JP2010101404A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission capable of reducing the number of clutches and disposing a brake on the radially outer side of the clutches. <P>SOLUTION: This automatic transmission includes first to third planetary gears. A carrier Cf is connected to an input shaft 2, and a carrier Cr is connected to an output gear 3. The automatic transmission further includes a first engaging element C1 connecting a sun gear Sm to the input shaft 2, a second engaging element C2 connecting a second connected body Rm, Sr composed by connecting a ring gear Rm to a sun gear Sr to the input shaft 2 via the carrier Cf, a third engaging element B1 fixing the sun gear Sm to a transmission case 1, a fourth engaging element B2 fixing a first connected body Rf, Cm, Rr composed by connecting a ring gear Rf, a carrier Cm, and a ring gear Rr to the transmission case 1, a fifth engaging element B3 fixing the second connected body Rm, Sr to the transmission case 1, and a sixth engaging element B4 fixing a sun gear Sf to the transmission case 1. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、入力部材の回転を複数段に変速して出力部材に伝達する自動変速機に関する。   The present invention relates to an automatic transmission that shifts the rotation of an input member to a plurality of stages and transmits it to an output member.

従来、入力部材の回転を変速機ケース内に配置した入力用の第１プラネタリギヤと変速用の複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機が知られている（例えば、特許文献１参照）。   2. Description of the Related Art Conventionally, there is known an automatic transmission in which rotation of an input member is shifted to a plurality of stages and transmitted to an output member via a first planetary gear for input disposed in a transmission case and a double planetary gear for shifting ( For example, see Patent Document 1).

特許文献１のものでは、第１プラネタリギヤはシングルピニオン型で構成され、複式プラネタリギヤはシングルピニオン型の第２プラネタリギヤとダブルピニオン型の第３プラネタリギヤとで構成されている。複式プラネタリギヤは、第２プラネタリギヤと第３プラネタリギヤとのリングギヤを同一部材で構成し、第２プラネタリのキャリアが支持するピニオンを第３プラネタリギヤの一対のピニオンの一方に用い、第２プラネタリギヤのキャリアと第３プラネタリギヤのキャリアとを連結して、第２，第３プラネタリギヤでラビニヨ型のプラネタリギヤを構成している。複式プラネタリギヤは、第２プラネタリギヤのサンギヤから成る第１回転要素と、第２，第３プラネタリギヤのキャリアから成る第２回転要素と、第３プラネタリギヤのリングギヤと共通の第２プラネタリギヤのリングギヤから成る第３回転要素と、第３プラネタリギヤのサンギヤから成る第４回転要素とを有する。これら第１から第４回転要素は、速度線図においてギヤ比に対応する間隔を存して順に並ぶ。そして、第３回転要素を出力部材に連結している。   In Patent Document 1, the first planetary gear is constituted by a single pinion type, and the double planetary gear is constituted by a single pinion type second planetary gear and a double pinion type third planetary gear. In the double planetary gear, the ring gears of the second planetary gear and the third planetary gear are constituted by the same member, and the pinion supported by the carrier of the second planetary is used for one of the pair of pinions of the third planetary gear, and the carrier of the second planetary gear and the second planetary gear A Ravigneaux type planetary gear is constituted by connecting the carrier of the three planetary gears and the second and third planetary gears. The compound planetary gear includes a first rotating element composed of a sun gear of the second planetary gear, a second rotating element composed of a carrier of the second and third planetary gears, and a third planetary gear ring gear shared with the ring gear of the third planetary gear. A rotating element and a fourth rotating element comprising a sun gear of a third planetary gear. These first to fourth rotating elements are arranged in order at intervals corresponding to the gear ratio in the velocity diagram. The third rotating element is connected to the output member.

また、係合要素として、第４回転要素に入力部材の回転を第１プラネタリギヤを介して減速して伝達させる状態とこの伝達を断つ状態とに切換自在な第１クラッチと、第２回転要素と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第２クラッチと、第１回転要素に入力部材の回転を第１プラネタリギヤを介して減速して伝達させる状態とこの伝達を断つ状態とに切換自在な第３クラッチと、第３回転要素と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第４クラッチと、第１回転要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第１ブレーキと、第２回転要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第２ブレーキとを備えている。   Further, as the engagement element, a first clutch that can be switched between a state in which the rotation of the input member is decelerated and transmitted to the fourth rotation element via the first planetary gear and a state in which the transmission is cut off, and a second rotation element A second clutch that can be switched between a state in which the input member is connected and a state in which the connection is cut off, a state in which the rotation of the input member is decelerated and transmitted to the first rotating element via the first planetary gear, and the transmission is cut off. A third clutch that can be switched between a state, a fourth clutch that can be switched between a state in which the third rotating element and the input member are connected, and a state in which the connection is broken, and a first rotating element that is fixed to the transmission case. A first brake which can be switched between a state and a state where the fixing is released, and a second brake which can be switched between a state where the second rotating element is fixed to the transmission case and a state where the fixing is released. .

以上の構成によれば、第１クラッチと第２ブレーキとを係合することで１速段が確立され、第１クラッチと第１ブレーキとを係合することで２速段が確立され、第１クラッチと第３クラッチとを係合することで３速段が確立され、第１クラッチと第２クラッチとを係合することで４速段が確立され、第２クラッチと第４クラッチとを係合することで５速段が確立され、第２クラッチと第３クラッチとを係合することで６速段が確立され、第２クラッチと第１ブレーキとを係合することで７速段が確立される。
特開２００５−５４８２４号公報（第１−３図） According to the above configuration, the first gear is established by engaging the first clutch and the second brake, the second gear is established by engaging the first clutch and the first brake, The third speed is established by engaging the first and third clutches, the fourth speed is established by engaging the first and second clutches, and the second and fourth clutches are engaged. The fifth gear is established by engaging, the sixth gear is established by engaging the second clutch and the third clutch, and the seventh gear is established by engaging the second clutch and the first brake. Is established.
Japanese Patent Laying-Open No. 2005-54824 (FIG. 1-3)

上記従来例のものでは、クラッチが４つ、ブレーキが２つで、ブレーキと比較してクラッチの数が多い。クラッチのピストンは、変速機ケースに設けられるブレーキのピストンと異なり、入力部材たる入力軸上や入力軸を軸支するメインシャフト上等に設けられるものであり、プラネタリギヤの径方向外方に配置することができない。このため、クラッチの数が多いと自動変速機の軸長が長くなるという不具合がある。   In the conventional example, there are four clutches and two brakes, and the number of clutches is larger than that of the brakes. Unlike the brake piston provided on the transmission case, the clutch piston is provided on the input shaft as the input member, the main shaft that supports the input shaft, and the like, and is disposed radially outward of the planetary gear. I can't. For this reason, when there are many clutches, there exists a malfunction that the axial length of an automatic transmission becomes long.

又、ブレーキも自動変速機の構成の関係上、プラネタリギヤの径方向外方に配置できないものもある。   Some brakes cannot be arranged radially outward of the planetary gear because of the configuration of the automatic transmission.

以上の点に鑑み、本発明は、クラッチの数を少なくすると共にブレーキをクラッチの径方向外方に配置することができる自動変速機を提供することを目的とする。   In view of the above points, an object of the present invention is to provide an automatic transmission that can reduce the number of clutches and can dispose a brake radially outward of the clutch.

