備えられる。このクラッチ部として、従来、特許文献１に示される如く第1クラッチが第２クラッチの外周側に位置し、第３クラッチが第４クラッチの外周側に位置したクラッチ部を採用されていた。 In this type of transmission, the input side rotating member is linked to the first clutch in which the input side rotating member is linked to the ring gear of the third planetary transmission mechanism, and the sun gear gear of the second planetary transmission mechanism and the third planetary transmission mechanism. The second clutch, the carrier of the first planetary transmission mechanism, the ring gear of the second planetary transmission mechanism, the third clutch in which the input side rotating member is linked to the carrier of the third planetary transmission mechanism, the first clutch, A clutch portion is provided that includes a fourth clutch in which the input side rotating member is linked to the output side rotating member of the two clutches. As this clutch part, conventionally, as shown in Patent Document 1, a clutch part in which the first clutch is located on the outer peripheral side of the second clutch and the third clutch is located on the outer peripheral side of the fourth clutch has been adopted.

Ｕ．Ｓ．Ｐ．６，０４２，４９６（第２−４欄、図１）U. S. P. 6,042,496 (column 2-4, FIG. 1)

上記した従来の変速伝動装置において、クラッチとして、クラッチに内装の油圧ピストンによって入り状態と切り状態に切り換え操作される油圧クラッチを採用すると、殊に、外周側に位置するクラッチには内周側に位置するクラッチよりも強い遠心力が発生することから、遠心力が作動油に及ぼす影響のためにクラッチが切り換わりにくくなる事態が発生しやすくなっていた。 In the above-described conventional transmission gear transmission, when a hydraulic clutch that is switched between an on state and a disengaged state by an internal hydraulic piston is adopted as the clutch, in particular, the clutch located on the outer peripheral side has an inner peripheral side. Since a centrifugal force stronger than that of the clutch that is positioned is generated, a situation in which the clutch is difficult to switch due to the influence of the centrifugal force on the hydraulic oil is likely to occur.

本発明の目的は、油圧クラッチを採用しても遠心力の影響を受けにくい状態で変速作動させることができる変速伝動装置を提供することにある。 SUMMARY OF THE INVENTION An object of the present invention is to provide a speed change transmission apparatus that can perform a speed change operation without being affected by centrifugal force even when a hydraulic clutch is employed.

本第１発明にあっては、エンジン駆動力が入力される無段変速装置、前記無段変速装置からの出力と、前記無段変速装置による変速作用を受けないエンジン駆動力とを第１遊星伝動機構、第２遊星伝動機構、第３遊星伝動機構によって合成する遊星伝動部、前記遊星伝動部から合成駆動力を入力するとともに第１クラッチ、第２クラッチ、第３クラッチ、第４クラッチを備えたクラッチ部、前記クラッチ部から入力する第４遊星伝動機構、前記第４遊星伝動機構のリングギヤに作用するブレーキを備え、前記無段変速装置が変速操作され、かつ、前記各クラッチ及び前記ブレーキが入り状態と切り状態に切り換え操作されることにより、無段変速装置の変速状態、各クラッチ及びブレーキの操作状態に対応した回転速度の出力を前記第４遊星伝動機構に連動された出力軸から出力する変速伝動装置において、
前記無段変速装置による変速作用を受けないエンジン駆動力を前記第１遊星伝動機構のリングギヤに伝達する伝動軸の軸芯方向に並べて前記伝動軸に相対回転自在に外嵌させた第１伝動筒軸と第２伝動筒軸を備え、
前記第２遊星伝動機構及び前記第３遊星伝動機構のサンギヤと、前記第２クラッチの入力側回転部材とを前記第１伝動筒軸に一体回転自在に支持させ、
前記第１クラッチの入力側回転部材を、前記第２クラッチの入力側回転部材と前記伝動軸の軸芯に沿う方向に並べて前記第１伝動筒軸に相対回転自在に支持させるとともに、前記第1クラッチの入力側回転部材に前記第３遊星伝動機構のリングギヤを連動させる連動部材を、前記第１クラッチと前記第３遊星伝動機構の間を通る状態に配置し、
前記第1クラッチ及び前記第２クラッチの出力側回転部材を前記第２伝動筒軸に連動させるとともに、前記第４クラッチの入力側回転部材を前記第２伝動筒軸に一体回転自在に支持させ、
前記第３クラッチの入力側回転部材を、前記第４クラッチの入力側回転部材と前記伝動軸の軸芯に沿う方向に並べて前記第２伝動筒軸に相対回転自在に支持させるとともに、前記第３クラッチの入力側回転部材に前記第1遊星伝動機構のキャリヤ、前記第２遊星伝動機構のリングギヤ、前記第３遊星伝動機構のキャリヤを連動させる連動部材を、前記第２クラッチと前記第３クラッチの間を通る状態に配置し、
前記第３クラッチの出力側回転部材と、前記第４クラッチの出力側回転部材とを一体形成し、第４クラッチの前記出力側回転部材に、前記第４遊星伝動機構のキャリヤに対して係止して連動する係止連動部を設けてある。 According to the first aspect of the present invention, the continuously variable transmission to which the engine driving force is input, the output from the continuously variable transmission, and the engine driving force that is not subjected to the shifting action by the continuously variable transmission are the first planetary. A transmission mechanism, a second planetary transmission mechanism, a planetary transmission section synthesized by a third planetary transmission mechanism, a composite driving force is input from the planetary transmission section, and a first clutch, a second clutch, a third clutch, and a fourth clutch are provided. A clutch unit, a fourth planetary transmission mechanism that inputs from the clutch unit, a brake that acts on a ring gear of the fourth planetary transmission mechanism, the continuously variable transmission is operated for shifting, and the clutches and the brakes are By switching between the on state and the off state, the output of the rotational speed corresponding to the shift state of the continuously variable transmission and the operation state of each clutch and brake is output to the fourth planetary gear. In the speed change transmission apparatus to be output from the interlocking output shaft rotation mechanism,
A first transmission cylinder that is lined up in the axial direction of the transmission shaft that transmits engine driving force that is not subjected to a speed change effect by the continuously variable transmission to the ring gear of the first planetary transmission mechanism, and is fitted around the transmission shaft so as to be relatively rotatable. A shaft and a second transmission cylinder shaft,
A sun gear of the second planetary transmission mechanism and the third planetary transmission mechanism, and an input side rotation member of the second clutch are supported on the first transmission cylinder shaft so as to be integrally rotatable,
The input side rotation member of the first clutch is arranged in a direction along the axis of the transmission side of the input clutch of the second clutch and the shaft of the transmission shaft, and is supported by the first transmission cylinder shaft so as to be relatively rotatable. An interlocking member for interlocking the ring gear of the third planetary transmission mechanism with the input side rotation member of the clutch is disposed so as to pass between the first clutch and the third planetary transmission mechanism,
The output side rotation member of the first clutch and the second clutch is interlocked with the second transmission cylinder shaft, and the input side rotation member of the fourth clutch is supported on the second transmission cylinder shaft so as to be integrally rotatable.
The input side rotating member of the third clutch is arranged in a direction along the axis of the transmission shaft of the fourth clutch and the shaft of the transmission shaft, and is supported by the second transmission cylinder shaft so as to be relatively rotatable. An interlocking member that interlocks the carrier of the first planetary transmission mechanism, the ring gear of the second planetary transmission mechanism, and the carrier of the third planetary transmission mechanism with the input side rotation member of the clutch, and the second clutch and the third clutch. Place it in a state that passes between ,
The output side rotation member of the third clutch and the output side rotation member of the fourth clutch are integrally formed, and the output side rotation member of the fourth clutch is locked to the carrier of the fourth planetary transmission mechanism. A locking interlocking portion that interlocks with each other is provided .

すなわち、第１〜第４クラッチを伝動軸の軸芯に沿う方向に一列に並んだ状態に配置しても、第1クラッチの入力側回転部材が前記伝動部材によって第３遊星伝動機構のリングギヤに連動され、第２クラッチの入力側回転部材が第1伝動筒軸によって第２遊星伝動機構及び第３遊星伝動機構のサンギヤに連動され、第１クラッチ及び第２クラッチの出力側回転部材が第２伝動筒軸によって第４クラッチの入力側回転部材に連動され、第３クラッチの入力側回転部材が前記連動部材によって第1遊星伝動機構のキャリヤ、第２遊星伝動機構のリングギヤ、第３遊星伝動機構のキャリヤのそれぞれに連動され、無段変速装置、各クラッチ、ブレーキが適切に操作されることによってエンジン駆動力が所定の回転速度に変速されて出力軸から出力されるように、遊星伝動部からの合成駆動力をクラッチ部を介して第４遊星伝動機構に連動させることができる。
第３クラッチの出力側回転部材と第４クラッチの出力側回転部材を一体部材に製作しながら、出力側回転部材と、第４遊星伝動機構のキャリヤとを係止連動部で分離させて、第３及び第４クラッチと第４遊星伝動機構を別々に第２伝動筒軸に組み付けても、第３及び第４クラッチ、第４遊星伝動機構の第２伝動筒軸への組み付けが完了した状態では、出力側回転部材と第４遊星伝動機構のキャリヤが係止連動部で係止し合って第３クラッチ及び第４ラッチの出力側回転部材が第４遊星伝動機構のキャリヤに連動された組み立て状態を得ることができる。 That is, even if the first to fourth clutches are arranged in a line along the axis of the transmission shaft, the input side rotating member of the first clutch is used as a ring gear of the third planetary transmission mechanism by the transmission member. The input side rotation member of the second clutch is linked to the sun gears of the second planetary transmission mechanism and the third planetary transmission mechanism by the first transmission cylinder shaft, and the output side rotation members of the first clutch and the second clutch are the second one. The transmission cylinder shaft is linked to the input side rotating member of the fourth clutch, and the input side rotating member of the third clutch is linked to the carrier of the first planetary transmission mechanism, the ring gear of the second planetary transmission mechanism, and the third planetary transmission mechanism. The engine driving force is shifted to a predetermined rotational speed and output from the output shaft by appropriately operating the continuously variable transmission, each clutch, and the brake in conjunction with each of the carriers. Sea urchin, it is possible to interlock the combined drive force from the planetary transmission section to the fourth planetary transmission mechanism through the clutch unit.
While the output-side rotating member of the third clutch and the output-side rotating member of the fourth clutch are manufactured as an integrated member, the output-side rotating member and the carrier of the fourth planetary transmission mechanism are separated by the locking interlocking portion, Even when the third and fourth clutches and the fourth planetary transmission mechanism are separately assembled to the second transmission cylinder shaft, the assembly of the third and fourth clutches and the fourth planetary transmission mechanism to the second transmission cylinder shaft is completed. The assembled state in which the output-side rotating member and the carrier of the fourth planetary transmission mechanism are engaged with each other by the engaging interlocking portion, and the output-side rotating member of the third clutch and the fourth latch are interlocked with the carrier of the fourth planetary transmission mechanism. Can be obtained.

