JP5113718B2 - Automatic transmission - Google Patents

Automatic transmission Download PDF

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JP5113718B2
JP5113718B2 JP2008276436A JP2008276436A JP5113718B2 JP 5113718 B2 JP5113718 B2 JP 5113718B2 JP 2008276436 A JP2008276436 A JP 2008276436A JP 2008276436 A JP2008276436 A JP 2008276436A JP 5113718 B2 JP5113718 B2 JP 5113718B2
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gear
planetary gear
state
planetary
input member
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JP2010106863A (en
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憲明 斉藤
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Honda Motor Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Description

本発明は、ロックアップクラッチ付き流体トルクコンバータを介してエンジン等の動力源の回転が入力される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 which rotation of a power source such as an engine is input via a fluid torque converter with a lock-up clutch to a plurality of stages and transmits the rotation to an output member.

従来、ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転を複数段に変速して出力部材に出力する自動変速機が知られている（例えば、特許文献１参照）。   Conventionally, a fluid torque converter having a lockup clutch that mechanically connects a pump and a turbine and connected to a power source, and a plurality of stages of rotation of an input member to which the rotation of the power source is input via the fluid torque converter There is known an automatic transmission that shifts the speed and outputs to an output member (for example, see Patent Document 1).

特許文献１のものでは、減速用の第１プラネタリギヤと、変速用の第２と第３との２つのプラネタリギヤとを備える。第１プラネタリギヤと第２プラネタリギヤとはシングルピニオン型で構成され、第３プラネタリギヤはダブルピニオン型で構成されている。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は同一部材で構成され、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プラネタリギヤで複式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。   The thing of patent document 1 is provided with the 1st planetary gear for deceleration, and the 2nd and 3rd planetary gears for gear shifting. The first planetary gear and the second planetary gear are configured as a single pinion type, and the third planetary gear is configured as a double pinion type. The ring gears of the second planetary gear and the third planetary gear are composed of the same member, and the pinion supported by the carrier of the second planetary is used as one of the pair of pinions of the third planetary gear, and the carrier of the second planetary gear and the carrier of the third planetary gear And the second and third planetary gears constitute a double planetary gear. 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 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.
JP 2005-54824 A

上記従来例のものでは、第１〜第４クラッチの４つと第１，第２ブレーキの２つとで、係合要素が合計６つと多い。係合要素が多いと構造が複雑になると共に自動変速機が大きくなってしまう。   In the above-described conventional example, there are a total of six engaging elements including four of the first to fourth clutches and two of the first and second brakes. If there are many engaging elements, the structure becomes complicated and the automatic transmission becomes large.

以上の点に鑑み、本発明は、係合要素を少なくし小型化と構造の簡略化を図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, it is an object of the present invention to provide an automatic transmission that can be reduced in size and simplified in structure by reducing the number of engaging elements.

上記目的を達成するため、本発明は、ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、サンギヤ、キャリア及びリングギヤから成る３個の要素を有する複数のプラネタリギヤとを備え、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転をプラネタリギヤで複数段に変速して出力部材に出力する自動変速機であって、入力部材は第１と第２の２つの入力部材で構成され、第１入力部材はタービンに連結され、第２入力部材は、ロックアップクラッチに介設された第２入力部材用ディスクと、プラネタリギヤの何れか１の要素とに連結され、ロックアップクラッチの係合で動力源の回転が伝達される状態となり、ロックアップクラッチの開放で動力源の回転の伝達を断たれる状態となることを特徴とする。   In order to achieve the above object, the present invention includes a fluid torque converter having a lockup clutch for mechanically connecting a pump and a turbine and connected to a power source, and three elements including a sun gear, a carrier, and a ring gear. A plurality of planetary gears, and an automatic transmission that shifts the rotation of an input member to which rotation of a power source is input via a fluid torque converter to a plurality of stages with a planetary gear and outputs the output to an output member. It is composed of two first and second input members, the first input member is connected to the turbine, and the second input member is either a second input member disk interposed in a lock-up clutch or a planetary gear. 1 is connected, and the rotation of the power source is transmitted when the lock-up clutch is engaged, and the power source is released when the lock-up clutch is released. Characterized in that a state of cut off the transmission of rotation.

本発明によれば、ロックアップクラッチが係合する高速段側の変速段を確立する際にのみ係合される係合要素の機能を、ロックアップクラッチと第２入力部材用ディスクとで果たすことができ、変速機の高速段側でのみ係合される係合要素を１つ少なくすることができる。これにより、係合要素のピストンや油圧回路等をロックアップクラッチのもので共通化でき、自動変速機の小型化及び構造の簡略化を図ることができる。   According to the present invention, the lock-up clutch and the second input member disk perform the function of the engagement element that is engaged only when the high-speed gear stage to which the lock-up clutch is engaged is established. Thus, one engagement element that is engaged only on the high speed stage side of the transmission can be reduced. As a result, the piston and hydraulic circuit of the engagement element can be shared by those of the lock-up clutch, and the automatic transmission can be downsized and the structure can be simplified.

第２入力部材に連結されるプラネタリギヤの要素としては、例えば、前進１速段を確立する際に変速機ケースに固定される要素が挙げられる。前進１速段を確立する際に変速機ケースに固定される要素は、高速段側の変速段を確立する際にのみ係合する係合要素で入力部材と連結されるように構成されることが多い。従って、第２入力部材と前記要素とを連結することにより、高速段側の変速段を確立する際にのみ前記要素と入力部材と連結する状態とする係合要素の機能を、ロックアップクラッチと第２入力部材用ディスクとで果たすことができ、自動変速機の小型化及び構成の簡略化を図ることができる。   Examples of the planetary gear element connected to the second input member include an element fixed to the transmission case when establishing the first forward speed. The element fixed to the transmission case when establishing the first forward speed is configured to be connected to the input member with an engaging element that is engaged only when the high speed stage is established. There are many. Therefore, by connecting the second input member and the element, the function of the engagement element that connects the element and the input member only when establishing a shift stage on the high-speed stage side is used as a lock-up clutch. This can be achieved with the second input member disk, and the automatic transmission can be reduced in size and configuration.