上記目的を達成するため、本発明の第１の態様は、入力部材の回転を変速機ケース内に配置した入力用の第１プラネタリギヤと変速用の複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、複式プラネタリギヤは、第２と第３の２つのプラネタリギヤで構成され、第１プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第１要素、第２要素及び第３要素とし、第２プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第４要素、第５要素及び第６要素とし、第３プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第７要素、第８要素及び第９要素として、第２要素と第５要素と第７要素とを連結して第１連結体が構成され、第３要素に入力部材が連結され、第６要素と第９要素とを連結して第２連結体が構成されると共に、第８要素が出力部材に連結され、第４要素と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素と、第２連結体と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第２係合要素と、第４要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な３係合要素と、第１連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第４係合要素と、第２連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第５係合要素と、第１要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする。   To achieve the above object, according to a first aspect of the present invention, the rotation of an input member is shifted in a plurality of stages via a first planetary gear for input disposed in a transmission case and a double planetary gear for transmission. An automatic transmission for transmitting to an output member, wherein the compound planetary gear is composed of two second and third planetary gears, and the three elements including the sun gear, the carrier and the ring gear of the first planetary gear are shown in the velocity diagram. The first element, the second element, and the third element are arranged in the order corresponding to the gear ratio, and the three elements including the sun gear, the carrier, and the ring gear of the second planetary gear correspond to the gear ratio in the velocity diagram. The fourth element, the fifth element, and the sixth element are respectively arranged in the order of intervals, and three elements including the sun gear, the carrier, and the ring gear of the third planetary gear are provided. As the seventh element, the eighth element, and the ninth element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram, the first element is configured by connecting the second element, the fifth element, and the seventh element. The input member is connected to the third element, the sixth element and the ninth element are connected to form a second connecting body, the eighth element is connected to the output member, and the fourth element and the input member A first engagement element that can be switched between a state in which the connection is cut off and a state in which the connection is cut off, and a second engagement that is switchable between a state in which the second connecting body and the input member are connected and a state in which the connection is cut off An element, a three-engagement element switchable between a state in which the fourth element is fixed to the transmission case and a state in which this fixing is released, a state in which the first coupling body is fixed to the transmission case, and this fixing is released A fourth engaging element that can be switched between a state and a state in which the second coupling body is fixed to the transmission case. A fifth engagement element that can be switched to a state of releasing the fixation, and a sixth engagement element that can be switched to a state of fixing the first element to the transmission case and a state of releasing the fixation. Features.

本発明の第１の態様によれば、後述する実施形態の説明から明らかなように、第１、第２係合要素たる２つのクラッチと、第３〜第６係合要素たる４つのブレーキで、前進７段の変速を行うことができる。又、第３係合要素を第１係合要素の径方向外方に配置し、第４係合要素を複式プラネタリギヤの径方向外方に配置し、第５係合要素を第２係合要素の径方向外方に配置することができる。従って、従来のものと比較して、クラッチの数を減少させることができると共に、ブレーキをクラッチ又はプラネタリギヤの径方向外方に配置して、自動変速機の軸長を短くすることができる。   According to the first aspect of the present invention, as will be apparent from the description of the embodiments described later, two clutches serving as the first and second engagement elements and four brakes serving as the third to sixth engagement elements. , 7 shifts forward can be performed. Further, the third engagement element is disposed radially outward of the first engagement element, the fourth engagement element is disposed radially outward of the double planetary gear, and the fifth engagement element is disposed in the second engagement element. Can be arranged radially outward. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.

本発明の第２の態様は、入力部材の回転を変速機ケース内に配置した入力用の第１プラネタリギヤと変速用の複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、複式プラネタリギヤは、第２と第３の２つのプラネタリギヤで構成され、第１プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第１要素、第２要素及び第３要素とし、第２プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第４要素、第５要素及び第６要素とし、第３プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第７要素、第８要素及び第９要素として、第１要素が変速機ケースに固定され、第２要素に入力部材が連結され、第５要素と第７要素とを連結して第１連結体が構成され、第６要素と第９要素とを連結して第２連結体が構成されると共に、第８要素が出力部材に連結され、第３要素と第４要素とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素と、第３要素と第２連結体とを連結する状態とこの連結を断つ状態とに切換自在な第２係合要素と、第１連結体と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な３係合要素と、第１連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第４係合要素と、第２連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第５係合要素と、第４要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする。   According to a second aspect of the present invention, an automatic transmission that shifts the rotation of an input member to a plurality of stages via a first planetary gear for input disposed in a transmission case and a double planetary gear for transmission is transmitted to an output member. The compound planetary gear is composed of two planetary gears, a second planetary gear and a third planetary gear comprising a sun gear, a carrier, and a ring gear at intervals corresponding to the gear ratio in the velocity diagram. The first element, the second element, and the third element are arranged in the order of the three elements, and the three elements including the sun gear, the carrier, and the ring gear of the second planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram. The four elements, the fifth element, and the sixth element, and the three elements including the sun gear, the carrier, and the ring gear of the third planetary gear, As the seventh element, the eighth element, and the ninth element, respectively, in order of arrangement at corresponding intervals, the first element is fixed to the transmission case, the input member is connected to the second element, the fifth element, the seventh element, Are connected to each other to form a first connecting body, and the sixth element and the ninth element are connected to form a second connecting body, and the eighth element is connected to the output member, and the third element and the fourth element are connected to each other. A first engagement element that can be switched between a state in which the elements are connected and a state in which the connection is cut off; a second state in which the connection is made between a state in which the third element and the second connection body are connected; The engaging element, three engaging elements that can be switched between a state in which the first connecting body and the input member are connected and a state in which the connection is cut off, a state in which the first connecting body is fixed to the transmission case, and this fixing A fourth engagement element that can be switched to a released state, a state in which the second coupling body is fixed to the transmission case, and this fixed element. A fifth engagement element that can be switched to a state in which the release is released, and a sixth engagement element that is switchable to a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released. And

本発明の第２の態様によれば、後述する実施形態の説明から明らかなように、第１〜第３係合要素たる３つのクラッチと、第４〜第６係合要素たる３つのブレーキで、前進７段の変速を行うことができる。又、第４係合要素を複式プラネタリギヤの径方向外方に配置し、第５係合要素を第２係合要素の径方向外方に配置することができる。従って、従来のものと比較して、クラッチの数を減少させることができると共に、ブレーキをクラッチ又はプラネタリギヤの径方向外方に配置して、自動変速機の軸長を短くすることができる。   According to the second aspect of the present invention, as will be apparent from the description of the embodiment described later, the three clutches as the first to third engagement elements and the three brakes as the fourth to sixth engagement elements. , 7 shifts forward can be performed. In addition, the fourth engagement element can be disposed radially outward of the double planetary gear, and the fifth engagement element can be disposed radially outward of the second engagement element. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.

又、本発明の第１及び第２の態様において、第６要素が第２プラネタリギヤのリングギヤであり、第９要素が第３プラネタリギヤのサンギヤである場合、第３プラネタリギヤを第２プラネタリギヤの径方向外側に配置し、第２プラネタリギヤのリングギヤと第３プラネタリギヤのサンギヤとを一体化して第２連結体を構成すれば、自動変速機の軸長をより短くすることができる。   In the first and second aspects of the present invention, when the sixth element is a ring gear of the second planetary gear and the ninth element is a sun gear of the third planetary gear, the third planetary gear is radially outside of the second planetary gear. The shaft length of the automatic transmission can be made shorter by arranging the ring gear of the second planetary gear and the sun gear of the third planetary gear to form the second coupling body.

又、本発明の第１及び第２の態様において、後進段に於いてのみ係合する、すなわち前進段に於いては常に開放することとなる第４係合要素をドグクラッチで構成すれば、多板クラッチで構成したものと比較して、前進段に於ける多板クラッチの開放に伴うフリクションロスを低減させることができ、伝達効率を向上させることができる。   In the first and second aspects of the present invention, if the fourth engagement element that is engaged only in the reverse gear, that is, is always released in the forward gear, is constituted by a dog clutch. Compared with a plate clutch, the friction loss associated with the release of the multi-plate clutch in the forward gear can be reduced, and the transmission efficiency can be improved.