従って、本第１発明によると、第１〜第４クラッチを伝動軸の軸芯に沿う方向に一列に並んだ配置状態にして、各クラッチに発生する遠心力が同一又はそれに近い値の遠心力になるように、かつ、極力小さな遠心力になるように各クラッチの外径を同一またはほぼ同一で、かつ、極力小さい外径にし、各クラッチを油圧クラッチにしたとしても、遠心力に起因したトラブルが発生しにくくてスムーズに変速作動させることができる。
本第１発明によると、第３クラッチと第４クラッチの出力側回転部材を一体部材に製作して安価に得ることができるものでありながら、第３及び第４クラッチと第４遊星伝動機構とを別々に第２伝動筒軸に組み付けるという組み付け方法を採用して、組み立て作業を容易にかつ能率よく行うことができる。 Therefore, according to the first invention, the first to fourth clutches are arranged in a line in the direction along the axis of the transmission shaft, and the centrifugal force generated in each clutch is equal to or close to the centrifugal force. Even if the outer diameter of each clutch is the same or almost the same and the outer diameter is made as small as possible so that the centrifugal force is as small as possible, and each clutch is a hydraulic clutch, it is caused by centrifugal force. Troubles are unlikely to occur and the gear shifting operation can be performed smoothly.
According to the first aspect of the present invention, the third and fourth clutches and the fourth planetary transmission mechanism can be obtained at low cost by manufacturing the output side rotation members of the third clutch and the fourth clutch as an integral member. Assembling work can be easily and efficiently carried out by adopting an assembling method of separately assembling to the second transmission cylinder shaft.

本第２発明にあっては、本第１発明の構成において、前記第１クラッチの前記出力側回転部材と、前記第２クラッチの前記出力側回転部材とを一体形成し、第２クラッチの出力側回転部材の係止連動部に一端側が一体回動自在に係止され、他端側が前記第２伝動筒軸に連結されて第１及び第２クラッチの出力側回転部材を第２伝動筒軸に連動させている伝動部材を備えてある。 In the second invention, in the configuration of the first invention, the output-side rotating member of the first clutch and the output-side rotating member of the second clutch are integrally formed, and the output of the second clutch One end side is locked to the interlocking interlocking portion of the side rotation member so as to be integrally rotatable, the other end side is connected to the second transmission cylinder shaft, and the output side rotation members of the first and second clutches are connected to the second transmission cylinder shaft. Is provided with a transmission member linked to the.

すなわち、第１クラッチの出力側回転部材と第２クラッチの出力側回転部材を一体部材に作製しながら、出力側回転部材と伝動部材を係止連動部で分離させて第１伝動筒軸と第２伝動筒軸に別々に組み付け、この後、第１及び第２クラッチを第１伝動筒軸と共に伝動軸に組み付け、伝動部材を第２伝動筒軸と共に伝動軸に組み付けても、第１及び第２伝動筒軸を伝動軸に組み付けた状態では、出力側回転部材と伝動部材が係止連動部で係止し合って第１クラッチ及び第２クラッチの出力側回転部材が第２伝動筒軸に連動された組み立て状態を得ることができる。 That is, while the output-side rotating member of the first clutch and the output-side rotating member of the second clutch are made as an integral member, the output-side rotating member and the transmission member are separated by the locking interlocking portion, and the first transmission cylinder shaft and the first 2 Even if the first and second clutches are assembled to the transmission shaft together with the first transmission cylinder shaft, and the transmission member is assembled to the transmission shaft together with the second transmission cylinder shaft. 2 In the state where the transmission cylinder shaft is assembled to the transmission shaft, the output side rotation member and the transmission member are engaged with each other by the interlocking interlocking portion, and the output side rotation members of the first clutch and the second clutch become the second transmission cylinder shaft. A linked assembly state can be obtained.

従って、本第２発明によると、第１クラッチと第２クラッチの出力側回転部材を一体部材に製作して安価に得ることができるものでありながら、かつ、第１及び第２クラッチを第１伝動筒軸に支持させ、第１及び第２クラッチの出力側回転部材を第２伝動筒軸に連動させるものでありながら、第１及び第２クラッチと伝動部材を別々に第１伝動筒軸や第２伝動筒軸に組み付け、第１及び第２クラッチを第１伝動筒軸と共に伝動軸に、伝動部材を第２伝動筒軸と共に伝動軸にそれぞれ組み付けるという組み付け方法を採用して組み立て作業を容易にかつ能率よく行うことができる。 Therefore, according to the second aspect of the present invention, the output side rotating member of the first clutch and the second clutch can be manufactured as an integral member and can be obtained at a low cost, and the first and second clutches can be obtained as the first clutch. The first and second clutches and the transmission member are separately supported by the first transmission cylinder shaft, while being supported by the transmission cylinder shaft and interlocking the output side rotation members of the first and second clutches with the second transmission cylinder shaft. Assembling is easy by assembling the second transmission cylinder shaft and the first and second clutches together with the first transmission cylinder shaft to the transmission shaft and the transmission member together with the second transmission cylinder shaft. And can be carried out efficiently.

本第３発明にあっては、本第１又は第２発明の構成において、前記ブレーキに、前記第４遊星伝動機構のリングギヤに連結された状態で前記伝動軸に相対回転自在に外嵌させた可動側ブレーキ体を備えてある。 In the third aspect of the invention, in the configuration of the first or second aspect of the invention, the brake is externally fitted to the transmission shaft so as to be relatively rotatable while being connected to the ring gear of the fourth planetary transmission mechanism. A movable brake body is provided.

すなわち、ブレーキの可動側ブレーキ体が伝動軸に支持され、遊星伝動部、クラッチ部、第４遊星伝動機構、ブレーキが伝動軸に支持されてユニットになった状態になるものである。 That is, the movable brake body of the brake is supported by the transmission shaft, and the planetary transmission unit, the clutch unit, the fourth planetary transmission mechanism, and the brake are supported by the transmission shaft and become a unit.

従って、本第３発明によると、遊星伝動部、クラッチ部、第４遊星伝動機構、ブレーキを伝動軸に組み付けたユニット状態にして一挙にミッションケースに組み付け、組み付け作業を能率よく行うことができる。 Therefore, according to the third aspect of the invention, the planetary transmission unit, the clutch unit, the fourth planetary transmission mechanism, and the brake can be assembled into the transmission case at once, and the assembly operation can be performed efficiently.

以下、本発明の実施例を図面に基づいて説明する。
図１に示されるように、エンジン１の出力軸１ａから出力されるエンジン駆動力が主クラッチ２を介して変速伝動装置Ａの入力軸としてのポンプ軸１１に入力され、この変速伝動装置Ａの出力軸３からの出力が前後進切り換え装置２０の入力軸２１に伝達され、この前後進切り換え装置２０の出力軸２２からの出力が後輪差動機構４に伝達されるように構成し、前記前後進切り換え装置２０の出力軸２２からの出力が前輪動力取り出し軸５及び伝動軸６を介して前輪差動機構７に伝達されるように構成して、トラクタの走行用伝動装置を構成してある。 Embodiments of the present invention will be described below with reference to the drawings.
As shown in FIG. 1, the engine driving force output from the output shaft 1 a of the engine 1 is input to the pump shaft 11 as the input shaft of the transmission transmission A via the main clutch 2, and the transmission transmission A The output from the output shaft 3 is transmitted to the input shaft 21 of the forward / reverse switching device 20, and the output from the output shaft 22 of the forward / backward switching device 20 is transmitted to the rear wheel differential mechanism 4. The output from the output shaft 22 of the forward / reverse switching device 20 is configured to be transmitted to the front wheel differential mechanism 7 via the front wheel power take-out shaft 5 and the transmission shaft 6 to constitute a tractor traveling transmission device. is there.