本発明の第１の具体的態様としては、自動変速機を、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第２と第３の２つのプラネタリギヤとを備え、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５要素を第２入力部材に連結し、第６要素と第９要素とを連結すると共に、第８要素を出力部材に連結し、更に、第４要素と第６要素の何れか一方に第１入力部材の回転を第１プラネタリギヤを介して伝達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４要素と第６要素の何れか他方に第１入力部材の回転を第１プラネタリギヤを介して伝達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要素と第７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３係合要素と、第５要素と第７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４係合要素と、第５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５係合要素とを備えるもので構成することができる。   As a first specific aspect of the present invention, an automatic transmission includes a first planetary gear for input disposed in a transmission case, and second and third planetary gears for transmission, and the first planetary gear is provided. The three elements consisting of the sun gear, the carrier, and the ring gear are the first element, the second element, and the third element, respectively, in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The three elements consisting of the ring gear are 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 the three elements consisting of the sun gear, the carrier, and the ring gear of the third planetary gear. The fifth element is connected to the second input member as the seventh element, the eighth element, and the ninth element in the order of arrangement at intervals corresponding to the gear ratio in the speed diagram. The sixth element and the ninth element are connected, the eighth element is connected to the output member, and the rotation of the first input member is connected to one of the fourth element and the sixth element via the first planetary gear. A first engagement element that can be switched between a state of transmitting and a state of disconnecting the connection, and a state of transmitting the rotation of the first input member to one of the fourth element and the sixth element via the first planetary gear. A second engagement element that can be switched to a state in which the connection is broken, a third engagement element that is switchable to a state in which the fourth element and the seventh element are coupled, and a state in which the connection is broken, and a fifth Switchable between a state where the element and the seventh element are connected and a state where the connection is cut off, a fourth engagement element, a state where the fifth element is fixed to the transmission case, and a state where the fixing is released And a fifth engaging element.

本発明の第１の具体的態様によれば、後述する実施形態の説明から明らかなように、ロックアップクラッチを除く５つの係合要素で、前進８段の変速を行うことができる。又、従来のものは、各変速段において係合する係合要素の数が２つであり開放している係合要素の数が４つと多く、開放されている係合要素の引き摺りによるフリクションロスが大きく、変速機の効率が悪化する不具合がある。本発明の第１の具体的態様によれば、全ての変速段において開放されている係合要素の数を３つ以下とすることができ、フリクションロスを軽減し、自動変速機の効率を向上させることができる。   According to the first specific aspect of the present invention, as will be apparent from the description of the embodiments described later, eight forward shifting can be performed with five engagement elements excluding the lockup clutch. In addition, the conventional one has two engagement elements engaged at each gear stage and has a large number of four engagement elements that are open, and the friction loss due to dragging of the open engagement elements. There is a problem that the efficiency of the transmission deteriorates. According to the first specific aspect of the present invention, the number of engagement elements opened at all gear positions can be three or less, reducing friction loss and improving the efficiency of the automatic transmission. Can be made.

又、本発明の第１の具体的態様のものに、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係合要素を設ければ、従来と同数の６つの係合要素で前進１０段の変速を行うことができる。   Further, if the sixth specific element of the first specific aspect of the present invention is provided with a sixth engagement element that can be switched between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released, The same number of six engaging elements can be used to shift 10 forward speeds.

又、本発明の第１の具体的態様において、第６要素が第２プラネタリギヤのサンギヤであり、第９要素が第３プラネタリギヤのリングギヤである場合、第３プラネタリギヤを第２プラネタリギヤの径方向内側に配置し、第２プラネタリギヤのサンギヤと第３プラネタリギヤのリングギヤとを一体化すれば、自動変速機の軸長をより短くすることができる。   Further, in the first specific aspect of the present invention, when the sixth element is the sun gear of the second planetary gear and the ninth element is the ring gear of the third planetary gear, the third planetary gear is placed radially inward of the second planetary gear. By arranging and integrating the sun gear of the second planetary gear and the ring gear of the third planetary gear, the shaft length of the automatic transmission can be made shorter.

本発明の第２の具体的態様として、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第２と第３の２つのプラネタリギヤとを備え、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５要素を第２入力部材に連結し、第６要素と第９要素とを連結すると共に、第８要素を出力部材に連結し、第４要素又は第６要素の一方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態と、第４要素又は第６要素の他方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態と、第４要素及び第６要素に第１プラネタリギヤを介した第１入力部材の回転の伝達を断つ状態とに切換自在な同期噛合機構と、第４要素と第７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５要素と第７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２係合要素と、第５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３係合要素と、第１要素又は第３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４係合要素とを備えるもので構成することができる。   As a second specific aspect of the present invention, the first planetary gear for input disposed in the transmission case and the second and third planetary gears for transmission are provided, and the sun gear, carrier and ring gear of the first planetary gear are provided. The three elements are the first element, the second element, and the third element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram, respectively, and the three planetary gears are the sun gear, the carrier, and the ring gear. The elements are the fourth element, the fifth element, and the sixth element in the order of arrangement at intervals corresponding to the gear ratio in the speed diagram, and the three elements including the sun gear, the carrier, and the ring gear of the third planetary gear are The fifth element is connected to the second input member as the seventh element, the eighth element, and the ninth element in the arrangement order at intervals corresponding to the gear ratio in the figure, and the sixth element and the And a state in which the eighth element is connected to the output member, the rotation of the first input member is transmitted to one of the fourth element and the sixth element via the first planetary gear, and the fourth element or the second element. A state in which the rotation of the first input member is transmitted to the other of the six elements through the first planetary gear, and a state in which the transmission of the rotation of the first input member through the first planetary gear is cut off to the fourth and sixth elements. A switchable synchronous meshing mechanism, a state of connecting the fourth element and the seventh element, and a state of connecting the fifth element and the seventh element that are switchable between a state of disconnecting the connection and a state of disconnecting the connection. A second engagement element that can be switched to a state in which the connection is broken, a third engagement element that can be switched to a state in which the fifth element is fixed to the transmission case, and a state in which the fixation is released, The state in which the element or the third element is fixed to the transmission case and the The state and the switching freely fourth engagement elements can be composed of one including a.