図１（ａ）は、本発明の自動変速機の第１実施形態を示している。この第１実施形態は、変速機ケース１内に回転自在に軸支した、図外のエンジン等の動力源に連結される入力部材たる入力軸２と、入力軸２と同心に配置された出力部材たる出力ギヤ３とを備えている。出力ギヤ３の回転は、図外のデファレンシャルギヤを介して車両の左右の駆動輪に伝達される。   Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. In the first embodiment, an input shaft 2 that is rotatably supported in a transmission case 1 and that is connected to a power source such as an engine (not shown), and an output that is arranged concentrically with the input shaft 2. And an output gear 3 as a member. The rotation of the output gear 3 is transmitted to the left and right drive wheels of the vehicle via a differential gear (not shown).

又、変速機ケース１内には、入力軸２の周りに位置させて、入力用の第１プラネタリギヤ４と、変速用の複式プラネタリギヤ５とが配置されている。第１プラネタリギヤ４は、サンギヤＳｆと、リングギヤＲｆと、互いに噛合すると共に一方がサンギヤＳｆ、他方がリングギヤＲｆに噛合する一対のピニオンＰｆ，Ｐｆ’を自転及び公転自在に支持するキャリアＣｆとから成るダブルピニオン型のプラネタリギヤで構成されている。   In the transmission case 1, an input first planetary gear 4 and a shift-type planetary gear 5 are arranged around the input shaft 2. The first planetary gear 4 includes a sun gear Sf, a ring gear Rf, and a carrier Cf that meshes with each other and supports a pair of pinions Pf and Pf ′ that mesh with the sun gear Sf and the other mesh with the ring gear Rf so as to rotate and revolve. It is composed of a double pinion type planetary gear.

図２の上段に示す第１プラネタリギヤ４の速度線図を参照して、第１プラネタリギヤ４のサンギヤＳｆ、キャリアＣｆ及びリングギヤＲｆから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第１要素、第２要素及び第３要素とすると、第１要素はサンギヤＳｆ、第２要素はリングギヤＲｆ、第３要素はキャリアＣｆになる。尚、サンギヤＳｆとキャリアＣｆ間の間隔とキャリアＣｆとリングギヤＲｆ間の間隔との比は、第１プラネタリギヤ４のギヤ比をｉ（リングギヤの歯数／サンギヤの歯数）として、ｉ：１に設定される。又、キャリアＣｆは入力軸２に連結されている。尚、速度線図において、下の横線と上の横線は夫々回転速度が「０」と「１」（入力軸２と同じ回転速度）であることを示している。   Referring to the velocity diagram of the first planetary gear 4 shown in the upper part of FIG. 2, three elements including the sun gear Sf, the carrier Cf, and the ring gear Rf of the first planetary gear 4 are separated by a distance corresponding to the gear ratio in the velocity diagram. If the first element, the second element, and the third element are arranged from the left side in the order in which they are arranged, the first element is the sun gear Sf, the second element is the ring gear Rf, and the third element is the carrier Cf. The ratio between the distance between the sun gear Sf and the carrier Cf and the distance between the carrier Cf and the ring gear Rf is set to i: 1 where i is the gear ratio of the first planetary gear 4 (number of teeth of the ring gear / number of teeth of the sun gear). Is set. The carrier Cf is connected to the input shaft 2. In the velocity diagram, the lower horizontal line and the upper horizontal line indicate that the rotational speeds are “0” and “1” (the same rotational speed as the input shaft 2), respectively.

複式プラネタリギヤ５は、第２プラネタリギヤ６と第３プラネタリギヤ７とで構成されている。第２プラネタリギヤ６は、サンギヤＳｍと、リングギヤＲｍと、サンギヤＳｍとリングギヤＲｍとに噛合するピニオンＰｍを自転及び公転自在に支持するキャリアＣｍとから成るシングルピニオン型のプラネタリギヤで構成され、第３プラネタリギヤ７も、サンギヤＳｒと、リングギヤＲｒと、サンギヤＳｒとリングギヤＲｒとに噛合するピニオンＰｒを自転及び公転自在に支持するキャリアＣｒとから成るシングルピニオン型のプラネタリギヤで構成されている。   The compound planetary gear 5 includes a second planetary gear 6 and a third planetary gear 7. The second planetary gear 6 is composed of a single planetary gear comprising a sun gear Sm, a ring gear Rm, and a carrier Cm that supports the pinion Pm meshing with the sun gear Sm and the ring gear Rm so as to rotate and revolve. 7 is also composed of a single pinion type planetary gear comprising a sun gear Sr, a ring gear Rr, and a carrier Cr that supports the pinion Pr meshing with the sun gear Sr and the ring gear Rr so as to rotate and revolve.

図２の下段に示す複式プラネタリギヤ５の速度線図を参照して、第２プラネタリギヤ６のサンギヤＳｍ、キャリアＣｍ及びリングギヤＲｍから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第４要素、第５要素及び第６要素とすると、第４要素はサンギヤＳｍ、第５要素はキャリアＣｍ、第６要素はリングギヤＲｍになる。尚、サンギヤＳｍとキャリアＣｍ間の間隔とキャリアＣｍとリングギヤＲｍ間の間隔との比は、第２プラネタリギヤ６のギヤ比をｊとして、ｊ：１に設定される。   Referring to the speed diagram of the compound planetary gear 5 shown in the lower part of FIG. 2, the three elements including the sun gear Sm, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fourth element is the sun gear Sm, the fifth element is the carrier Cm, and the sixth element is the ring gear Rm. The ratio between the distance between the sun gear Sm and the carrier Cm and the distance between the carrier Cm and the ring gear Rm is set to j: 1 where j is the gear ratio of the second planetary gear 6.

又、上記複式プラネタリギヤ５の速度線図を参照して、第３プラネタリギヤ７のサンギヤＳｒ、キャリアＣｒ及びリングギヤＲｒから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第７要素、第８要素及び第９要素とすると、第７要素はリングギヤＲｒ、第８要素はキャリアＣｒ、第９要素はサンギヤＳｒになる。尚、サンギヤＳｒ（縦線Ｙ４）とキャリアＣｒ（縦線Ｙ３）間の間隔とキャリアＣｒ（縦線Ｙ３）とリングギヤＲｒ（縦線Ｙ２）間の間隔との比は、第３プラネタリギヤ６のギヤ比をｋとして、ｋ：１に設定される。   Further, referring to the velocity diagram of the compound planetary gear 5, the three elements including the sun gear Sr, the carrier Cr and the ring gear Rr of the third planetary gear 7 are arranged in the order corresponding to the gear ratio in the velocity diagram. Assuming that the seventh element, the eighth element, and the ninth element are the left side, the seventh element is the ring gear Rr, the eighth element is the carrier Cr, and the ninth element is the sun gear Sr. The ratio between the distance between the sun gear Sr (vertical line Y4) and the carrier Cr (vertical line Y3) and the distance between the carrier Cr (vertical line Y3) and the ring gear Rr (vertical line Y2) is the gear of the third planetary gear 6. The ratio is set to k: 1, where k is the ratio.

ここで、第１実施形態では、第１プラネタリギヤ４のリングギヤＲｆ（第２要素）と第２プラネタリギヤ６のキャリアＣｍ（第５要素）と第３プラネタリギヤ７のリングギヤＲｒ（第７要素）とを連結して第１連結体Ｒｆ，Ｃｍ，Ｒｒ（縦線Ｙ２）を構成し、第１プラネタリギヤ４のキャリアＣｆ（第３要素）に入力軸２を連結し、第２プラネタリギヤ６のリングギヤＲｍ（第６要素）と第３プラネタリギヤ７のサンギヤＳｒ（第９要素）とを連結して第２連結体Ｒｍ，Ｓｒを構成し、第３プラネタリギヤ７のキャリアＣｒ（第８要素）を出力部材たる出力ギヤ３に連結している。   Here, in the first embodiment, the ring gear Rf (second element) of the first planetary gear 4, the carrier Cm (fifth element) of the second planetary gear 6, and the ring gear Rr (seventh element) of the third planetary gear 7 are coupled. The first coupling bodies Rf, Cm, Rr (vertical line Y2) are configured, the input shaft 2 is coupled to the carrier Cf (third element) of the first planetary gear 4, and the ring gear Rm (sixth sixth) of the second planetary gear 6 is coupled. Element) and the sun gear Sr (the ninth element) of the third planetary gear 7 are connected to form the second connecting body Rm, Sr, and the carrier Cr (the eighth element) of the third planetary gear 7 is the output member 3 serving as an output member. It is linked to.