図１に示すように、前記変速伝動装置Ａは、前記ポンプ軸１１を備えた無段変速装置１０、この無段変速装置１０のポンプ軸１１及びモータ軸１２から入力されるとともに第１遊星伝動機構Ｐ１、第２遊星伝動機構Ｐ２、第３遊星伝動機構Ｐ３を備えた遊星伝動部Ｐ、この遊星伝動部Ｐから入力されるとともに第１クラッチＣ１、第２クラッチＣ２、第３クラッチＣ３、第４クラッチＣ４を備えたクラッチ部Ｃ、このクラッチ部Ｃから入力される第４遊星伝動機構Ｐ４、この第４遊星伝動機構Ｐ４に作用するブレーキＢＧ、前記第４遊星伝動機構Ｐ４にギヤ機構１２０を介して連動された前記出力軸３を備えて構成してある。 As shown in FIG. 1, the transmission A is input from a continuously variable transmission 10 having the pump shaft 11, a pump shaft 11 and a motor shaft 12 of the continuously variable transmission 10, and a first planetary transmission. A planetary transmission unit P including a mechanism P1, a second planetary transmission mechanism P2, a third planetary transmission mechanism P3, and the first clutch C1, the second clutch C2, the third clutch C3, A clutch unit C having four clutches C4, a fourth planetary transmission mechanism P4 inputted from the clutch unit C, a brake BG acting on the fourth planetary transmission mechanism P4, and a gear mechanism 120 on the fourth planetary transmission mechanism P4. The output shaft 3 is interlocked with each other.

前記無段変速装置１０は、前記ポンプ軸１１を備えた可変容量形のアキシャルプランジャ形油圧ポンプ１３、この油圧ポンプ１３からの圧油によって駆動されるとともに前記モータ軸１２を備えたアキシャルプランジャ形の油圧モータ１４を備えて成る静油圧式無段変速装置に構成してある。
従って、この無段変速装置１０は、油圧ポンプ１３の斜板角変更が行われることにより、エンジン１からの駆動力を正回転方向の駆動力に変換するとともに無段階に変速してモータ軸１２から出力する正回転伝動状態と、エンジン１からの駆動力を逆回転方向の駆動力に変換するとともに無段階に変速してモータ軸１２から出力する逆回転伝動状態と、油圧モータ１４の駆動を停止してモータ軸１２からの出力を停止する中立状態とに切り換わる。 The continuously variable transmission 10 is a variable displacement axial plunger type hydraulic pump 13 having the pump shaft 11 and is driven by pressure oil from the hydraulic pump 13 and is an axial plunger type having the motor shaft 12. The hydrostatic continuously variable transmission is provided with a hydraulic motor 14.
Accordingly, the continuously variable transmission 10 changes the swash plate angle of the hydraulic pump 13 to convert the driving force from the engine 1 into a driving force in the forward rotation direction and continuously shifts the motor shaft 12. A normal rotation transmission state output from the motor 1, a reverse rotation transmission state in which the driving force from the engine 1 is converted into a driving force in the reverse rotation direction, and the speed is steplessly output from the motor shaft 12, and the hydraulic motor 14 is driven. It switches to the neutral state in which it stops and stops the output from the motor shaft 12.

図２，３に示すように、遊星伝動部Ｐの第１遊星伝動機構Ｐ１は、サンギヤ３１、このサンギヤ３１の周囲に分散して位置する複数個の遊星ギヤ３２、各遊星ギヤ３２を自転回動自在に支持するキャリヤ３３、各遊星ギヤ３２に噛合ったリングギヤ３４を備えて構成してある。この第１遊星伝動機構Ｐ１のサンギヤ３１は、無段変速装置１０のモータ軸１２からの出力が第１入力軸１２１などによって入力される。図１に示すように、この第１遊星伝動機構Ｐ１のリングギヤ３４は、無段変速装置１０のポンプ軸１１から第２入力軸１２３によって取り出された駆動力が伝動軸１２４などによって入力される。 As shown in FIGS. 2 and 3, the first planetary transmission mechanism P1 of the planetary transmission unit P includes a sun gear 31, a plurality of planetary gears 32 that are distributed around the sun gear 31, and each planetary gear 32 that rotates. A carrier 33 that is movably supported and a ring gear 34 that meshes with each planetary gear 32 are provided. In the sun gear 31 of the first planetary transmission mechanism P1, the output from the motor shaft 12 of the continuously variable transmission 10 is input by the first input shaft 121 or the like. As shown in FIG. 1, in the ring gear 34 of the first planetary transmission mechanism P1, the driving force extracted by the second input shaft 123 from the pump shaft 11 of the continuously variable transmission 10 is input by the transmission shaft 124 or the like.

図２，３に示すように、遊星伝動部Ｐの第２遊星伝動機構Ｐ２は、サンギヤ４１、サンギヤ４１の周囲に分散して位置する複数個の遊星ギヤ４２、各遊星ギヤ４２を自転回動自在に支持するキャリヤ４３、各遊星ギヤ４２にかみ合ったリングギヤ４４を備えて構成してある。図１に示すように、この第２遊星伝動機構Ｐ２のキャリヤ４３は、無段変速装置１０のポンプ軸１１から第２入力軸１２３によって取り出された駆動力が伝動軸１２４などによって入力される。 As shown in FIGS. 2 and 3, the second planetary transmission mechanism P2 of the planetary transmission unit P includes a sun gear 41, a plurality of planetary gears 42 that are distributed around the sun gear 41, and each planetary gear 42 that rotates. A carrier 43 that is freely supported and a ring gear 44 that meshes with each planetary gear 42 are provided. As shown in FIG. 1, in the carrier 43 of the second planetary transmission mechanism P2, the driving force extracted by the second input shaft 123 from the pump shaft 11 of the continuously variable transmission 10 is input by the transmission shaft 124 or the like.

図２，３に示すように、遊星伝動部Ｐの第３遊星伝動機構Ｐ３は、サンギヤ５１、このサンギヤ５１の周囲に分散して位置する複数個の遊星ギヤ５２、各遊星ギヤ５２を自転回動自在に支持するキャリヤ５３、各遊星ギヤ５２に噛合ったリングギヤ５４を備えて構成してある。 As shown in FIGS. 2 and 3, the third planetary transmission mechanism P3 of the planetary transmission unit P includes a sun gear 51, a plurality of planetary gears 52 that are distributed around the sun gear 51, and each planetary gear 52 that rotates. A carrier 53 that is movably supported and a ring gear 54 that meshes with each planetary gear 52 are provided.

図２，３に示すように、第１遊星伝動機構Ｐ１のキャリヤ３３と、第２遊星伝動機構Ｐ２のリングギヤ４４と、第３遊星伝動機構Ｐ３のキャリヤ５３とは、各キャリヤ３３，５３及びリングギヤ４４の外周側に係合した円筒状の連動部材１２５によって一体回転自在に連動されている。第１遊星伝動機構Ｐ１のリングギヤ３４と、第２遊星伝動機構Ｐ２のキャリヤ４３とは、一体回転自在に連動されている。第２遊星伝動機構Ｐ２のサンギヤ４１は、前記第１伝動筒軸１２６の端部にスプライン係合によって一体回転自在な状態で支持され、第３遊星伝動機構Ｐ３のサンギヤ５１は、前記第１伝動筒軸１２６の中間部に一体形成されており、第２遊星伝動機構Ｐ２のサンギヤ４１と、第３遊星伝動機構Ｐ３のサンギヤ５１とは、伝動筒軸１２６によって一体回転自在に連動されている。 As shown in FIGS. 2 and 3, the carrier 33 of the first planetary transmission mechanism P1, the ring gear 44 of the second planetary transmission mechanism P2, and the carrier 53 of the third planetary transmission mechanism P3 include the carriers 33 and 53 and the ring gear. A cylindrical interlocking member 125 engaged with the outer peripheral side of 44 is interlocked so as to be integrally rotatable. The ring gear 34 of the first planetary transmission mechanism P1 and the carrier 43 of the second planetary transmission mechanism P2 are interlocked so as to be integrally rotatable. The sun gear 41 of the second planetary transmission mechanism P2 is supported by the end of the first transmission cylindrical shaft 126 so as to be integrally rotatable by spline engagement. The sun gear 51 of the third planetary transmission mechanism P3 is supported by the first transmission transmission shaft P126. The sun gear 41 of the second planetary transmission mechanism P2 and the sun gear 51 of the third planetary transmission mechanism P3 are interlocked with the transmission cylinder shaft 126 so as to be integrally rotatable.

図２，４に示すように、クラッチ部Ｃの第１クラッチＣ１は、第３遊星伝動機構Ｐ３のリングギヤ５４に円板状の連動部材１２７によって連動された筒状の入力側回転部材６１、この入力側回転部材６１の外周囲に位置する筒状の出力側回転部材６２、入力側回転部材６１と出力側回転部材６２の間に設けた多板式の摩擦クラッチ機構６３を備えて構成してある。これにより、第１クラッチＣ１は、摩擦クラッチ機構６３が入り切り操作されることにより、第３遊星伝動機構Ｐ３のリングギヤ５４と出力側回転部材６２が一体回転自在に連動するように入力側回転部材６１と出力側回転部材６２とを摩擦クラッチ機構６３によって一体回転自在に摩擦連動させた入り状態と、第３遊星伝動機構Ｐ３のリングギヤ５４と出力側回転部材６２が相対回転するように入力側回転部材６１と出力側回転部材６２の連動を絶った切り状態とに切り換わる。 As shown in FIGS. 2 and 4, the first clutch C1 of the clutch portion C includes a cylindrical input-side rotating member 61 that is linked to the ring gear 54 of the third planetary transmission mechanism P3 by a disk-like interlocking member 127. A cylindrical output-side rotating member 62 located on the outer periphery of the input-side rotating member 61, and a multi-plate friction clutch mechanism 63 provided between the input-side rotating member 61 and the output-side rotating member 62 are configured. . As a result, the first clutch C1 is operated so that the friction clutch mechanism 63 is turned on and off, so that the ring gear 54 of the third planetary transmission mechanism P3 and the output-side rotating member 62 are interlocked so as to be integrally rotatable. And the input side rotating member 62 so that the ring gear 54 of the third planetary transmission mechanism P3 and the output side rotating member 62 rotate relative to each other. 61 and the output side rotating member 62 are switched to the cut-off state.