本発明の第２の具体的態様は、第１の具体的態様の第１，第２係合要素に代えて、同期噛合装置を設けると共に、第４係合要素により第１要素又は第３要素を変速機ケースに固定する状態とこの状態を解除する状態とに切換自在としたものである。第２の具体的態様によれば、１つの係合要素が同期噛合機構に置き換えられることとなり、フリクションロスをより低減させることができる。   In the second specific aspect of the present invention, in place of the first and second engaging elements of the first specific aspect, a synchronous meshing device is provided, and the first or third element is provided by the fourth engaging element. Can be switched between a state of fixing to the transmission case and a state of releasing this state. According to the second specific mode, one engagement element is replaced with the synchronous meshing mechanism, and the friction loss can be further reduced.

又、上記第１及び第２の具体的態様において、第１プラネタリギヤを、第１要素と第３要素の一方を第１入力部材に連結する入力要素、他方を変速機ケースに固定する固定要素、第２要素を出力要素とする減速用のプラネタリギヤで構成すれば、良好な減速比を得ることができる。   Further, in the first and second specific embodiments, the first planetary gear may be an input element that connects one of the first element and the third element to the first input member, and a fixing element that fixes the other to the transmission case, A good reduction ratio can be obtained by using a planetary gear for reduction with the second element as an output element.

本発明の第３の具体的態様として、第１プラネタリギヤと第２プラネタリギヤとを備え、第１プラネタリギヤのサンギヤ、キャリア、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要素として、第６要素を第２入力部材に連結し、第３要素と第４要素とを連結して連結体を構成し、第１，第２入力部材に平行に配置した出力部材たる出力軸に、第１ギヤ列を介して第２要素を連結すると共に、第１ギヤ列とは異なるギヤ比の第２ギヤ列を介して第５要素を連結し、第１要素と第１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、連結体と第１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３係合要素と、第６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４係合要素とを備えるもので構成することができる。   As a third specific aspect of the present invention, a first planetary gear and a second planetary gear are provided, and three elements including a sun gear, a carrier, and a ring gear of the first planetary gear are arranged 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. As the fourth element, the fifth element, and the sixth element, the sixth element is connected to the second input member, the third element and the fourth element are connected to form a connection body, and the first and second input members are connected. The second element is connected to the output shaft, which is an output member arranged in parallel, via the first gear train, and the fifth element is connected via the second gear train having a gear ratio different from that of the first gear train, 1st element and 1st input part A first engagement element that can be switched between a state in which the connection is disconnected and a state in which the connection is disconnected, and a second engagement that is switchable between a state in which the connection body and the first input member are connected and a state in which the connection is disconnected. An element, a third engaging element that can be switched between a state in which the first element is fixed to the transmission case and a state in which the fixing is released, and a state in which the sixth element is fixed to the transmission case, and the fixing is released. And a fourth engagement element that can be switched between states.

本発明の第３の具体的態様によれば、後述する実施形態の説明から明らかなように、ロックアップクラッチを除く４つの係合要素で、前進６段の変速を行うことができる。又、第１と第２の２つのプラネタリギヤで構成できるため、構成をより簡略化して小型化を図ることができると共に、自動変速機の軸長を短くすることができる。更に、５速段と６速段と後進段以外の変速段では第１と第２の両プラネタリギヤの片方のプラネタリギヤ単独での動力伝達が行われると共に、３速段と４速段との２つの変速段において夫々第１プラネタリギヤと第２プラネタリギヤとがロック状態になるため、噛合伝達効率は１００％になり、全ての変速段のトータルの伝達効率が向上する。   According to the third specific aspect of the present invention, as will be apparent from the description of the embodiment described later, it is possible to perform six forward shifts with four engagement elements except for the lock-up clutch. In addition, since the first and second planetary gears can be used, the configuration can be further simplified and the size can be reduced, and the shaft length of the automatic transmission can be shortened. Further, at the speeds other than the 5th speed stage, the 6th speed stage, and the reverse speed stage, power is transmitted by only one of the planetary gears of the first and second planetary gears. Since the first planetary gear and the second planetary gear are in a locked state at each shift stage, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the shift stages is improved.

又、本発明の第３の具体的態様において、第３要素が第１プラネタリギヤのリングギヤであり、第４要素が第２プラネタリギヤのサンギヤである場合、第２プラネタリギヤを第１プラネタリギヤの径方向外側に配置し、第１プラネタリギヤのリングギヤと第２プラネタリギヤのサンギヤとを一体化して前記連結体を構成すれば、変速機の軸長を更に短縮することができる。   Further, in the third specific aspect of the present invention, when the third element is a ring gear of the first planetary gear and the fourth element is a sun gear of the second planetary gear, the second planetary gear is disposed radially outward of the first planetary gear. By arranging and integrating the ring gear of the first planetary gear and the sun gear of the second planetary gear to form the coupling body, the shaft length of the transmission can be further shortened.

本発明の第４の具体的態様として、第１プラネタリギヤと第２プラネタリギヤとを備え、第１プラネタリギヤのサンギヤ、キャリア、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要素として、第１要素と第１入力部材とを連結し、第５要素と第２入力部材とを連結し、第１入力部材及び第２入力部材たる入力軸に平行に配置した出力部材たる出力軸に、第１ギヤ列を介して第２要素を連結すると共に、第１ギヤ列とは異なるギヤ比の第２ギヤ列を介して第６要素を連結し、第１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５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第３係合要素と、第５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４係合要素とを備えるもので構成することができる。   As a fourth specific aspect of the present invention, a first planetary gear and a second planetary gear are provided, and three elements including a sun gear, a carrier, and a ring gear of the first planetary gear are arranged 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. As the 4th element, the 5th element, and the 6th element, the 1st element and the 1st input member are connected, the 5th element and the 2nd input member are connected, and the input shaft which is the 1st input member and the 2nd input member The second element is connected to the output shaft, which is an output member arranged in parallel with the first element, via the first gear train, and the sixth element is connected via the second gear train having a gear ratio different from that of the first gear train. And the first element A first engagement element that can be switched between a state in which the four elements are connected and a state in which the connection is cut off, and a second switchable in a state that connects the third element and the fifth element and a state in which the connection is cut off. An engagement element, a third engagement element that can be switched between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released, a state in which the fifth element is fixed to the transmission case, and this fixing It can comprise with the 4th engagement element switchable to the state to cancel | release.