又、係合要素として、第２プラネタリギヤ６のサンギヤＳｍ（第４要素）と入力軸２とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素たる第１クラッチＣ１と、第２連結体Ｒｍ，Ｓｒと入力軸２とをキャリアＣｆを介して連結する状態とこの連結を断つ状態とに切換自在な第２係合要素たる第２クラッチＣ２と、第２プラネタリギヤ６のサンギヤＳｍ（第４要素）を変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第３係合要素たる第１ブレーキＢ１と、第１連結体Ｒｆ，Ｃｍ，Ｒｒを変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第４係合要素たる第２ブレーキＢ２と、第２連結体Ｒｍ，Ｓｒを変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第５係合要素たる第３ブレーキＢ３と、第１プラネタリギヤのサンギヤＳｆ（第１要素）を変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第６係合要素たる第４ブレーキＢ４とを備えている。   Further, as an engagement element, a first clutch C1 as a first engagement element that can be switched between a state in which the sun gear Sm (fourth element) of the second planetary gear 6 and the input shaft 2 are connected and a state in which the connection is cut off. The second clutch C2, which is a second engagement element that can be switched between a state in which the second connecting bodies Rm, Sr and the input shaft 2 are connected via the carrier Cf and a state in which the connection is cut off, and a second planetary gear 6 A first brake B1, which is a third engagement element that can be switched between a state in which the sun gear Sm (fourth element) is fixed to the transmission case 1 and a state in which the sun gear Sm is released, and a first coupling body Rf, Cm, Rr. A state in which the second brake B2, which is a fourth engagement element that can be switched between a state in which the transmission case 1 is fixed and a state in which the fixation is released, and a state in which the second coupling bodies Rm, Sr are fixed to the transmission case 1 It can be switched to the state of releasing the fixation. The fifth brake B3, which is the fifth engagement element, and the sixth engagement element, which is switchable between a state in which the sun gear Sf (first element) of the first planetary gear is fixed to the transmission case 1 and a state in which the fixation is released. 4 brakes B4.

第１クラッチＣ１と第３ブレーキＢ３とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「１」、第２プラネタリギヤ６のリングギヤＲｍ、第３プラネタリギヤ７のサンギヤＳｒが位置する縦線Ｙ４での回転速度が「０」になり、出力ギヤ３に連結される第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「１ｓｔ」になり、１速段が確立される。   When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the ring gear Rm of the second planetary gear 6, the third planetary gear 7 The rotational speed at the vertical line Y4 where the sun gear Sr is located is “0”, and the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 connected to the output gear 3 is located is “1st”. 1st gear is established.

第３ブレーキＢ３と第４ブレーキＢ４とを係合させると、第１プラネタリギヤ４のサンギヤＳｆ及び第３プラネタリギヤのサンギヤＳｒの回転速度が「０」、第１プラネタリギヤ４のキャリアＣｆの回転速度が「１」になり、第１プラネタリギヤ４のリングギヤＲｆの回転速度及び第３プラネタリギヤ７のリングギヤＲｒ（縦線Ｙ２）の回転速度がＮ１（（ｉ−１）／ｉ）になって、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「２ｎｄ」になり、２速段が確立される。   When the third brake B3 and the fourth brake B4 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 4 and the sun gear Sr of the third planetary gear is “0”, and the rotational speed of the carrier Cf of the first planetary gear 4 is “ 1 ”, the rotation speed of the ring gear Rf of the first planetary gear 4 and the rotation speed of the ring gear Rr (vertical line Y2) of the third planetary gear 7 become N1 ((i−1) / i), and the third planetary gear 7 The rotational speed at the vertical line Y3 where the second carrier Cr is located is “2nd”, and the second speed stage is established.

第１クラッチＣ１と第４ブレーキＢ４とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「１」、第１プラネタリギヤ４のリングギヤＲｆ、第２プラネタリギヤ６のキャリアＣｍ、第３プラネタリギヤ７のリングギヤＲｒが位置する縦線Ｙ２での回転速度がＮ１となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「３ｒｄ」になり、３速段が確立される。   When the first clutch C1 and the fourth brake B4 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the ring gear Rf of the first planetary gear 4, the second planetary gear 6 The rotational speed at the vertical line Y2 at which the carrier Cm of the third planetary gear 7 is located and the vertical line Y2 at which the ring gear Rr of the third planetary gear 7 is located is N1, and the rotational speed at the vertical line Y3 at which the carrier Cr of the third planetary gear 7 is located is 3rd. A speed is established.

第１ブレーキＢ１と第４ブレーキＢ４とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「０」、第１プラネタリギヤ４のリングギヤＲｆ、第２プラネタリギヤ６のキャリアＣｍ、第３プラネタリギヤ７のリングギヤＲｒが位置する縦線Ｙ２での回転速度がＮ１となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「４ｔｈ」になり、４速段が確立される。   When the first brake B1 and the fourth brake B4 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is “0”, the ring gear Rf of the first planetary gear 4 and the second planetary gear 6 The rotational speed at the vertical line Y2 where the carrier Cm and the ring gear Rr of the third planetary gear 7 are located is N1, and the rotational speed at the vertical line Y3 where the carrier Cr is located at the third planetary gear 7 is "4th". A speed is established.

第２クラッチＣ２と第４ブレーキＢ４とを係合させると、第３プラネタリギヤ７のサンギヤＳｒが位置する縦線Ｙ５での回転速度が「１」、第１プラネタリギヤ４のリングギヤＲｆ、第３プラネタリギヤ７のリングギヤＲｒが位置する縦線Ｙ２での回転速度がＮ１となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「５ｔｈ」になり、５速段が確立される。   When the second clutch C2 and the fourth brake B4 are engaged, the rotational speed of the third planetary gear 7 at the vertical line Y5 where the sun gear Sr is located is "1", the ring gear Rf of the first planetary gear 4, the third planetary gear 7 The rotational speed at the vertical line Y2 where the ring gear Rr is located is N1, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "5th", and the fifth gear is established.

第２クラッチＣ２と第１ブレーキＢ１とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「０」、第２プラネタリギヤ６のリングギヤＲｍ、第３プラネタリギヤ７のサンギヤＳｒが位置する縦線Ｙ４での回転速度が「１」となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「６ｔｈ」になり、６速段が確立される。   When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "0", the ring gear Rm of the second planetary gear 6, the third planetary gear 7 The rotational speed at the vertical line Y4 where the sun gear Sr is located is "1", the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "6th", and the sixth gear is established. .

第１クラッチＣ１と第２クラッチＣ２とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１及び第２プラネタリギヤ６のリングギヤＲｍが位置する縦線Ｙ５での回転速度が「１」となって第２プラネタリギヤ６の各要素が相対回転不能なロック状態となる。これに伴い、第３プラネタリギヤ７もロック状態となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度も「１」である「７ｔｈ」になり、７速段が確立される。   When the first clutch C1 and the second clutch C2 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located and the vertical line Y5 where the ring gear Rm of the second planetary gear 6 is located is “1”. The elements of the second planetary gear 6 are in a locked state in which relative rotation is impossible. As a result, the third planetary gear 7 is also locked, the rotational speed of the third planetary gear 7 along the vertical line Y3 where the carrier Cr is located is also “1”, “7th”, and the seventh gear is established.