図２，４に示すように、クラッチ部Ｃの第２クラッチＣ２は、第２遊星伝動機構Ｐ２及び第３遊星伝動機構Ｐ３のサンギヤ４１，５１に第１連動筒軸１２６によって一体回転自在に連動された筒状の入力側回転部材７１、この入力側回転部材７１の外周囲に位置する筒状の出力側回転部材７２、入力側回転部材７１と出力側回転部材７２の間に設けた多板式の摩擦クラッチ機構７３を備えて構成してある。これにより、第２クラッチＣ２は、摩擦クラッチ機構７３が入り切り操作されることにより、第２遊星伝動機構Ｐ２及び第３遊星伝動機構Ｐ３のサンギヤ４１，５１と出力側回転部材７２が一体回転自在に連動するように入力側回転部材７１と出力側回転部材７２を摩擦クラッチ機構７３によって一体回転自在に摩擦連動させた入り状態と、第２遊星伝動機構Ｐ２及び第３遊星伝動機構Ｐ３のサンギヤ４１，５１と出力側回転部材７２が相対回転するように入力側回転部材７１と出力側回転部材７２の連動を絶った切り状態とに切り換わる。 As shown in FIGS. 2 and 4, the second clutch C 2 of the clutch portion C is linked to the sun gears 41 and 51 of the second planetary transmission mechanism P 2 and the third planetary transmission mechanism P 3 so as to be integrally rotatable by the first interlocking cylinder shaft 126. A cylindrical input side rotating member 71, a cylindrical output side rotating member 72 located on the outer periphery of the input side rotating member 71, and a multi-plate type provided between the input side rotating member 71 and the output side rotating member 72. The friction clutch mechanism 73 is provided. As a result, the second clutch C2 allows the sun gears 41 and 51 of the second planetary transmission mechanism P2 and the third planetary transmission mechanism P3 and the output-side rotating member 72 to rotate together as the friction clutch mechanism 73 is turned on and off. An input state in which the input-side rotating member 71 and the output-side rotating member 72 are frictionally interlocked with each other by the friction clutch mechanism 73 so as to be interlocked, and the sun gears 41 of the second planetary transmission mechanism P2 and the third planetary transmission mechanism P3. The input side rotation member 71 and the output side rotation member 72 are switched to a cut-off state so that the 51 and the output side rotation member 72 rotate relative to each other.

図２，４に示すように、クラッチ部Ｃの第３クラッチＣ３は、第１遊星伝動機構Ｐ１のキャリヤ３３、第２遊星伝動機構Ｐ２のリングギヤ４４、第３遊星伝動機構Ｐ３のキャリヤ５３のそれぞれに前記連動部材１２５と、この連動部材１２５に一端側が連結した連動部材１２８によって一体回転自在に連結された筒状の入力側回転部材８１、この入力側回転部材８１の外周囲に位置する筒状の出力側回転部材８２、入力側回転部材８１と出力側回転部材８２の間に設けた多板式の摩擦クラッチ機構８３を備えて構成してある。これにより、第３クラッチＣ３は、摩擦クラッチ機構８３が入り切り操作されることにより、第１遊星伝動機構Ｐ１のキャリヤ３３、第２遊星伝動機構Ｐ２のリングギヤ４４、第３遊星伝動機構Ｐ３のキャリヤ５３のそれぞれと出力側回転部材８２が一体回転するように入力側回転部材８１と出力側回転部材８２を摩擦クラッチ機構８３によって一体回転自在に摩擦連動させた入り状態と、第１遊星伝動機構Ｐ１のキャリヤ３３、第２遊星伝動機構Ｐ２のリングギヤ４４、第３遊星伝動機構Ｐ３のキャリヤ５３のそれぞれと出力側回転部材８２が相対回転するように入力側回転部材８１と出力側回転部材８２の連動を絶った切り状態とに切り換わる。 As shown in FIGS. 2 and 4, the third clutch C3 of the clutch portion C includes the carrier 33 of the first planetary transmission mechanism P1, the ring gear 44 of the second planetary transmission mechanism P2, and the carrier 53 of the third planetary transmission mechanism P3. Further, the interlocking member 125, a cylindrical input side rotating member 81 connected to the interlocking member 125 at one end side thereof so as to be integrally rotatable, and a cylindrical shape positioned on the outer periphery of the input side rotating member 81. Output side rotating member 82, and a multi-plate friction clutch mechanism 83 provided between the input side rotating member 81 and the output side rotating member 82. Thus, the third clutch C3 is operated by turning on and off the friction clutch mechanism 83, whereby the carrier 33 of the first planetary transmission mechanism P1, the ring gear 44 of the second planetary transmission mechanism P2, and the carrier 53 of the third planetary transmission mechanism P3. And an input state in which the input side rotating member 81 and the output side rotating member 82 are frictionally interlocked by the friction clutch mechanism 83 so that the output side rotating member 82 and the output side rotating member 82 rotate integrally, and the first planetary transmission mechanism P1. The input side rotating member 81 and the output side rotating member 82 are interlocked so that the carrier 33, the ring gear 44 of the second planetary transmission mechanism P2, the carrier 53 of the third planetary transmission mechanism P3, and the output side rotating member 82 rotate relative to each other. Switch to a cut-off state.

図２，４に示すように、クラッチ部Ｃの第４クラッチＣ４は、第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２に連動部材１２９、第２伝動筒軸１３０によって一体回動自在に連動された筒状の入力側回転部材９１、入力側回転部材９１の外周囲に位置する筒状の出力側回転部材９２、入力側回転部材９１と出力側回転部材９２の間に設けた多板式の摩擦クラッチ機構９３を備えて構成してある。これにより、第４クラッチＣ４は、摩擦クラッチ機構９３が入り切り操作されることにより、第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２と出力側回転部材９２が一体回転するように入力側回転部材９１と出力側回転部材９２を摩擦クラッチ機構９３によって一体回転自在に摩擦連動させた入り状態と、第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２と出力側回転部材９２が相対回転するように入力側回転部材９１と出力側回転部材９２の連動を絶った切り状態とに切り換わる。 As shown in FIGS. 2 and 4, the fourth clutch C 4 of the clutch portion C is integrally rotated by the interlocking member 129 and the second transmission cylinder shaft 130 on the output side rotating members 62 and 72 of the first clutch C 1 and the second clutch C 2. A cylindrical input-side rotating member 91 that is movably linked, a cylindrical output-side rotating member 92 that is positioned on the outer periphery of the input-side rotating member 91, and provided between the input-side rotating member 91 and the output-side rotating member 92. A multi-plate friction clutch mechanism 93 is provided. As a result, the fourth clutch C4 is configured so that the output-side rotating members 62 and 72 and the output-side rotating member 92 of the first clutch C1 and the second clutch C2 rotate integrally as the friction clutch mechanism 93 is turned on and off. An input state in which the input side rotation member 91 and the output side rotation member 92 are frictionally interlocked so as to be integrally rotatable by the friction clutch mechanism 93, and the output side rotation members 62 and 72 of the first clutch C1 and the second clutch C2 and the output side rotation. The input side rotating member 91 and the output side rotating member 92 are switched to a cut-off state so that the member 92 rotates relative to each other.

図２，５に示すように、第４遊星伝動機構Ｐ４は、第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２に伝動部材１２９、第２連動筒軸１３０を介して一体回転自在に連動されたサンギヤ１０１、このサンギヤ１０１の周囲に分散して位置する複数個の遊星ギヤ１０２、各遊星ギヤ１０２を自転回動自在に支持するキャリヤ１０３、各遊星ギヤ１０２に噛合ったリングギヤ１０４を備えて構成してある。第４遊星伝動機構Ｐ４のキャリヤ１０３は、第３クラッチＣ３及び第４クラッチＣ４の出力側回転部材８２，９２に一体回転自在に連動されている。 As shown in FIG. 2 and 5, the fourth planetary transmission mechanism P4 is heat moving member 129, through the second interlocking cylinder shaft 130 integrally with the output rotary member 62, 72 of the first clutch C1 and second clutch C2 A sun gear 101 that is rotatably coupled, a plurality of planetary gears 102 that are distributed around the sun gear 101, a carrier 103 that rotatably supports each planetary gear 102, and a planetary gear 102 that mesh with each other. A ring gear 104 is provided. The carrier 103 of the fourth planetary transmission mechanism P4 is interlocked to the third clutch C3 and the output side rotating members 82 and 92 of the fourth clutch C4 so as to be integrally rotatable.