本発明の第４の具体的態様によれば、後述する実施形態の説明から明らかなように、ロックアップクラッチを除く４つの係合要素で、前進６段の変速を行うことができる。又、２速段と３速段以外の変速段では第１と第２の両プラネタリギヤの片方のプラネタリギヤ単独での動力伝達が行われると共に、４速段と５速段との２つの変速段において夫々第１プラネタリギヤと第２プラネタリギヤとがロック状態になるため、噛合伝達効率は１００％になり、全ての変速段のトータルの伝達効率が向上する。   According to the fourth specific aspect of the present invention, as will be apparent from the description of the embodiment described later, it is possible to perform a forward six-speed shift with four engagement elements excluding the lockup clutch. Further, at the speeds other than the second speed stage and the third speed stage, power is transmitted by only one of the planetary gears of the first and second planetary gears, and at the two speed stages of the fourth speed stage and the fifth speed stage. Since the first planetary gear and the second planetary gear are respectively locked, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the gears is 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実施形態の変速機は、動力源たる図外のエンジンに連結される流体トルクコンバータ１を備えている。流体トルクコンバータ１は、エンジンのフライホイール２ａに回転振動吸収用のダンパ２ｂを介して連結されるポンプＰｏと、ポンプＰｏから内部流体を介して動力伝達されるタービンＴａと、ポンプＰｏとタービンＴａとの間に介設され一方向クラッチを介して変速機ケース３に固定されるステータＳｔと、タービンＴａをポンプＰｏに機械的に連結するロックアップクラッチＬＣとを備えている。   Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. The transmission according to the first embodiment includes a fluid torque converter 1 connected to an unillustrated engine serving as a power source. The fluid torque converter 1 includes a pump Po connected to a flywheel 2a of the engine via a damper 2b for absorbing rotational vibration, a turbine Ta to which power is transmitted from the pump Po via an internal fluid, a pump Po and a turbine Ta And a stator St that is fixed to the transmission case 3 via a one-way clutch, and a lock-up clutch LC that mechanically connects the turbine Ta to the pump Po.

又、変速機ケース３内には、タービンＴａと連結する第１入力部材たる中空の第１入力軸４１と、第１入力軸４１内に同心に内挿された第２入力部材たる第２入力軸４２とが回転自在に軸支されている。又、変速機は、入力用の第１プラネタリギヤ５と、変速用の第２プラネタリギヤ６及び第３プラネタリギヤ７と、出力部材たる出力ギヤ８ａとを備え、何れも第１，第２入力軸４１，４２と同心に配置される。出力ギヤ８ａ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両輪に伝達される。   Further, in the transmission case 3, a hollow first input shaft 41 as a first input member connected to the turbine Ta, and a second input as a second input member concentrically inserted in the first input shaft 41. A shaft 42 is rotatably supported. The transmission also includes a first planetary gear 5 for input, a second planetary gear 6 and a third planetary gear 7 for shifting, and an output gear 8a as an output member, both of which are first and second input shafts 41, 41, 42 and concentric. The rotation of the output gear 8a is transmitted to both the left and right wheels of the vehicle via a differential gear (not shown).

ロックアップクラッチＬＣには、第２入力軸４２と連結する第２入力軸用ディスク４２ａが介設されている。ロックアップクラッチＬＣを係合させるとポンプＰｏとタービンＴａとが機械的に連結されると共に、第２入力軸４２も第２入力軸用ディスク４２ａを介してポンプＰｏとタービンＴａとに機械的に連結される。尚、ロックアップクラッチＬＣは、単板式のものでも多板式のものでもよい。   A second input shaft disk 42 a connected to the second input shaft 42 is interposed in the lockup clutch LC. When the lockup clutch LC is engaged, the pump Po and the turbine Ta are mechanically connected, and the second input shaft 42 is also mechanically connected to the pump Po and the turbine Ta via the second input shaft disk 42a. Connected. The lock-up clutch LC may be a single plate type or a multi-plate type.

第１プラネタリギヤ５は、サンギヤＳｆと、リングギヤＲｆと、サンギヤＳｆとリングギヤＲｆとに噛合するピニオン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 first planetary gear 5 is formed of a single pinion type planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the sun gear Sf and the ring gear Rf so as to freely rotate and revolve.

図２の上段に示す速度線図（サンギヤ、キャリア、リングギヤの３個の要素の回転速度を直線で表すことができる図）を参照して、第１プラネタリギヤ５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要素はキャリアＣｆ、第３要素はリングギヤＲｆになる。   Referring to the speed diagram shown in the upper part of FIG. 2 (a diagram in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), the sun gear Sf, the carrier Cf, and the ring gear Rf of the first planetary gear 5 Are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, the first element is the sun gear Sf, and the second element is The carrier Cf and the third element are the ring gear Rf.

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５のギヤ比（リングギヤの歯数／サンギヤの歯数）をｉとして、ｉ：１に設定される。第１実施形態では、サンギヤＳｆを変速機ケース３に固定される固定要素とし、リングギヤＲｆを第１入力軸４１に連結される入力要素として、キャリアＣｆが出力要素になるようにしている。第１プラネタリギヤ５の出力速度（キャリアＣｆの回転速度）Ｎ１はｉ／（ｉ＋１）になり、速度線図から明らかなように、第１入力軸４１の回転が減速されてキャリアＣｆから出力される。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。   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 5 (the number of teeth of the ring gear / the number of teeth of the sun gear). Is set. In the first embodiment, the sun gear Sf is a fixed element fixed to the transmission case 3 and the ring gear Rf is an input element connected to the first input shaft 41, so that the carrier Cf is an output element. The output speed of the first planetary gear 5 (rotational speed of the carrier Cf) N1 is i / (i + 1), and as is apparent from the speed diagram, the rotation of the first input shaft 41 is decelerated and output from the carrier Cf. . 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プラネタリギヤ６は、サンギヤＳｍと、リングギヤＲｍと、互いに噛合すると共に一方がサンギヤＳｍ、他方がリングギヤＲｍに噛合する一対のピニオンＰｍ，Ｐｍ’を自転及び公転自在に支持するキャリアＣｍとから成るダブルピニオン型のプラネタリギヤで構成されている。   The second planetary gear 6 includes a sun gear Sm, a ring gear Rm, and a carrier Cm that supports a pair of pinions Pm and Pm ′ that mesh with each other and one meshes with the sun gear Sm and the other meshes with the ring gear Rm. It is composed of a double pinion type planetary gear.