第１クラッチＣ１と第２ブレーキＢ２とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「１」、第２プラネタリギヤ６のキャリアＣｍ及び第３プラネタリギヤ７のリングギヤＲｒが位置する縦線Ｙ２での回転速度が「０」となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度はマイナスの「Ｒｅｖ」になって、後進段が確立される。   When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the carrier Cm of the second planetary gear 6 and the third planetary gear 7 The rotational speed at the vertical line Y2 where the ring gear Rr is located is “0”, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is negative “Rev”, and the reverse gear is established. Is done.

図１（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２、ブレーキＢ１，Ｂ２，Ｂ３，Ｂ４の係合状態との関係を纏めて表示した図であり、「○」は係合を表している。また、図１（ｂ）は、第１プラネタリギヤ４のギヤ比ｉを２．０、第２プラネタリギヤ６のギヤ比を２．７、第３プラネタリギヤ７のギヤ比を１．５とした場合における各変速段のギヤレシオ（入力軸２の回転速度／出力ギヤ３の回転速度）も示している。これによれば、公比（各変速段間のギヤレシオの比）が適切になると共に、レシオレンジ（第１速のギヤレシオと第７速のギヤレシオの比（図１（ｂ）の１速段のギヤレシオの右隣の欄に表示））も適切となる。   FIG. 1B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1 and C2 and the brakes B1, B2, B3, and B4. “O” represents engagement. ing. FIG. 1B shows each of the cases where the gear ratio i of the first planetary gear 4 is 2.0, the gear ratio of the second planetary gear 6 is 2.7, and the gear ratio of the third planetary gear 7 is 1.5. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (ratio of the first gear ratio to the seventh gear ratio (the first gear stage in FIG. 1B) Appears in the column to the right of the gear ratio))).

第１実施形態によれば、２つのクラッチＣ１，Ｃ２と４つのブレーキＢ１，Ｂ２，Ｂ３，Ｂ４で、前進７段の変速を行うことができる。又、第１ブレーキＢ１を第１クラッチＣ１の径方向外方に配置し、第２ブレーキＢ２を複式プラネタリギヤ５の径方向外方に配置し、第３ブレーキＢ３を第２クラッチＣ２の径方向外方に配置することができる。従って、従来のものと比較して、クラッチの数を減少させることができると共に、ブレーキをクラッチ又はプラネタリギヤの径方向外方に配置して、自動変速機の軸長を短くすることができる。   According to the first embodiment, seven forward shifts can be performed by the two clutches C1, C2 and the four brakes B1, B2, B3, B4. In addition, the first brake B1 is disposed radially outward of the first clutch C1, the second brake B2 is disposed radially outward of the compound planetary gear 5, and the third brake B3 is radially outward of the second clutch C2. Can be arranged in the direction. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.

次に、図３、図４を参照して本発明の第２実施形態の自動変速機を説明する。第２実施形態の変速機ケース１内には、入力軸２の周りに位置させて、入力用の第１プラネタリギヤ４と、変速用の複式プラネタリギヤ５とが配置されている。第１プラネタリギヤ４は、第１実施形態と同様にダブルピニオン型の単式プラネタリギヤで構成されている。   Next, an automatic transmission according to a second embodiment of the present invention will be described with reference to FIGS. In the transmission case 1 of the second embodiment, a first planetary gear 4 for input and a double planetary gear 5 for shifting are arranged around the input shaft 2. The first planetary gear 4 is a double-pinion type single planetary gear, as in the first embodiment.

図４の上段に示す第１プラネタリギヤ４の速度線図を参照して、第１プラネタリギヤ４のサンギヤＳｆ、キャリアＣｆ及びリングギヤＲｆから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第１要素、第２要素及び第３要素とすると、第１要素はキャリアＣｆ、第２要素はリングギヤＲｆ、第３要素はサンギヤＳｆになる。尚、サンギヤＳｆとキャリアＣｆ間の間隔とキャリアＣｆとリングギヤＲｆ間の間隔との比は、第１プラネタリギヤ４のギヤ比をｉとして、ｉ：１に設定される。   Referring to the velocity diagram of the first planetary gear 4 shown in the upper part of FIG. 4, three elements including the sun gear Sf, the carrier Cf, and the ring gear Rf of the first planetary gear 4 are arranged at intervals corresponding to the gear ratio in the velocity diagram. If the first element, the second element, and the third element are arranged from the left side in the order in which they are arranged, the first element is the carrier Cf, the second element is the ring gear Rf, and the third element is the sun gear Sf. The ratio between the distance between the sun gear Sf and the carrier Cf and the distance between the carrier Cf and the ring gear Rf is set to i: 1 where i is the gear ratio of the first planetary gear 4.

第２実施形態では、キャリアＣｆ（第１要素）は変速機ケース１に固定されて固定要素とされ、リングギヤＲｆ（第２要素）は入力軸２に連結されて入力要素とされ、サンギヤＳｆ（第３要素）を出力要素としている。そして、第１プラネタリギヤ４の出力速度（サンギヤＳｆの回転速度）Ｎ１は「ｉ」になる。尚、速度線図において、下の横線と上の横線は夫々回転速度が「０」と「１」（入力軸２と同じ回転速度）であることを示している。   In the second embodiment, the carrier Cf (first element) is fixed to the transmission case 1 as a fixed element, the ring gear Rf (second element) is connected to the input shaft 2 as an input element, and the sun gear Sf ( The third element) is the output element. The output speed of the first planetary gear 4 (the rotational speed of the sun gear Sf) N1 is “i”. In the velocity diagram, the lower horizontal line and the upper horizontal line indicate that the rotational speeds are “0” and “1” (the same rotational speed as the input shaft 2), respectively.

第２実施形態の複式プラネタリギヤ５は、第１実施形態と同様にシングルピニオン型の第２、第３プラネタリギヤ６，７で構成されている。図４の下段に示す複式プラネタリギヤ５の速度線図を参照して、第２プラネタリギヤ６のサンギヤＳｍ、キャリアＣｍ及びリングギヤＲｍから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第４要素、第５要素及び第６要素とすると、第４要素はサンギヤＳｍ、第５要素はキャリアＣｍ、第６要素はリングギヤＲｍになる。尚、サンギヤＳｍとキャリアＣｍ間の間隔とキャリアＣｍとリングギヤＲｍ間の間隔との比は、第２プラネタリギヤ６のギヤ比をｊとして、ｊ：１に設定される。   Similar to the first embodiment, the double planetary gear 5 of the second embodiment is composed of second and third planetary gears 6 and 7 of a single pinion type. Referring to the speed diagram of the double planetary gear 5 shown in the lower part of FIG. 4, the three elements including the sun gear Sm, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fourth element is the sun gear Sm, the fifth element is the carrier Cm, and the sixth element is the ring gear Rm. The ratio between the distance between the sun gear Sm and the carrier Cm and the distance between the carrier Cm and the ring gear Rm is set to j: 1 where j is the gear ratio of the second planetary gear 6.

又、上記複式プラネタリギヤ５の速度線図を参照して、第３プラネタリギヤ７のサンギヤＳｒ、キャリアＣｒ及びリングギヤＲｒから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に左側から夫々第７要素、第８要素及び第９要素とすると、第７要素はリングギヤＲｒ、第８要素はキャリアＣｒ、第９要素はサンギヤＳｒになる。尚、サンギヤＳｒ（縦線Ｙ４）とキャリアＣｒ（縦線Ｙ３）間の間隔とキャリアＣｒ（縦線Ｙ３）とリングギヤＲｒ（縦線Ｙ２）間の間隔との比は、第３プラネタリギヤ６のギヤ比をｋとして、ｋ：１に設定される。   Further, referring to the velocity diagram of the compound planetary gear 5, the three elements including the sun gear Sr, the carrier Cr and the ring gear Rr of the third planetary gear 7 are arranged in the order corresponding to the gear ratio in the velocity diagram. Assuming that the seventh element, the eighth element, and the ninth element are the left side, the seventh element is the ring gear Rr, the eighth element is the carrier Cr, and the ninth element is the sun gear Sr. The ratio between the distance between the sun gear Sr (vertical line Y4) and the carrier Cr (vertical line Y3) and the distance between the carrier Cr (vertical line Y3) and the ring gear Rr (vertical line Y2) is the gear of the third planetary gear 6. The ratio is set to k: 1, where k is the ratio.