図５に明示するように、ブレーキＢＧは、第４遊星伝動機構Ｐ４のリングギヤ１０４に連動部材１３１によって一体回動自在に連動された可動側ブレーキ体１１１、この可動側ブレーキ体１１１の外周囲に位置する円筒状の固定側ブレーキ体１１２、可動側ブレーキ体１１１と固定側ブレーキ体１１２の間に設けた多板式の摩擦ブレーキ機構１１３を備えて構成してある。これにより、ブレーキＢＧは、摩擦ブレーキ機構１１３が入り切り操作されることにより、第４遊星伝動機構Ｐ４のリングギヤ１０４を回動不能に固定するように可動側ブレーキ体１１１に摩擦ブレーキ機構１１３によって摩擦ブレーキを掛けた入り状態と、第４遊星伝動機構Ｐ４のリングギヤ１０４の回動を許容するように可動側ブレーキ体１１１の摩擦ブレーキを解除した切り状態とに切り換わる。 As clearly shown in FIG. 5, the brake BG is provided on the outer periphery of the movable brake body 111, and the movable brake body 111 is interlocked with the ring gear 104 of the fourth planetary transmission mechanism P4 by the interlocking member 131 so as to be integrally rotatable. A cylindrical fixed brake body 112 and a multi-plate friction brake mechanism 113 provided between the movable brake body 111 and the fixed brake body 112 are provided. As a result, the brake BG is frictionally braked by the friction brake mechanism 113 on the movable brake body 111 so that the ring gear 104 of the fourth planetary transmission mechanism P4 is fixed to be unrotatable when the friction brake mechanism 113 is turned on and off. Is switched to the engaged state where the friction brake of the movable brake body 111 is released so as to allow the ring gear 104 of the fourth planetary transmission mechanism P4 to rotate.

出力軸３は、この出力軸３に一体回転自在に設けた伝動ギヤ１３２、この伝動ギヤ１３２に噛合った伝動ギヤ１３３を一体回転自在に連結した連動筒軸１３４を介して第４遊星伝動機構Ｐ４のキャリヤ１０３に連動させてある。 The output shaft 3 is a fourth planetary transmission mechanism via a transmission gear 132 provided on the output shaft 3 so as to be integrally rotatable, and an interlocking cylindrical shaft 134 which is connected to the transmission gear 133 meshed with the transmission gear 132 so as to be integrally rotatable. It is linked with the carrier 103 of P4.

つまり、変速伝動装置Ａは、エンジン１からの駆動力を無段変速装置１０のポンプ軸１１に入力してこの無段変速装置１０によって正回転方向や逆回転方向の駆動力に変換するとともに正回転方向においても逆回転方向においても無段階に変速し、無段変速装置１０のモータ軸１２からの出力を第１入力軸１２１などによって遊星伝動部Ｐの第１遊星伝動機構Ｐ１のサンギヤ３１に入力し、無段変速装置１０による変速作用を受けないエンジン駆動力を無段変速装置１０のポンプ軸１１から第２入力軸１２３によって取り出して伝動軸１２４などによって遊星伝動部Ｐの第１遊星伝動機構Ｐ１のリングギヤ３４及び第２遊星伝動機構Ｐ２のキャリヤ４３に入力し、無段変速装置１０による変速作用を受けた駆動力と、無段変速装置１０による変速作用を受けていない駆動力とを遊星伝動部Ｐの第１遊星伝動機構Ｐ１、第２遊星伝動機構Ｐ２、第３遊星伝動機構Ｐ３によって合成し、遊星伝動部Ｐからの合成駆動力をクラッチ部Ｃから第４遊星伝動機構Ｐ４に入力し、第４遊星伝動機構Ｐ４のキャリヤ１０３から連動筒軸１３４、伝動ギヤ１３３を介して伝動ギヤ１３２に伝達して出力軸３から前後進切り換え装置２０の入力軸２１に伝達する。 That is, the transmission device A inputs the driving force from the engine 1 to the pump shaft 11 of the continuously variable transmission 10 and converts it into a driving force in the forward rotation direction or the reverse rotation direction by the continuously variable transmission 10. The speed is continuously variable in both the rotational direction and the reverse rotational direction, and the output from the motor shaft 12 of the continuously variable transmission 10 is transferred to the sun gear 31 of the first planetary transmission mechanism P1 of the planetary transmission unit P by the first input shaft 121 or the like. The engine driving force that is input and not subjected to the shifting action by the continuously variable transmission 10 is extracted from the pump shaft 11 of the continuously variable transmission 10 by the second input shaft 123 and is transmitted to the first planetary transmission portion P of the planetary transmission portion P by the transmission shaft 124 or the like. The driving force input to the ring gear 34 of the mechanism P1 and the carrier 43 of the second planetary transmission mechanism P2 and subjected to the shifting action by the continuously variable transmission 10 and the continuously variable transmission 10 The driving force not subjected to the speed action is synthesized by the first planetary transmission mechanism P1, the second planetary transmission mechanism P2, and the third planetary transmission mechanism P3 of the planetary transmission unit P, and the combined driving force from the planetary transmission unit P is clutched. Part C is input to the fourth planetary transmission mechanism P4, transmitted from the carrier 103 of the fourth planetary transmission mechanism P4 to the transmission gear 132 via the interlocking cylindrical shaft 134 and the transmission gear 133, and from the output shaft 3 to the forward / reverse switching device 20 To the input shaft 21.

すなわち、図７に第１〜第４クラッチＣ１，Ｃ２，Ｃ３，Ｃ４及びブレーキＢＧの操作状態と、変速伝動装置Ａの速度レンジとの関係を示し、図６に変速伝動装置Ａの速度レンジと、無段変速装置１０の変速状態と、出力速度（出力軸３の回転速度）の関係を示すように、変速伝動装置Ａは、無段変速装置１０が変速操作され、かつ、各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４及びブレーキＢＧが入り状態と切り状態に適切に切り換え操作されることにより、無段変速装置１０の変速状態、各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４及びブレーキＢＧの操作状態に対応した回転速度の出力を出力軸３から出力する。 That is, FIG. 7 shows the relationship between the operating states of the first to fourth clutches C1, C2, C3, and C4 and the brake BG and the speed range of the transmission gear A, and FIG. In order to show the relationship between the speed change state of the continuously variable transmission 10 and the output speed (the rotational speed of the output shaft 3), the transmission transmission A is operated by the continuously variable transmission 10 and each clutch C1, C2, C3, C4 and brake BG are appropriately switched between the on state and the off state, thereby responding to the shifting state of continuously variable transmission 10 and the operating states of clutches C1, C2, C3, C4 and brake BG. The output of the rotation speed is output from the output shaft 3.

つまり、変速伝動装置Ａは、図７に示す如く各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４及びブレーキＢＧが入り状態と切り状態に切り換え操作されることにより、１速レンジから４速レンジの４段階の速度レンジに切り換わり、図６に示す如く各速度レンジにおいて、無段変速装置１０が逆回転伝動状態での最高速度（−ｍａｘ）と、正回転伝動状態での最高速度（＋ｍａｘ）との間で変速操作されることにより、出力軸３の回転速度を無段階に変更する。
尚、図６に示す横軸の「０」は、無段変速装置１０の中立状態を示す。図７に示す「入り」は、各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４、ブレーキＢＧの入り状態を示し、「−」は、各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４、ブレーキＢＧの切り状態を示す。 That is, as shown in FIG. 7, the transmission C is operated by switching the clutches C1, C2, C3, and C4 and the brake BG between the on state and the disengaged state. As shown in FIG. 6, between each speed range, the continuously variable transmission 10 is between the maximum speed (−max) in the reverse rotation transmission state and the maximum speed (+ max) in the forward rotation transmission state. As a result of the speed change operation, the rotation speed of the output shaft 3 is changed steplessly.
Note that “0” on the horizontal axis shown in FIG. 6 indicates a neutral state of the continuously variable transmission 10. “On” shown in FIG. 7 indicates the engaged state of each of the clutches C1, C2, C3, and C4 and the brake BG, and “−” indicates the disconnected state of each of the clutches C1, C2, C3, C4, and the brake BG.

図１に示すように、前記前後進切り換え装置２０は、前記入力軸２１に入力側回転部材２３ａが一体回転自在に連結された前進クラッチ２３、前記入力軸２１に入力ギヤ２４ａが一体回転自在に連結されている後進ギヤ機構２４、この後進ギヤ機構２４の出力ギヤ２４ｂに入力側回転部材２５ａが一体回転自在に連結されている後進クラッチ２５、前進クラッチ２３及び後進クラッチ２５の出力側回転部材に回転伝動体２６を介して一体回転自在に連結された前記出力軸２２を備えて構成してある。 As shown in FIG. 1, the forward / reverse switching device 20 includes a forward clutch 23 in which an input side rotation member 23a is connected to the input shaft 21 so as to be integrally rotatable, and an input gear 24a that is integrally rotatable to the input shaft 21. To the reverse gear mechanism 24 connected, and to the output gear 24b of the reverse gear mechanism 24, the input side rotary member 25a is connected to the reverse clutch 25, the forward clutch 23 and the output side rotary member of the reverse clutch 25 so as to be integrally rotatable. The output shaft 22 is connected via a rotary transmission 26 so as to be integrally rotatable.

つまり、前後進切り換え装置１０は、前進クラッチ２３が入り状態に切り換え操作されることにより、変速伝動装置Ａの出力軸３からの出力を前進駆動力に変換して出力軸２２から後輪差動機構４及び前輪差動機構７に伝達し、後進クラッチ２５が入り状態に切り換え操作されることにより、変速伝動装置Ａの出力軸３からの出力を後進駆動力に変換して出力軸２２から後輪差動機構４及び前輪差動機構７に伝達する。 That is, the forward / reverse switching device 10 converts the output from the output shaft 3 of the transmission gearbox A into the forward driving force by switching the forward clutch 23 to the engaged state, and converts the output from the output shaft 22 to the rear wheel differential. By transmitting to the mechanism 4 and the front wheel differential mechanism 7 and switching the reverse clutch 25 to the engaged state, the output from the output shaft 3 of the transmission gearbox A is converted into the reverse drive force, and the rear from the output shaft 22 This is transmitted to the wheel differential mechanism 4 and the front wheel differential mechanism 7.