第３プラネタリギヤ７は、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 third planetary gear 7 is composed of a single pinion type planetary gear including 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要素はキャリアＣｍ、第５要素はリングギヤＲｍ、第６要素はサンギヤＳｍ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 velocity diagram 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 on the left side in the order corresponding to the gear ratio in the velocity diagram. Are the fourth element, the fifth element, and the sixth element, respectively, the fourth element is the carrier Cm, the fifth element is the ring gear Rm, and the sixth element is the sun gear Sm. 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、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要素はサンギヤＳｒ、第８要素はキャリアＣｒ、第９要素はリングギヤＲｒになる。尚、サンギヤＳｒ（縦線Ｙ２）とキャリアＣｒ（縦線Ｙ４）間の間隔とキャリアＣｒ（縦線Ｙ４）とリングギヤＲｒ（縦線Ｙ５）間の間隔との比は、第３プラネタリギヤ７のギヤ比をｋとして、ｋ：１に設定される。   In addition, 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 of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, from the left to the seventh element, the eighth element, and the ninth element. As elements, the seventh element is the sun gear Sr, the eighth element is the carrier Cr, and the ninth element is the ring gear Rr. The ratio between the distance between the sun gear Sr (vertical line Y2) and the carrier Cr (vertical line Y4) and the distance between the carrier Cr (vertical line Y4) and the ring gear Rr (vertical line Y5) is the gear of the third planetary gear 7. The ratio is set to k: 1, where k is the ratio.

ここで、第１実施形態では、第２プラネタリギヤ６のリングギヤＲｍ（第５要素）を第２入力軸４２に連結し、サンギヤＳｍ（第６要素）と第３プラネタリギヤ７のリングギヤＲｒ（第９要素）とを連結し、キャリアＣｒ（第８要素）を出力ギヤ８ａに連結している。   Here, in the first embodiment, the ring gear Rm (fifth element) of the second planetary gear 6 is connected to the second input shaft 42, and the ring gear Rr (ninth element) of the sun gear Sm (sixth element) and the third planetary gear 7 is connected. And the carrier Cr (eighth element) are connected to the output gear 8a.

又、係合要素として、第１プラネタリギヤ５のキャリアＣｆ（第２要素）と第２プラネタリギヤ６のキャリアＣｍ（第４要素）とを連結する状態とこの状態を断つ状態とに切換自在な第１係合要素又は第２係合要素たる第１クラッチＣ１と、第１プラネタリギヤ５のキャリアＣｆ（第２要素）と第２プラネタリギヤ６のサンギヤＳｍ（第６要素）とを連結する状態とこの状態を断つ状態とに切換自在な第２係合要素又は第１係合要素たる第２クラッチＣ２と、第２プラネタリギヤ６のキャリアＣｍ（第４要素）と第３プラネタリギヤ７のサンギヤＳｒ（第７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３係合要素たる第１切換クラッチＣａと、第２プラネタリギヤ６のリングギヤＲｍ（第５要素）と第３プラネタリギヤ７のサンギヤＳｒ（第７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４係合要素たる第２切換クラッチＣｂと、第２プラネタリギヤ６のリングギヤＲｍ（第５要素）を変速機ケース３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１ブレーキＢ１とを備えている。   In addition, the engaging element is a first switchable between a state in which the carrier Cf (second element) of the first planetary gear 5 and the carrier Cm (fourth element) of the second planetary gear 6 are connected and a state in which this state is cut off. The state in which the first clutch C1, which is the engagement element or the second engagement element, the carrier Cf (second element) of the first planetary gear 5 and the sun gear Sm (sixth element) of the second planetary gear 6 are coupled to each other. The second clutch C2 as the second engagement element or the first engagement element which can be switched to the disconnected state, the carrier Cm (fourth element) of the second planetary gear 6, and the sun gear Sr (seventh element) of the third planetary gear 7. , A first switching clutch Ca that is a third engagement element that can be switched between a state in which the connection is disconnected and a state in which the connection is disconnected, a ring gear Rm (fifth element) of the second planetary gear 6, and a third planetary gear 7. The second switching clutch Cb, which is a fourth engagement element that can be switched between a state in which the sun gear Sr (seventh element) is connected and a state in which the connection is cut off, and a ring gear Rm (fifth element) of the second planetary gear 6 are shifted. A first brake B1 is provided as a fifth engagement element that can be switched between a state of being fixed to the machine case 3 and a state of releasing the fixing.