ここで、第２実施形態では、第２プラネタリギヤ６のキャリアＣｍ（第５要素）と第３プラネタリギヤ７のリングギヤＲｒ（第７要素）とを連結して第１連結体Ｃｍ，Ｒｒ（縦線Ｙ２）を構成し、第１プラネタリギヤ４のリングギヤＲｆ（第２要素）に入力軸２を連結し、第２プラネタリギヤ６のリングギヤＲｍ（第６要素）と第３プラネタリギヤ７のサンギヤＳｒ（第９要素）とを連結して第２連結体Ｒｍ，Ｓｒを構成し、第３プラネタリギヤ７のキャリアＣｒ（第８要素）を出力部材たる出力ギヤ３に連結している。   Here, in 2nd Embodiment, the carrier Cm (5th element) of the 2nd planetary gear 6 and the ring gear Rr (7th element) of the 3rd planetary gear 7 are connected, and 1st connection body Cm, Rr (vertical line Y2) is connected. ), The input shaft 2 is connected to the ring gear Rf (second element) of the first planetary gear 4, and the ring gear Rm (sixth element) of the second planetary gear 6 and the sun gear Sr (ninth element) of the third planetary gear 7. Are connected to each other to form a second connecting body Rm, Sr, and the carrier Cr (eighth element) of the third planetary gear 7 is connected to the output gear 3 as an output member.

又、係合要素として、第１プラネタリギヤ４のサンギヤＳｆ（第３要素）と第２プラネタリギヤ６のサンギヤＳｍ（第４要素）とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素たる第１クラッチＣ１と、第１プラネタリギヤ４のサンギヤＳｆ（第３要素）と第２連結体Ｒｍ，Ｓｒとを連結する状態とこの連結を断つ状態とに切換自在な第２係合要素たる第２クラッチＣ２と、入力軸２と第１連結体Ｃｍ，Ｒｒとを連結する状態とこの連結を断つ状態とに切換自在な第３係合要素たる第３クラッチＣ３と、第２プラネタリギヤ６のサンギヤＳｍ（第４要素）を第１プラネタリギヤ４のキャリアＣｆを介して変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第６係合要素たる第１ブレーキＢ１と、第１連結体Ｃｍ，Ｒｒを変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第４係合要素たる第２ブレーキＢ２と、第２連結体Ｒｍ，Ｓｒを変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第５係合要素たる第３ブレーキＢ３とを備えている。   In addition, as an engagement element, a first gear that can be switched between a state in which the sun gear Sf (third element) of the first planetary gear 4 and the sun gear Sm (fourth element) of the second planetary gear 6 are connected and a state in which the connection is cut off. Second engagement that can be switched between a state in which the first clutch C1, which is an engagement element, the sun gear Sf (third element) of the first planetary gear 4 and the second coupling bodies Rm, Sr are coupled, and a state in which the coupling is disconnected. A second clutch C2, which is an element, a third clutch C3 which is a third engagement element which can be switched between a state where the input shaft 2 and the first connecting bodies Cm, Rr are connected and a state where the connection is disconnected, and a second planetary gear. The first brake B1 as a sixth engagement element that can be switched between a state in which the sun gear Sm (fourth element) 6 is fixed to the transmission case 1 via the carrier Cf of the first planetary gear 4 and a state in which the fixing is released. And first The second brake B2, which is a fourth engagement element that can be switched between a state in which the joints Cm, Rr are fixed to the transmission case 1 and a state in which the fixation is released, and the second coupling bodies Rm, Sr are connected to the transmission case 1. And a third brake B3 that is a fifth engagement element that can be switched between a state of being fixed to the state of releasing the fixed state and a state of releasing the fixing.

第１クラッチＣ１と第３ブレーキＢ３とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度がＮ１、第２連結体Ｒｍ，Ｓｒが位置する縦線Ｙ４での回転速度が「０」になり、出力ギヤ３に連結される第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「１ｓｔ」になり、１速段が確立される。   When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the vertical line Y4 at which the second coupling bodies Rm and Sr are located. Of the third planetary gear 7 connected to the output gear 3 at the vertical line Y3 where the carrier Cr is located is "1st", and the first gear is established.

第３クラッチＣ３と第３ブレーキＢ３とを係合させると、第１連結体Ｃｍ，Ｒｒを構成する第３プラネタリギヤ７のリングギヤＲｒ（縦線Ｙ２）の回転速度が「１」、第２連結体Ｒｍ，Ｓｒを構成する第３プラネタリギヤ７のサンギヤＳｒ（縦線Ｙ４）の回転速度が「０」になり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「２ｎｄ」になって、２速段が確立される。   When the third clutch C3 and the third brake B3 are engaged, the rotational speed of the ring gear Rr (vertical line Y2) of the third planetary gear 7 constituting the first coupling bodies Cm, Rr is “1”, and the second coupling body. The rotational speed of the sun gear Sr (vertical line Y4) of the third planetary gear 7 constituting Rm, Sr is “0”, and the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is “2nd”. Thus, the second gear is established.

第１クラッチＣ１と第３クラッチＣ３とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度がＮ１、第１連結体Ｃｍ，Ｒｒを構成する第２プラネタリギヤ６のキャリアＣｍ、第３プラネタリギヤ７のリングギヤＲｒ（縦線Ｙ２）の回転速度が「１」になり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「３ｒｄ」になり、３速段が確立される。   When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the second planetary gear 6 constituting the first coupling bodies Cm, Rr. The rotational speed of the carrier Cm, the ring gear Rr (vertical line Y2) of the third planetary gear 7 is "1", the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is "3rd", Third gear is established.

第３クラッチＣ３と第１ブレーキＢ１とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「０」、第１連結体Ｃｍ，Ｒｒが位置する縦線Ｙ２での回転速度が「１」となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「４ｔｈ」になり、４速段が確立される。   When the third clutch C3 and the first brake B1 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located is “0”, and the vertical line where the first coupling bodies Cm and Rr are located. The rotational speed at Y2 is “1”, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is “4th”, and the fourth speed stage is established.

第２クラッチＣ２と第３クラッチＣ３とを係合させると、第３プラネタリギヤ７のサンギヤＳｒが位置する縦線Ｙ４での回転速度がＮ１、第３プラネタリギヤ７のリングギヤＲｒが位置する縦線Ｙ２での回転速度が「１」となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「５ｔｈ」になり、５速段が確立される。   When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y4 where the sun gear Sr of the third planetary gear 7 is located is N1, and the vertical line Y2 at which the ring gear Rr of the third planetary gear 7 is located. The rotation speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is "5th", and the fifth gear is established.

第２クラッチＣ２と第１ブレーキＢ１とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度が「０」、第２連結体Ｒｍ，Ｓｒを構成する第２プラネタリギヤ６のリングギヤＲｍ、第３プラネタリギヤ７のサンギヤＳｒが位置する縦線Ｙ４での回転速度がＮ１となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度は「６ｔｈ」になり、６速段が確立される。   When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is “0”, and the second connecting members Rm and Sr are configured. The rotational speed at the vertical line Y4 where the ring gear Rm of the planetary gear 6 and the sun gear Sr of the third planetary gear 7 are located is N1, and the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "6th". 6th gear is established.

第１クラッチＣ１と第２クラッチＣ２とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１及び第２プラネタリギヤ６のリングギヤＲｍが位置する縦線Ｙ４での回転速度がＮ１となって第２プラネタリギヤ６の各要素が相対回転不能なロック状態となる。これに伴い、第３プラネタリギヤ７もロック状態となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度もＮ１である「７ｔｈ」になり、７速段が確立される。   When the first clutch C1 and the second clutch C2 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located and the vertical line Y4 where the ring gear Rm of the second planetary gear 6 is located is N1. Thus, each element of the second planetary gear 6 is in a locked state where relative rotation is impossible. Along with this, the third planetary gear 7 is also locked, the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is also “7th”, which is N1, and the seventh gear is established.