前記変速伝動装置Ａについてさらに詳述すると、この変速伝動装置Ａにおける前記遊星伝動部Ｐ、クラッチ部Ｃ、第４遊星伝動機構Ｐ４、ブレーキＢＧは、図２−５に示す如く構成してある。 The transmission gear transmission A will be described in further detail. The planetary transmission portion P, the clutch portion C, the fourth planetary transmission mechanism P4, and the brake BG in the transmission transmission device A are configured as shown in FIG.

ミッションケース１４０の一対の支持部１４１に回転自在に支持された前記伝動軸１２４、及び、この伝動軸１２４の軸芯に沿う方向に並べて伝動軸１２４に回転自在に外嵌された支持筒１３５、前記第１伝動筒軸１２６、前記第２伝動筒軸１３０、前記連動筒軸１３４をミッションケース１４０の内部に設け、第１遊星伝動機構Ｐ１のサンギヤ３１を、前記支持筒１３５にスプライン係合によって一体回転自在に連結した状態で支持させ、第１遊星伝動機構Ｐ１のキャリヤ３３を、前記支持筒１３５にベアリング１４２を介して相対回転自在に支持させてある。前記支持筒１３５に伝動ギヤ１４３を一体回転自在に連設し、この伝動ギヤ１４３に噛合った伝動ギヤ１４４を前記第１入力軸１２１に一体回転自在に設けてあり、無段変速装置１０のモータ軸１２から出力され、前記第１入力軸１２１によってミッションケース１４０に入力された駆動力が伝動ギヤ１４４，１４３及び支持筒１３５によって第１遊星伝動機構Ｐ１のサンギヤ３１に入力される。 The transmission shaft 124 rotatably supported by a pair of support portions 141 of the transmission case 140, and a support cylinder 135 that is rotatably fitted to the transmission shaft 124 in a direction along the axis of the transmission shaft 124, The first transmission cylinder shaft 126, the second transmission cylinder shaft 130, and the interlocking cylinder shaft 134 are provided inside the transmission case 140, and the sun gear 31 of the first planetary transmission mechanism P1 is engaged with the support cylinder 135 by spline engagement. The carrier 33 of the first planetary transmission mechanism P1 is supported in a state of being connected so as to be integrally rotatable, and is supported on the support cylinder 135 through a bearing 142 so as to be relatively rotatable. A transmission gear 143 is connected to the support cylinder 135 so as to be integrally rotatable, and a transmission gear 144 meshed with the transmission gear 143 is provided to be integrally rotatable on the first input shaft 121. The driving force output from the motor shaft 12 and input to the transmission case 140 by the first input shaft 121 is input to the sun gear 31 of the first planetary transmission mechanism P1 by the transmission gears 144 and 143 and the support cylinder 135.

第２遊星伝動機構Ｐ２のキャリヤ４３を、前記支持筒１３５と前記第１伝動筒軸１２６の間で前記伝動軸１２４にスプライン係合によって一体回転自在に連結した状態で支持させてある。前記伝動軸１２４の端部に伝動ギヤ１４５をスプライン係合によって一体回転自在に係合した状態で設け、この伝動ギヤ１４５に噛合った伝動ギヤ１４６を前記第２入力軸１２３に一体回転自在に設けてあり、無段変速装置１０のポンプ軸１１から第２入力軸１２３によって取り出されてミッションケース１４０に入力されたエンジン駆動力が伝動ギヤ１４６，１４５及び伝動軸１２４によって第２遊星伝動機構Ｐ２のキャリヤ４３、及び、第１遊星伝動機構Ｐ１のリングギヤ３４に入力される。 The carrier 43 of the second planetary transmission mechanism P2 is supported between the support cylinder 135 and the first transmission cylinder shaft 126 in a state of being connected to the transmission shaft 124 so as to be integrally rotatable by spline engagement. A transmission gear 145 is provided at the end portion of the transmission shaft 124 so as to be integrally rotated by spline engagement, and the transmission gear 146 engaged with the transmission gear 145 is integrally rotatable with the second input shaft 123. The engine driving force taken out from the pump shaft 11 of the continuously variable transmission 10 by the second input shaft 123 and input to the transmission case 140 is transmitted to the second planetary transmission mechanism P2 by the transmission gears 146, 145 and the transmission shaft 124. To the carrier 43 and the ring gear 34 of the first planetary transmission mechanism P1.

第１クラッチＣ１の前記出力側回転部材６２と、第２クラッチＣ２の前記出力側回転部材７２とは、単一の部品になるように一体形成してある。第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２は、この出力側回転部材６２，７２の内部に連設された取付け筒部１４７を介して前記第１伝動筒軸１２６に相対回転自在に支持させてある。第１クラッチＣ１の前記入力側回転部材６１と、第２クラッチＣ２の前記入力側回転部材７１とは、伝動軸１２４の軸芯に沿う方向に並べた状態で第１クラッチＣ１の出力側回転部材６２の内側と、第２クラッチＣ２の出力側回転部材７２の内側とに分散させて配置してある。第１クラッチＣ１の入力側回転部材６１は、前記第１伝動筒軸１２６にベアリング１４８を介して相対回転自在に支持させてある。第１クラッチＣ１と第３遊星伝動機構Ｐ３の間を通るように配置した円板状の前記連動部材１２７の一端側を第３遊星伝動機構Ｐ３のリングギヤ５４に連結し、前記連動部材１２７の他端側を第１クラッチＣ１の入力側回転部材６１に連結してあり、第１クラッチＣ１の入力側回転部材６１が、前記連動部材１２７によって第３遊星伝動機構Ｐ３のリングギヤ５４に一体回転自在に連動されている。 The output side rotation member 62 of the first clutch C1 and the output side rotation member 72 of the second clutch C2 are integrally formed so as to be a single component. The output-side rotating members 62 and 72 of the first clutch C1 and the second clutch C2 are relative to the first transmission cylinder shaft 126 via an attachment cylinder portion 147 that is continuously provided inside the output-side rotating members 62 and 72. It is supported rotatably. The input-side rotation member 61 of the first clutch C1 and the input-side rotation member 71 of the second clutch C2 are arranged in a direction along the axis of the transmission shaft 124, and the output-side rotation member of the first clutch C1. 62 and distributed inside the output side rotation member 72 of the second clutch C2. The input side rotation member 61 of the first clutch C1 is supported on the first transmission cylinder shaft 126 via a bearing 148 so as to be relatively rotatable. One end side of the disk-like interlocking member 127 arranged so as to pass between the first clutch C1 and the third planetary transmission mechanism P3 is connected to the ring gear 54 of the third planetary transmission mechanism P3. The end side is connected to the input side rotating member 61 of the first clutch C1, and the input side rotating member 61 of the first clutch C1 is integrally rotatable with the ring gear 54 of the third planetary transmission mechanism P3 by the interlocking member 127. It is linked.

第２クラッチＣ２の入力側回転部材７１は、前記第１伝動筒軸１２６の端部にスプライン係合によって一体回転自在に連結した状態で支持させてある。第２遊星伝動機構Ｐ２及び第３遊星伝動機構Ｐ３のサンギヤ４１，５１は、第１伝動筒軸１２６の他方の端部に一体回転自在に連結した状態で支持されており、第２クラッチＣ２の入力側回転部材７１が、第１伝動筒軸１２６によって第２遊星伝動機構Ｐ２のサンギヤ４１と、第３遊星伝動機構Ｐ３のサンギヤ５１とのそれぞれに一体回転自在に連動されている。 The input side rotation member 71 of the second clutch C2 is supported in a state of being connected to the end of the first transmission cylinder shaft 126 so as to be integrally rotatable by spline engagement. The sun gears 41 and 51 of the second planetary transmission mechanism P2 and the third planetary transmission mechanism P3 are supported in a state of being connected to the other end of the first transmission cylindrical shaft 126 so as to be integrally rotatable, and the second gear C2 The input side rotation member 71 is interlocked to the sun gear 41 of the second planetary transmission mechanism P2 and the sun gear 51 of the third planetary transmission mechanism P3 by the first transmission cylinder shaft 126 so as to be integrally rotatable.