上記の如く第２プラネタリギヤ６のサンギヤＳｍと第３プラネタリギヤ７のリングギヤＲｒとを連結することにより、図２の下段に示す速度線図において、第２プラネタリギヤ６のサンギヤＳｍは、第３プラネタリギヤ７のリングギヤＲｒと同一の縦線Ｙ５上に常時位置する。一方、第２プラネタリギヤ６のリングギヤＲｍとキャリアＣｍの速度線図上の位置は、第１切換クラッチＣａを係合させた場合と第２切換クラッチＣｂを係合させた場合とで異なる。これを詳述するに、第１切換クラッチＣａの係合時には、第２プラネタリギヤ６のキャリアＣｍが第３プラネタリギヤ７のサンギヤＳｒと同一の縦線Ｙ２上に位置し、第２プラネタリギヤ６のリングギヤＲｍは、縦線Ｙ２と縦線Ｙ５間の間隔の１／ｊだけ縦線Ｙ２から右側に離れた縦線Ｙ３上に位置する。又、第２切換クラッチＣｂの係合時には、第２プラネタリギヤ６のリングギヤＲｍが縦線Ｙ２上に位置し、第２プラネタリギヤ６のキャリアＣｍは、縦線Ｙ２との間の間隔と縦線Ｙ５との間の間隔との比が１：ｊとなるように縦線Ｙ２から左に離れた縦線Ｙ１上に位置する。   By connecting the sun gear Sm of the second planetary gear 6 and the ring gear Rr of the third planetary gear 7 as described above, the sun gear Sm of the second planetary gear 6 in the speed diagram shown in the lower stage of FIG. It is always located on the same vertical line Y5 as the ring gear Rr. On the other hand, the positions of the ring gear Rm of the second planetary gear 6 and the carrier Cm on the velocity diagram are different between when the first switching clutch Ca is engaged and when the second switching clutch Cb is engaged. More specifically, when the first switching clutch Ca is engaged, the carrier Cm of the second planetary gear 6 is positioned on the same vertical line Y2 as the sun gear Sr of the third planetary gear 7, and the ring gear Rm of the second planetary gear 6 is located. Is located on the vertical line Y3 that is separated from the vertical line Y2 to the right by 1 / j of the interval between the vertical line Y2 and the vertical line Y5. When the second switching clutch Cb is engaged, the ring gear Rm of the second planetary gear 6 is positioned on the vertical line Y2, and the carrier Cm of the second planetary gear 6 is separated from the distance between the vertical line Y2 and the vertical line Y5. It is located on the vertical line Y1 that is separated from the vertical line Y2 to the left so that the ratio to the interval between the two is 1: j.

第２クラッチＣ２と第１切換クラッチＣａ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のリングギヤＲｍ（縦線Ｙ３）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「１ｓｔ」になって、１速段が確立される。   When the second clutch C2, the first switching clutch Ca and the first brake B1 are engaged, the rotational speed of the ring gear Rm (vertical line Y3) of the second planetary gear 6 is “0”, and the rotational speed at the vertical line Y5 is The output speed N1 of the first planetary gear 5 is reached, the rotational speed of the third planetary gear 7 connected to the output gear 8a at the vertical line Y4 where the carrier Cr is located is “1st”, and the first gear is established. .

第２クラッチＣ２と第２切換クラッチＣｂと第１ブレーキＢ１とを係合させると、第３プラネタリギヤ７のサンギヤＳｒ（縦線Ｙ２）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「２ｎｄ」になって、２速段が確立される。   When the second clutch C2, the second switching clutch Cb and the first brake B1 are engaged, the rotational speed of the sun gear Sr (vertical line Y2) of the third planetary gear 7 is "0", and the rotational speed at the vertical line Y5 is The rotational speed at the vertical line Y4 at which the carrier Cr of the third planetary gear 7 connected to the output gear 8a is "2nd" becomes the output speed N1 of the first planetary gear 5, and the second speed stage is established. .

第２クラッチＣ２と第１切換クラッチＣａと第２切換クラッチＣｂとを係合させると、第２プラネタリギヤ６のリングギヤＲｍとキャリアＣｍとが連結されて、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に第１プラネタリギヤ５の出力速度Ｎ１になり、縦線Ｙ４での回転速度もＮ１である「３ｒｄ」になって、３速段が確立される。尚、３速段においては、第１クラッチＣ１も一緒に係合させてもよい。これにより、第１クラッチＣ１でフリクションロスが発生することを確実に防止することができる。   When the second clutch C2, the first switching clutch Ca, and the second switching clutch Cb are engaged, the ring gear Rm of the second planetary gear 6 and the carrier Cm are connected, and the second planetary gear 6 cannot rotate relative to each other. Therefore, both the rotational speed at the vertical line Y2 and the rotational speed at the vertical line Y5 are the output speed N1 of the first planetary gear 5, and the rotational speed at the vertical line Y4 is also N1 “3rd” Then, the third gear is established. In the third speed, the first clutch C1 may be engaged together. Thereby, it is possible to reliably prevent the occurrence of friction loss in the first clutch C1.

第２クラッチＣ２と第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「４ｔｈ」になって、４速段が確立される。第１実施形態では、４速段以上の変速段においてはロックアップクラッチＬＣを係合させてトルクコンバータにおけるスリップを防止することで燃費の向上を図るように構成されている。   When the second clutch C2, the second switching clutch Cb, and the lockup clutch LC are engaged, the rotational speed at the vertical line Y2 is “1”, the rotational speed at the vertical line Y5 is N1, and the vertical line Y4 is Becomes the 4th speed, and the 4th gear is established. The first embodiment is configured to improve fuel efficiency by engaging the lock-up clutch LC and preventing slippage in the torque converter at the fourth speed or higher.

第２クラッチＣ２と第１切換クラッチＣａとロックアップクラッチＬＣとを係合させると、縦線Ｙ３での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「５ｔｈ」になって、５速段が確立される。   When the second clutch C2, the first switching clutch Ca, and the lockup clutch LC are engaged, the rotational speed at the vertical line Y3 is “1”, the rotational speed at the vertical line Y5 is N1, and the vertical line Y4 is The rotation speed becomes “5th” and the fifth gear is established.

第１切換クラッチＣａと第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に「１」になり、縦線Ｙ４での回転速度も１である「６ｔｈ」になって、６速段が確立される。   When the first switching clutch Ca, the second switching clutch Cb, and the lock-up clutch LC are engaged, the second planetary gear 6 is in a locked state where the relative rotation of each element is impossible. The rotational speed on the line Y5 is both “1”, and the rotational speed on the vertical line Y4 is also “6th” which is 1, so that the sixth gear is established.

第１クラッチＣ１と第１切換クラッチＣａとロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「１」となり、縦線Ｙ４での回転速度が「７ｔｈ」となって、７速段が確立される。   When the first clutch C1, the first switching clutch Ca, and the lock-up clutch LC are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “1”, and the vertical line Y4 The rotational speed becomes “7th”, and the seventh gear is established.

第１クラッチＣ１と第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「１」となり、縦線Ｙ４での回転速度が「８ｔｈ」となって、８速段が確立される。   When the first clutch C1, the second switching clutch Cb, and the lock-up clutch LC are engaged, the rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is "1", and the vertical line Y4 The rotational speed becomes “8th”, and the eighth gear is established.