第１クラッチＣ１と第２ブレーキＢ２とを係合させると、第２プラネタリギヤ６のサンギヤＳｍが位置する縦線Ｙ１での回転速度がＮ１、第１連結体Ｃｍ，Ｒｒが位置する縦線Ｙ２での回転速度が「０」となり、第３プラネタリギヤ７のキャリアＣｒが位置する縦線Ｙ３での回転速度はマイナスの「Ｒｅｖ」になって、後進段が確立される。   When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the vertical line Y2 at which the first coupling bodies Cm and Rr are located. The rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located becomes negative “Rev”, and the reverse speed is established.

図３（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２，Ｃ３、ブレーキＢ１，Ｂ２，Ｂ３の係合状態との関係を纏めて表示した図であり、「○」は係合を表している。また、図３（ｂ）は、第１プラネタリギヤ４のギヤ比ｉを２．０、第２プラネタリギヤ６のギヤ比を２．７、第３プラネタリギヤ７のギヤ比を１．５とした場合における各変速段のギヤレシオ（入力軸２の回転速度／出力ギヤ３の回転速度）も示している。これによれば、公比（各変速段間のギヤレシオの比）が適切になると共に、レシオレンジ（第１速のギヤレシオと第７速のギヤレシオの比（図３（ｂ）の１速段のギヤレシオの右隣の欄に表示））も適切となる。   FIG. 3B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1, B2, and B3. “O” represents engagement. ing. FIG. 3B shows each of the cases where the gear ratio i of the first planetary gear 4 is 2.0, the gear ratio of the second planetary gear 6 is 2.7, and the gear ratio of the third planetary gear 7 is 1.5. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (the ratio of the gear ratio between the respective gears) becomes appropriate, and the ratio orange (the ratio of the gear ratio of the first speed to the gear ratio of the seventh speed (the first gear stage of FIG. 3B) Appears in the column to the right of the gear ratio))).

第２実施形態の自動変速機によれば、３つのクラッチと３つのブレーキで前進７段の変速を行うことができる。又、第４係合要素たる第２ブレーキＢ２を複式プラネタリギヤ５の径方向外方に配置し、第５係合要素たる第３ブレーキＢ３を第２係合要素たる第２クラッチＣ２の径方向外方に配置することができる。従って、従来のものと比較して、クラッチの数を減少させることができると共に、ブレーキをクラッチ又はプラネタリギヤの径方向外方に配置でき、自動変速機の軸長を短くできる。   According to the automatic transmission of the second embodiment, it is possible to perform a forward seven-speed shift with three clutches and three brakes. Further, the second brake B2 as the fourth engagement element is disposed radially outward of the double planetary gear 5, and the third brake B3 as the fifth engagement element is radially outward of the second clutch C2 as the second engagement element. Can be arranged in the direction. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the brake can be disposed radially outward of the clutch or the planetary gear, so that the axial length of the automatic transmission can be shortened.

尚、図５に示す第３実施形態の自動変速機の如く、第１実施形態の第３プラネタリギヤ７を第２プラネタリギヤ６の径方向外側に配置し、第２プラネタリギヤ６のリングギヤＲｍと第３プラネタリギヤ７のサンギヤＳｒとを一体に形成してもよい。これによれば、更に変速機の軸長を短くすることができる。又、第２実施形態のものにおいても同様に第３プラネタリギヤ７を第２プラネタリギヤ６の径方向外側に配置して、軸長を短くすることができる。   In addition, like the automatic transmission of the third embodiment shown in FIG. 5, the third planetary gear 7 of the first embodiment is arranged on the radially outer side of the second planetary gear 6, and the ring gear Rm of the second planetary gear 6 and the third planetary gear are arranged. 7 sun gear Sr may be integrally formed. According to this, the shaft length of the transmission can be further shortened. Similarly, in the second embodiment, the third planetary gear 7 can be disposed radially outside the second planetary gear 6 to shorten the axial length.

又、図６に示す第４実施形態の自動変速機の如く、第１実施形態の第４係合要素たる多板クラッチ式の第２ブレーキＢ２に代えて、第１連結体Ｒｆ，Ｃｍ，Ｒｒを変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在なドグクラッチＤ１を用いてもよい。これにより、多板クラッチで構成したものと比較して、前進段に於ける多板クラッチの開放に伴うフリクションロスを低減させることができ、伝達効率を向上させることができる。ドグクラッチＤ１は、第３プラネタリギヤ７のリングギヤＲｒに外周にスプライン結合された可動ドグＤ１ａと、変速機ケース１内に固定した固定ドグＤ１ｂとで構成され、可動ドグＤ１ａのドグ歯を固定ドグＤ１ｂのドグ歯に係合させることでリングギヤＲｒの回転が拘束される。第２実施形態の第４係合要素たる第２ブレーキＢ２、第３実施形態の第２ブレーキＢ２についても同様にドグクラッチに置き換えることにより、前進段に於ける多板クラッチの開放に伴うフリクションロスを低減させ、伝達効率を向上させることができる。   Further, as in the automatic transmission of the fourth embodiment shown in FIG. 6, instead of the multi-plate clutch type second brake B2 as the fourth engagement element of the first embodiment, the first coupling bodies Rf, Cm, Rr A dog clutch D1 that can be switched between a state in which the gear is fixed to the transmission case 1 and a state in which the fixing is released may be used. As a result, the friction loss associated with the release of the multi-plate clutch at the forward stage can be reduced and the transmission efficiency can be improved as compared with the multi-plate clutch. The dog clutch D1 includes a movable dog D1a splined to the outer periphery of the ring gear Rr of the third planetary gear 7, and a fixed dog D1b fixed in the transmission case 1. The dog teeth of the movable dog D1a are connected to the dog teeth of the fixed dog D1b. Engagement with the dog teeth restrains the rotation of the ring gear Rr. Similarly, the second brake B2 as the fourth engagement element of the second embodiment and the second brake B2 of the third embodiment are replaced with dog clutches, so that friction loss due to the release of the multi-plate clutch at the forward gear is reduced. It is possible to reduce the transmission efficiency.

（ａ）は本発明の自動変速機の第１実施形態のスケルトン図、（ｂ）は各変速段と各係合要素の係合状態との関係を纏めて示す図。(A) is a skeleton diagram of the first embodiment of the automatic transmission according to the present invention, and (b) is a diagram collectively showing the relationship between each shift stage and the engagement state of each engagement element. 第１実施形態の第１〜第３プラネタリギヤの速度線図。The speed diagram of the 1st-3rd planetary gear of 1st Embodiment. （ａ）は本発明の自動変速機の第２実施形態のスケルトン図、（ｂ）は各変速段と各係合要素の係合状態との関係を纏めて示す図。(A) is a skeleton figure of 2nd Embodiment of the automatic transmission of this invention, (b) is a figure which shows collectively the relationship between each gear stage and the engagement state of each engagement element. 第２実施形態の第１〜第３プラネタリギヤの速度線図。The speed diagram of the 1st-3rd planetary gear of 2nd Embodiment. 本発明の自動変速機の第３実施形態のスケルトン図。The skeleton figure of 3rd Embodiment of the automatic transmission of this invention. 本発明の自動変速機の第４実施形態のスケルトン図。The skeleton figure of 4th Embodiment of the automatic transmission of this invention.