第３クラッチＣ３の前記出力側回転部材８２と、第４クラッチＣ４の前記出力側回転部材９２とは、単一の部品になるように一体形成してある。第３クラッチＣ３及び第４クラッチＣ４の出力側回転部材８２，９２は、この出力側回転部材８２，９２の内部に連設された取付け筒部１４９を介して前記第２伝動筒軸１３０の中間部に相対回転自在に支持させてある。第３クラッチＣ３の前記入力側回転部材８１と、第４クラッチＣ４の前記入力側回転部材９１とは、伝動軸１２４の軸芯に沿う方向に並べた状態で第３クラッチＣ３の出力側回転部材８２の内側と、第４クラッチＣ４の出力側回転部材９２の内側とに分散させて配置してある。第３クラッチＣ３の入力側回転部材８１は、前記第２伝動筒軸１３０にベアリング１５０を介して相対回転自在に支持させてある。第２クラッチＣ２と第３クラッチＣ３の間を通るように配置した円筒状の前記連動部材１２８の一端側を、第１遊星伝動機構Ｐ１のキャリヤ３３、第２遊星伝動機構Ｐ２のリングギヤ４４、第３遊星伝動機構Ｐ３のキャリヤ５３を連動させている前記連動部材１２５の端部に連結し、前記連動部材１２８の他端側を、第３クラッチＣ３の入力側回転部材８１に連結してあり、第３クラッチＣ３の入力側回転部材８１が、連動部材１２８と連動部材１２５によって第１遊星伝動機構Ｐ１のキャリヤ３３、第２遊星伝動機構Ｐ２のリングギヤ４４、第３遊星伝動機構Ｐ３のキャリヤ５３のそれぞれに一体回転自在に連動されている。 The output side rotation member 82 of the third clutch C3 and the output side rotation member 92 of the fourth clutch C4 are integrally formed so as to be a single component. The output-side rotating members 82 and 92 of the third clutch C3 and the fourth clutch C4 are intermediate between the second transmission cylinder shaft 130 via an attachment cylinder portion 149 that is continuously provided inside the output-side rotating members 82 and 92. The part is supported so as to be relatively rotatable. The input side rotation member 81 of the third clutch C3 and the input side rotation member 91 of the fourth clutch C4 are arranged in a direction along the axis of the transmission shaft 124, and the output side rotation member of the third clutch C3. 82 and distributed inside the output side rotation member 92 of the fourth clutch C4. The input side rotation member 81 of the third clutch C3 is supported by the second transmission cylinder shaft 130 via a bearing 150 so as to be relatively rotatable. One end side of the cylindrical interlocking member 128 disposed so as to pass between the second clutch C2 and the third clutch C3 is connected to the carrier 33 of the first planetary transmission mechanism P1, the ring gear 44 of the second planetary transmission mechanism P2, the first A third planetary transmission mechanism P3 is connected to the end of the interlocking member 125 that is interlocked with the carrier 53, and the other end of the interlocking member 128 is connected to the input side rotating member 81 of the third clutch C3; The input side rotating member 81 of the third clutch C3 is connected to the carrier 33 of the first planetary transmission mechanism P1, the ring gear 44 of the second planetary transmission mechanism P2, and the carrier 53 of the third planetary transmission mechanism P3 by the interlocking member 128 and the interlocking member 125. They are linked to each other so that they can rotate together.

第４クラッチＣ４の入力側回転部材９１を、第２伝動筒軸１３０の端部にスプライン係合によって一体回転自在に連結するようにして支持させてある。第２クラッチＣ２の出力側回転部材７１の端部に、この出力側回転部材７１の周方向での複数箇所に位置する係入凹部１５１ａを備えた係止連動部１５１を設け、この係止連動部１５１の前記各係入凹部１５１ａに外周側が係合爪によって係入するように構成した円板状の前記伝動部材１２９の内周側を、前記第２伝動筒軸１３０の一端側にスプライン係合によって一体回転自在に連結してあり、第１クラッチＣ１及び第２クラッチＣ２の出力側回転部材６２，７２が、前記伝動部材１２９によって第２伝動筒軸１３０に一体回転自在に連結されている。これにより、第４クラッチＣ４の入力側回転部材９１が、第３伝動筒軸１３０と前記伝動部材１２９によって第１クラッチＣ１の出力側回転部材６２、第２クラッチＣ２の出力側回転部材７２のそれぞれに一体回転自在に連結されている。 The input side rotation member 91 of the fourth clutch C4 is supported so as to be connected to the end of the second transmission cylinder shaft 130 so as to be integrally rotatable by spline engagement. At the end of the output-side rotating member 71 of the second clutch C2, a locking interlocking portion 151 having engaging recesses 151a located at a plurality of locations in the circumferential direction of the output-side rotating member 71 is provided. The inner peripheral side of the disk-shaped transmission member 129 configured so that the outer peripheral side is engaged with the engaging recesses 151a of the portion 151 by the engaging claws is connected to one end side of the second transmission cylindrical shaft 130 by the spline. The output side rotation members 62 and 72 of the first clutch C1 and the second clutch C2 are connected to the second transmission cylinder shaft 130 by the transmission member 129 so as to be integrally rotatable. . As a result, the input side rotation member 91 of the fourth clutch C4 is connected to the output side rotation member 62 of the first clutch C1 and the output side rotation member 72 of the second clutch C2 by the third transmission cylinder shaft 130 and the transmission member 129, respectively. Are connected to each other in a rotatable manner.

第４遊星伝動機構Ｐ４のサンギヤ１０１は、第３伝動筒軸１３０の端部に一体形成されており、第３伝動筒軸１３０と、前記伝動部材１２９とによって第１クラッチＣ１の出力側回転部材６２、第２クラッチＣ２の出力側回転部材７２のそれぞれに一体回転自在に連結されている。 The sun gear 101 of the fourth planetary transmission mechanism P4 is integrally formed at the end of the third transmission cylindrical shaft 130, and the output side rotating member of the first clutch C1 is constituted by the third transmission cylindrical shaft 130 and the transmission member 129. 62, and is connected to each of the output side rotation members 72 of the second clutch C2 so as to be integrally rotatable.

第４クラッチＣ４の出力側回転部材９２の端部に、この出力側回転部材９２の周方向での複数箇所に位置する係入凹部１５２ａを備えた係止連動部１５２を設け、この係止連動部１５２の前記各係入凹部１５２ａに係合爪によって係入するように構成した連結部１５３を第４遊星伝動機構Ｐ４のキャリヤ１０３に設けてあり、第４遊星伝動機構Ｐ４のキャリヤ１０３は、第４クラッチＣ４の出力側回転部材９２に一体回転自在に係止連動され、これによって第３クラッチＣ３の出力側回転部材８２にも一体回転自在に連動されている。 At the end of the output side rotating member 92 of the fourth clutch C4, there are provided locking interlocking portions 152 provided with engaging recesses 152a located at a plurality of locations in the circumferential direction of the output side rotating member 92. A connecting portion 153 configured to engage with each engaging recess 152a of the portion 152 by an engaging claw is provided in the carrier 103 of the fourth planetary transmission mechanism P4, and the carrier 103 of the fourth planetary transmission mechanism P4 is The output side rotating member 92 of the fourth clutch C4 is interlocked and interlocked with the output side rotating member 92, so that the output side rotating member 82 of the third clutch C3 is also interlocked with the output side rotating member 82 so as to be integrally rotatable.

ブレーキＢＧの前記可動側ブレーキ体１１１は、ベアリング１５４、第４遊星伝動機構Ｐ４のキャリヤ１０３を前記出力軸３に連動させている前記連動筒軸１３４を介して前記伝動軸１２４に相対回転自在に支持されている。ブレーキＢＧの前記固定側ブレーキ体１１２は、取付け筒部１１２ａで前記連動筒軸１３４に相対回転自在に支持されている。この固定側ブレーキ体１１２は、ミッションケース１４０の壁面に固定されたストッパー１５５に係止されて回り止めされている。 The movable brake body 111 of the brake BG is rotatable relative to the transmission shaft 124 via the interlocking cylindrical shaft 134 that interlocks the bearing 154 and the carrier 103 of the fourth planetary transmission mechanism P4 with the output shaft 3. It is supported. The fixed brake body 112 of the brake BG is supported by the interlocking cylinder shaft 134 so as to be relatively rotatable by an attachment cylinder portion 112a. The fixed-side brake body 112 is locked by a stopper 155 fixed to the wall surface of the mission case 140 and stopped.

前記第１クラッチＣ１、第２クラッチＣ２、第３クラッチＣ３、第４クラッチＣ４のそれぞれは、出力側回転部材６２，７２，８２，９２の内部に設けた油圧ピストン６４，７４，８４，９４によって入り状態と切り状態に切り換え操作されるように油圧クラッチに構成してある。前記ブレーキＢＧは、固定側ブレーキ体１１２の内部に設けた油圧ピストン１１４によって入り状態と切り状態に切り換え操作されるように油圧ブレーキに構成してある。 The first clutch C1, the second clutch C2, the third clutch C3, and the fourth clutch C4 are respectively provided by hydraulic pistons 64, 74, 84, and 94 provided inside the output side rotating members 62, 72, 82, and 92. The hydraulic clutch is configured to be switched between the on state and the off state. The brake BG is configured as a hydraulic brake so as to be switched between the on state and the off state by a hydraulic piston 114 provided in the fixed brake body 112.

前記各クラッチＣ１，Ｃ２，Ｃ３，Ｃ４の油圧ピストン６４，７４，８４，９４、前記ブレーキＢＧの油圧ピストン１１４は、出力側回転部材６２，７２，８２，９２の前記取付け筒部１４７，１４９や連動筒軸１３４、前記第１伝動筒軸１２６や前記第２伝動筒軸１３０、前記伝動軸１２４に穿設した操作油路１５６を介して油圧が供給や排出されることにより、クラッチやブレーキの入り側や切り側に操作されるように構成してある。 The hydraulic pistons 64, 74, 84, 94 of the clutches C1, C2, C3, C4 and the hydraulic piston 114 of the brake BG are connected to the mounting cylinder portions 147, 149 of the output side rotating members 62, 72, 82, 92, The hydraulic pressure is supplied and discharged through the operation oil passage 156 formed in the interlocking cylinder shaft 134, the first transmission cylinder shaft 126, the second transmission cylinder shaft 130, and the transmission shaft 124, so that the clutch and brake It is configured to be operated on the entry side or the cut side.