第１クラッチＣ１と第１切換クラッチＣａと第１ブレーキＢ１とを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ１」となって、後進１速段が確立される。   When the first clutch C1, the first switching clutch Ca, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, and the vertical line Y4 The rotation speed becomes negative “Rev1”, and the first reverse speed is established.

第１クラッチＣ１と第２切換クラッチＣｂと第１ブレーキＢ１とを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ２」となって、後進２速段が確立される。   When the first clutch C1, the second switching clutch Cb, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is "0", and the vertical line Y4 The rotation speed becomes negative “Rev2”, and the second reverse speed is established.

図１（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２，Ｃａ，Ｃｂ、ブレーキＢ１、ロックアップクラッチＬＣ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。又、図１（ｂ）は、第１プラネタリギヤ５のギヤ比ｉを１．４、第２プラネタリギヤ６のギヤ比ｊを２．４、第３プラネタリギヤ７のギヤ比ｋを１．７とした場合における各変速段のギヤレシオ（第１入力軸４１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）およびレシオレンジ（１速段と８速段のギヤレシオの比（図１（ｂ）の１速段のギヤレシオの右隣の欄に表示））が適切になる。   FIG. 1 (b) is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C 1, C 2, Ca, Cb, the brake B 1, and the lock-up clutch LC. Represents the event. FIG. 1B shows the case where the gear ratio i of the first planetary gear 5 is 1.4, the gear ratio j of the second planetary gear 6 is 2.4, and the gear ratio k of the third planetary gear 7 is 1.7. 6 also shows the gear ratio of each gear stage (the rotational speed of the first input shaft 41 / the rotational speed of the output gear 3). According to this, the common ratio (ratio of gear ratios between the respective gears) and ratio orange (ratio of gear ratios of the first gear and the eighth gear (the gear ratio of the first gear in FIG. Display)) is appropriate.

第１実施形態の自動変速機によれば、ロックアップクラッチＬＣを除くクラッチＣ１，Ｃ２，Ｃａ，Ｃｂ、ブレーキＢ１の５つの係合要素で、前進８段の変速を行うことができる。従って、従来のものよりも係合要素が１つ少ないにもかかわらず、前進変速段が１段多い自動変速機を構成することができ、又、係合要素が１つ減るため、小型化と構成の簡略化を図ることができる。又、従来のものは各変速段において係合する係合要素の数が２つであり開放している係合要素の数が４つと多く、開放されている係合要素の引き摺りによるフリクションロスが大きく、変速機の効率が悪化する不具合がある。第１実施形態のものによれば、全ての変速段において開放されている係合要素の数を３つ以下とすることができ、特に１〜３速段においては開放されている係合要素の数を２とすることができ、更に３速段においては第１クラッチＣ１も係合させれば、開放されている係合要素の数を１とすることができる。従って、第１実施形態のものによれば、フリクションロスを軽減し、自動変速機の効率を向上させることができる。   According to the automatic transmission of the first embodiment, eight forward shifts can be performed by the five engagement elements of the clutches C1, C2, Ca, Cb, and the brake B1, excluding the lockup clutch LC. Therefore, it is possible to configure an automatic transmission having one forward shift stage in spite of the fact that the engagement element is one less than that of the conventional one. The configuration can be simplified. Further, the conventional one has two engaging elements engaged at each gear stage, and the number of open engaging elements is as large as four, and the friction loss due to dragging of the opened engaging elements is large. There is a problem that the efficiency of the transmission deteriorates greatly. According to the first embodiment, the number of engagement elements that are opened at all gear positions can be three or less, and in particular, the engagement elements that are opened at the first to third speed stages. The number can be two, and if the first clutch C1 is also engaged at the third speed, the number of released engagement elements can be one. Therefore, according to the first embodiment, the friction loss can be reduced and the efficiency of the automatic transmission can be improved.

尚、第１実施形態の自動変速機においては、入力用の第１プラネタリギヤ５のリングギヤＲｆを第１入力軸４１に連結される入力要素、サンギヤＳｆを変速機ケース３に固定される固定要素、キャリアＣｆを出力要素としているが、サンギヤＳｆを入力要素、リングギヤＲｆを固定要素、キャリアＣｆを出力要素としてもよい。又、第１プラネタリギヤをダブルピニオン型のブラネタリギヤで構成し、サンギヤＳｆとキャリアＣｆの一方を入力要素、他方を固定要素、リングギヤＲｆを出力要素としてもよい。この場合、第１要素がサンギヤＳｆとキャリアＣｆの一方、第２要素がリングギヤＲｆ、第３要素がサンギヤＳｆとキャリアＣｆの他方となる。   In the automatic transmission of the first embodiment, an input element that connects the ring gear Rf of the first planetary gear 5 for input to the first input shaft 41, a fixed element that fixes the sun gear Sf to the transmission case 3, Although the carrier Cf is an output element, the sun gear Sf may be an input element, the ring gear Rf may be a fixed element, and the carrier Cf may be an output element. The first planetary gear may be a double pinion type planetary gear, and one of the sun gear Sf and the carrier Cf may be an input element, the other may be a fixed element, and the ring gear Rf may be an output element. In this case, the first element is one of the sun gear Sf and the carrier Cf, the second element is the ring gear Rf, and the third element is the other of the sun gear Sf and the carrier Cf.

又、図３に示す第２実施形態の如く、第３プラネタリギヤ７を第２プラネタリギヤ６の径方向内側に配置して、第２プラネタリギヤ６のサンギヤＳｍと第３プラネタリギヤ７のリングギヤＲｒとを一体化してもよい。これによれば、第１実施形態のものと比較して変速機の軸長を更に短縮できる。   Further, as in the second embodiment shown in FIG. 3, the third planetary gear 7 is disposed radially inward of the second planetary gear 6 so that the sun gear Sm of the second planetary gear 6 and the ring gear Rr of the third planetary gear 7 are integrated. May be. According to this, the shaft length of the transmission can be further shortened as compared with that of the first embodiment.