符号の説明Explanation of symbols

１…変速機ケース、２…入力軸、３…出力ギヤ、４…第１プラネタリギヤ、５…複式プラネタリギヤ、６…第２プラネタリギヤ、７…第３プラネタリギヤ、Ｓｆ…第１プラネタリギヤのサンギヤ（第１要素）、Ｒｆ…第１プラネタリギヤのリングギヤ（第２要素）、Ｃｆ…第１プラネタリギヤのキャリア（第３要素）、Ｓｍ…第２プラネタリギヤのサンギヤ（第４要素）、Ｒｍ…第２プラネタリギヤのリングギヤ（第６要素）、Ｃｍ…第２プラネタリギヤのキャリア（第５要素）、Ｓｒ…第３プラネタリギヤのサンギヤ（第９要素）、Ｒｒ…第３プラネタリギヤのリングギヤ（第７要素）、Ｃｒ…第３プラネタリギヤのキャリア（第８要素）、Ｃ１…第１クラッチ（第１係合要素）、Ｃ２…第２クラッチ（第２係合要素）、Ｃ３…第３クラッチ（第２実施形態の第３係合要素）、Ｂ１…第１ブレーキ（第１，３，４実施形態の第３係合要素，第２実施形態の第６係合要素）、Ｂ２…第２ブレーキ（第４係合要素）、Ｂ３…第３ブレーキ（第５係合要素）、Ｂ４…第４ブレーキ（第６係合要素）、Ｄ１…ＤＯＧクラッチ。 DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output gear, 4 ... 1st planetary gear, 5 ... Double planetary gear, 6 ... 2nd planetary gear, 7 ... 3rd planetary gear, Sf ... Sun gear of 1st planetary gear (1st element) ), Rf: ring gear (second element) of the first planetary gear, Cf: carrier of the first planetary gear (third element), Sm: sun gear (fourth element) of the second planetary gear, Rm: ring gear (second element) of the second planetary gear 6 element), Cm: second planetary gear carrier (fifth element), Sr ... third planetary gear sun gear (ninth element), Rr ... third planetary gear ring gear (seventh element), Cr ... third planetary gear carrier (8th element), C1 ... 1st clutch (1st engagement element), C2 ... 2nd clutch (2nd engagement element), C3 ... 3rd clutch (3rd engagement element of 2nd Embodiment), B1 ... 1st brake (3rd engagement element of 1st, 3rd, 4th embodiment, 6th engagement element of 2nd Embodiment), B2 ... 2nd Brake (fourth engagement element), B3 ... third brake (fifth engagement element), B4 ... fourth brake (sixth engagement element), D1 ... DOG clutch.

Claims (4)

入力部材の回転を変速機ケース内に配置した入力用の第１プラネタリギヤと変速用の複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、
複式プラネタリギヤは、第２と第３の２つのプラネタリギヤで構成され、
第１プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第１要素、第２要素及び第３要素とし、第２プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第４要素、第５要素及び第６要素とし、第３プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第７要素、第８要素及び第９要素として、
第２要素と第５要素と第７要素とを連結して第１連結体が構成され、第３要素に入力部材が連結され、第６要素と第９要素とを連結して第２連結体が構成されると共に、第８要素が出力部材に連結され、
第４要素と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素と、
第２連結体と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第２係合要素と、
第４要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な３係合要素と、
第１連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第４係合要素と、
第２連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第５係合要素と、
第１要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする自動変速機。 An automatic transmission that shifts the rotation of an input member to a plurality of stages through a first planetary gear for input disposed in a transmission case and a dual planetary gear for transmission and transmits it to an output member.
The compound planetary gear is composed of the second and third planetary gears,
The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are set as the first element, the second element, and the third element in the order corresponding to the gear ratio in the velocity diagram, respectively. The sun gear of the second planetary gear The three elements consisting of the carrier and the ring gear are designated as the fourth element, the fifth element, and the sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, and from the sun gear, the carrier, and the ring gear of the third planetary gear. The three elements consisting of the seventh element, the eighth element, and the ninth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
The first element is configured by connecting the second element, the fifth element, and the seventh element, the input member is connected to the third element, and the second element is connected by connecting the sixth element and the ninth element. And the eighth element is connected to the output member,
A first engagement element switchable between a state in which the fourth element and the input member are connected and a state in which the connection is broken;
A second engagement element that is switchable between a state in which the second connection body and the input member are connected and a state in which the connection is broken;
A three-engagement element switchable between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released;
A fourth engagement element switchable between a state in which the first coupling body is fixed to the transmission case and a state in which the fixation is released;
A fifth engagement element switchable between a state in which the second coupling body is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising: a sixth engaging element that is switchable between a state in which the first element is fixed to the transmission case and a state in which the fixing is released. 入力部材の回転を変速機ケース内に配置した入力用の第１プラネタリギヤと変速用の複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、
複式プラネタリギヤは、第２と第３の２つのプラネタリギヤで構成され、
第１プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第１要素、第２要素及び第３要素とし、第２プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第４要素、第５要素及び第６要素とし、第３プラネタリギヤのサンギヤ、キャリア及びリングギヤから成る３個の要素を、速度線図におけるギヤ比に対応する間隔での並び順に夫々第７要素、第８要素及び第９要素として、
第１要素が変速機ケースに固定され、第２要素に入力部材が連結され、第５要素と第７要素とを連結して第１連結体が構成され、第６要素と第９要素とを連結して第２連結体が構成されると共に、第８要素が出力部材に連結され、
第３要素と第４要素とを連結する状態とこの連結を断つ状態とに切換自在な第１係合要素と、
第３要素と第２連結体とを連結する状態とこの連結を断つ状態とに切換自在な第２係合要素と、
第１連結体と入力部材とを連結する状態とこの連結を断つ状態とに切換自在な第３係合要素と、
第１連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第４係合要素と、
第２連結体を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第５係合要素と、
第４要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする自動変速機。 An automatic transmission that shifts the rotation of an input member to a plurality of stages through a first planetary gear for input disposed in a transmission case and a dual planetary gear for transmission and transmits it to an output member.
The compound planetary gear is composed of the second and third planetary gears,
The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are set as the first element, the second element, and the third element in the order corresponding to the gear ratio in the velocity diagram, respectively. The sun gear of the second planetary gear The three elements consisting of the carrier and the ring gear are designated as the fourth element, the fifth element, and the sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, and from the sun gear, the carrier, and the ring gear of the third planetary gear. The three elements consisting of the seventh element, the eighth element, and the ninth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
The first element is fixed to the transmission case, the input member is connected to the second element, the fifth element and the seventh element are connected to form a first connection body, and the sixth element and the ninth element are connected. The second connected body is configured by connecting, and the eighth element is connected to the output member,
A first engagement element that is switchable between a state in which the third element and the fourth element are connected and a state in which the connection is cut off;
A second engagement element that is switchable between a state in which the third element and the second connection body are connected and a state in which the connection is broken;
A third engagement element switchable between a state in which the first connection body and the input member are connected and a state in which the connection is cut off;
A fourth engagement element switchable between a state in which the first coupling body is fixed to the transmission case and a state in which the fixation is released;
A fifth engagement element switchable between a state in which the second coupling body is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising a sixth engaging element that is switchable between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released. 請求項１又は請求項２に記載の自動変速機において、
第６要素は第２プラネタリギヤのリングギヤであり、第９要素は第３プラネタリギヤのサンギヤであり、第３プラネタリギヤが第２プラネタリギヤの径方向外側に配置され、第２プラネタリギヤのリングギヤと第３プラネタリギヤのサンギヤとを一体化して第２連結体が構成されることを特徴とする自動変速機。 The automatic transmission according to claim 1 or 2,
The sixth element is a ring gear of the second planetary gear, the ninth element is a sun gear of the third planetary gear, the third planetary gear is disposed radially outside the second planetary gear, and the ring gear of the second planetary gear and the sun gear of the third planetary gear And an integrated transmission to form a second coupling body. 請求項１から請求項３の何れか１項に記載の自動変速機において、第４係合要素がドグクラッチであることを特徴とする自動変速機。   The automatic transmission according to any one of claims 1 to 3, wherein the fourth engagement element is a dog clutch.

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