トラクタの走行用伝動装置の線図Diagram of tractor travel transmission 主変速装置の断面図Cross section of main transmission 遊星伝動部の断面図Cross section of planetary transmission section クラッチ部の断面図Cross section of clutch 第４遊星伝動機構、ブレーキの断面図Cross section of the fourth planetary transmission mechanism and brake 無段変速装置の変速状態、速度レンジ、出力速度の関係を示す説明図Explanatory drawing which shows the relationship between the speed change state, speed range, and output speed of the continuously variable transmission 速度レンジ、クラッチ及びブレーキの操作状態の関係を示す説明図Explanatory diagram showing the relationship between speed range, clutch and brake operation states

３出力軸
１０無段変速装置
３３第１遊星伝動機構のキャリヤ
３４第１遊星伝動機構のリングギヤ
４１第２遊星伝動機構のサンギヤ
４４第２遊星伝動機構のリングギヤ
５１第３遊星伝動機構のサンギヤ
５３第３遊星伝動機構のキャリヤ
５４第３遊星伝動機構のリングギヤ
６１第１クラッチの入力側回転部材
６２第１クラッチの出力側回転部材
７１第２クラッチの入力側回転部材
７２第２クラッチの出力側回転部材
８１第３クラッチの入力側回転部材
８２第３クラッチの出力側回転部材
９１第４クラッチの入力側回転部材
９２第４クラッチの出力側回転部材
１０３第４遊星伝動機構のキャリヤ
１０４第４遊星伝動機構のリングギヤ
１１１可動側ブレーキ体
１２４伝動軸
１２６第１伝動筒軸
１２７連動部材
１２８連動部材
１２９伝動部材
１３０第２伝動筒軸
１５１、１５２係止連動部
ＢＧブレーキ
Ｃクラッチ部
Ｃ１第１クラッチ
Ｃ２第２クラッチ
Ｃ３第３クラッチ
Ｃ４第４クラッチ
Ｐ遊星伝動部
Ｐ１第１遊星伝動機構
Ｐ２第２遊星伝動機構
Ｐ３第３遊星伝動機構
Ｐ４第４遊星伝動機構
3 Output shaft 10 continuously variable transmission 33 carrier of first planetary transmission mechanism
34 Ring gear 41 of the first planetary transmission mechanism 41 Sun gear 44 of the second planetary transmission mechanism 44 Ring gear of the second planetary transmission mechanism
51 Sun gear 53 of the third planetary transmission mechanism 53 Carrier 54 of the third planetary transmission mechanism Ring gear 61 of the third planetary transmission mechanism 61 Input-side rotation member 62 of the first clutch Output-side rotation member 71 of the first clutch Input-side rotation of the second clutch Member 72 output side rotation member 81 of the second clutch input side rotation member 82 of the third clutch output side rotation member 91 of the third clutch input side rotation member 92 of the fourth clutch output side rotation member 103 of the fourth clutch fourth planet Carrier 104 of transmission mechanism Ring gear 111 of fourth planetary transmission mechanism Movable brake body 124 Transmission shaft 126 First transmission cylinder shaft
127 interlocking member
128 interlocking member 129 Den dynamic member 130 second transmission cylinder shaft 151 engaging interlocking portion BG brake C clutch portion C1 first clutch C2 second clutch C3 the third clutch C4 fourth clutch P planetary transmission section P1 first planetary transmission Mechanism P2 Second planetary transmission mechanism P3 Third planetary transmission mechanism P4 Fourth planetary transmission mechanism

Claims

エンジン駆動力が入力される無段変速装置、前記無段変速装置からの出力と、前記無段変速装置による変速作用を受けないエンジン駆動力とを第１遊星伝動機構、第２遊星伝動機構、第３遊星伝動機構によって合成する遊星伝動部、前記遊星伝動部から合成駆動力を入力するとともに第１クラッチ、第２クラッチ、第３クラッチ、第４クラッチを備えたクラッチ部、前記クラッチ部から入力する第４遊星伝動機構、前記第４遊星伝動機構のリングギヤに作用するブレーキを備え、前記無段変速装置が変速操作され、かつ、前記各クラッチ及び前記ブレーキが入り状態と切り状態に切り換え操作されることにより、無段変速装置の変速状態、各クラッチ及びブレーキの操作状態に対応した回転速度の出力を前記第４遊星伝動機構に連動された出力軸から出力する変速伝動装置であって、
前記無段変速装置による変速作用を受けないエンジン駆動力を前記第１遊星伝動機構のリングギヤに伝達する伝動軸の軸芯方向に並べて前記伝動軸に相対回転自在に外嵌させた第１伝動筒軸と第２伝動筒軸を備え、
前記第２遊星伝動機構及び前記第３遊星伝動機構のサンギヤと、前記第２クラッチの入力側回転部材とを前記第１伝動筒軸に一体回転自在に支持させ、
前記第１クラッチの入力側回転部材を、前記第２クラッチの入力側回転部材と前記伝動軸の軸芯に沿う方向に並べて前記第１伝動筒軸に相対回転自在に支持させるとともに、前記第1クラッチの入力側回転部材に前記第３遊星伝動機構のリングギヤを連動させる連動部材を、前記第１クラッチと前記第３遊星伝動機構の間を通る状態に配置し、
前記第1クラッチ及び前記第２クラッチの出力側回転部材を前記第２伝動筒軸に連動させるとともに、前記第４クラッチの入力側回転部材を前記第２伝動筒軸に一体回転自在に支持させ、
前記第３クラッチの入力側回転部材を、前記第４クラッチの入力側回転部材と前記伝動軸の軸芯に沿う方向に並べて前記第２伝動筒軸に相対回転自在に支持させるとともに、前記第３クラッチの入力側回転部材に前記第1遊星伝動機構のキャリヤ、前記第２遊星伝動機構のリングギヤ、前記第３遊星伝動機構のキャリヤを連動させる連動部材を、前記第２クラッチと前記第３クラッチの間を通る状態に配置し、
前記第３クラッチの出力側回転部材と、前記第４クラッチの出力側回転部材とを一体形成し、第４クラッチの前記出力側回転部材に、前記第４遊星伝動機構のキャリヤに対して係止して連動する係止連動部を設けてある変速伝動装置。 A continuously variable transmission to which an engine driving force is input, an output from the continuously variable transmission, and an engine driving force that is not subjected to a shifting action by the continuously variable transmission include a first planetary transmission mechanism, a second planetary transmission mechanism, A planetary transmission unit that is combined by a third planetary transmission mechanism, a combined drive force is input from the planetary transmission unit, and a clutch unit that includes a first clutch, a second clutch, a third clutch, and a fourth clutch is input from the clutch unit. A fourth planetary transmission mechanism, a brake acting on a ring gear of the fourth planetary transmission mechanism, the continuously variable transmission is operated to change gears, and the clutches and the brakes are operated to be switched between on and off. As a result, the output of the rotational speed corresponding to the shifting state of the continuously variable transmission and the operating state of each clutch and brake is output in conjunction with the fourth planetary transmission mechanism. A speed change transmission apparatus to be output from the axis,
A first transmission cylinder that is lined up in the axial direction of the transmission shaft that transmits engine driving force that is not subjected to a speed change effect by the continuously variable transmission to the ring gear of the first planetary transmission mechanism, and is fitted around the transmission shaft so as to be relatively rotatable. A shaft and a second transmission cylinder shaft,
A sun gear of the second planetary transmission mechanism and the third planetary transmission mechanism, and an input side rotation member of the second clutch are supported on the first transmission cylinder shaft so as to be integrally rotatable,
The input side rotation member of the first clutch is arranged in a direction along the axis of the transmission side of the input clutch of the second clutch and the shaft of the transmission shaft, and is supported by the first transmission cylinder shaft so as to be relatively rotatable. An interlocking member for interlocking the ring gear of the third planetary transmission mechanism with the input side rotation member of the clutch is disposed so as to pass between the first clutch and the third planetary transmission mechanism,
The output side rotation member of the first clutch and the second clutch is interlocked with the second transmission cylinder shaft, and the input side rotation member of the fourth clutch is supported on the second transmission cylinder shaft so as to be integrally rotatable.
The input side rotating member of the third clutch is arranged in a direction along the axis of the transmission shaft of the fourth clutch and the shaft of the transmission shaft, and is supported by the second transmission cylinder shaft so as to be relatively rotatable. An interlocking member that interlocks the carrier of the first planetary transmission mechanism, the ring gear of the second planetary transmission mechanism, and the carrier of the third planetary transmission mechanism with the input side rotation member of the clutch, and the second clutch and the third clutch. Place it in a state that passes between ,
The output side rotation member of the third clutch and the output side rotation member of the fourth clutch are integrally formed, and the output side rotation member of the fourth clutch is locked to the carrier of the fourth planetary transmission mechanism. A shift transmission device provided with a locking interlocking portion that interlocks with each other .

前記第１クラッチの前記出力側回転部材と、前記第２クラッチの前記出力側回転部材とを一体形成し、第２クラッチの出力側回転部材の係止連動部に一端側が一体回動自在に係止され、他端側が前記第２伝動筒軸に連結されて第１及び第２クラッチの出力側回転部材を第２伝動筒軸に連動させている伝動部材を備えてある請求項１記載の変速伝動装置。 The output-side rotating member of the first clutch and the output-side rotating member of the second clutch are integrally formed, and one end side is engaged with the interlocking interlocking portion of the output-side rotating member of the second clutch. 2. The speed change according to claim 1, further comprising: a transmission member that is stopped and has the other end connected to the second transmission cylinder shaft to link the output side rotation members of the first and second clutches to the second transmission cylinder shaft. Transmission device.

前記ブレーキに、前記第４遊星伝動機構のリングギヤに連結された状態で前記伝動軸に相対回転自在に外嵌させた可動側ブレーキ体を備えてある請求項１又は２記載の変速伝動装置。 The speed change transmission apparatus according to claim 1 or 2 , wherein the brake includes a movable brake body externally fitted to the transmission shaft so as to be relatively rotatable in a state of being connected to a ring gear of the fourth planetary transmission mechanism .