次に、図４、図５を参照して、本発明の第３実施形態の自動変速機を説明する。第３実施形態の自動変速機は、図４に示すように、第１実施形態の第２プラネタリギヤ６の第５要素たるリングギヤを同一歯数で一対のリングギヤＲｍ，Ｒｍ’に分割して入力軸４１，４２方向に間隔を存して配置すると共に、この一対のリングギヤＲｍ，Ｒｍ’間を介して第２プラネタリギヤ６の第４要素たるキャリアＣｍを変速機ケース３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２ブレーキＢ２を追加したものであり、他の構成は、第１実施形態のものと同一である。尚、図４（ａ）で、第２ブレーキＢ２が第２プラネタリギヤ６のピニオンＰｍ’を貫通してキャリアＣｍと連結しているように見えるが、実際には、ピニオンＰｍ’と接触しないようにピニオンＰｍ’に対しキャリアＣｍの回転方向に間隔を存して第２ブレーキＢ２がキャリアＣｍと連結している。   Next, an automatic transmission according to a third embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 4, the automatic transmission according to the third embodiment divides the ring gear as the fifth element of the second planetary gear 6 according to the first embodiment into a pair of ring gears Rm and Rm ′ with the same number of teeth. The carrier Cm, which is the fourth element of the second planetary gear 6, is fixed to the transmission case 3 via the pair of ring gears Rm, Rm ′, and this is fixed. The second brake B2, which is a sixth engagement element that can be switched to the released state, is added, and the other configuration is the same as that of the first embodiment. In FIG. 4 (a), the second brake B2 appears to be connected to the carrier Cm through the pinion Pm ′ of the second planetary gear 6. However, in practice, the second brake B2 should not be in contact with the pinion Pm ′. The second brake B2 is connected to the carrier Cm with an interval in the rotation direction of the carrier Cm with respect to the pinion Pm ′.

図５を参照して、第３実施形態の自動変速機では、第２クラッチＣ２と第１切換クラッチＣａ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のリングギヤＲｍおよびＲｍ’（縦線Ｙ３）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「１ｓｔ」になって、１速段が確立される。   Referring to FIG. 5, in the automatic transmission according to the third embodiment, when second clutch C2, first switching clutch Ca, and first brake B1 are engaged, ring gears Rm and Rm ′ (second planetary gear 6) are engaged. The vertical line where the rotational speed of the vertical line Y3) is “0”, the rotational speed of the vertical line Y5 is the output speed N1 of the first planetary gear 5, and the carrier Cr of the third planetary gear 7 connected to the output gear 8a is located. The rotational speed at Y4 is “1st”, and the first gear is established.

第２クラッチＣ２と第２切換クラッチＣｂと第１ブレーキＢ１とを係合させると、第３プラネタリギヤ７のサンギヤＳｒ（縦線Ｙ２）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「２ｎｄ」になって、２速段が確立される。   When the second clutch C2, the second switching clutch Cb and the first brake B1 are engaged, the rotational speed of the sun gear Sr (vertical line Y2) of the third planetary gear 7 is "0", and the rotational speed at the vertical line Y5 is The rotational speed at the vertical line Y4 at which the carrier Cr of the third planetary gear 7 connected to the output gear 8a is "2nd" becomes the output speed N1 of the first planetary gear 5, and the second speed stage is established. .

第２クラッチＣ２と第２切換クラッチＣｂ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のキャリアＣｍ（縦線Ｙ１）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「３ｒｄ」になって、３速段が確立される。   When the second clutch C2, the second switching clutch Cb, and the second brake B2 are engaged, the rotational speed of the carrier Cm (vertical line Y1) of the second planetary gear 6 is “0”, and the rotational speed at the vertical line Y5 is The output speed N1 of the first planetary gear 5 is reached, the rotational speed of the third planetary gear 7 connected to the output gear 8a at the vertical line Y4 where the carrier Cr is located is “3rd”, and the third speed stage is established. .

第２クラッチＣ２と第１切換クラッチＣａと第２切換クラッチＣｂとを係合させると、第２プラネタリギヤ６のリングギヤＲｍとキャリアＣｍとが連結されて、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に第１プラネタリギヤ５の出力速度Ｎ１になり、縦線Ｙ４での回転速度もＮ１である「４ｔｈ」になって、４速段が確立される。尚、４速段においては、第１クラッチＣ１も一緒に係合させてもよい。これにより、第１クラッチＣ１でフリクションロスが発生することを確実に防止することができる。   When the second clutch C2, the first switching clutch Ca, and the second switching clutch Cb are engaged, the ring gear Rm of the second planetary gear 6 and the carrier Cm are connected, and the second planetary gear 6 cannot rotate relative to each other. Therefore, the rotational speed at the vertical line Y2 and the rotational speed at the vertical line Y5 are both the output speed N1 of the first planetary gear 5, and the rotational speed at the vertical line Y4 is also N1 “4th”. Thus, the fourth gear is established. In the fourth speed, the first clutch C1 may be engaged together. Thereby, it is possible to reliably prevent the occurrence of friction loss in the first clutch C1.

第２クラッチＣ２と第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「５ｔｈ」になって、５速段が確立される。第２実施形態では、５速段以上の変速段においてはロックアップクラッチＬＣを係合させてトルクコンバータにおけるスリップを防止することで燃費の向上を図るように構成されている。   When the second clutch C2, the second switching clutch Cb, and the lockup clutch LC are engaged, the rotational speed at the vertical line Y2 is “1”, the rotational speed at the vertical line Y5 is N1, and the vertical line Y4 is The rotation speed becomes “5th” and the fifth gear is established. The second embodiment is configured to improve fuel efficiency by engaging the lock-up clutch LC and preventing slippage in the torque converter at the fifth speed or higher.

第２クラッチＣ２と第１切換クラッチＣａとロックアップクラッチＬＣとを係合させると、縦線Ｙ３での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「６ｔｈ」になって、６速段が確立される。   When the second clutch C2, the first switching clutch Ca, and the lockup clutch LC are engaged, the rotational speed at the vertical line Y3 is “1”, the rotational speed at the vertical line Y5 is N1, and the vertical line Y4 is The rotation speed becomes “6th” and the sixth gear is established.

第１切換クラッチＣａと第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に「１」になり、縦線Ｙ４での回転速度も１である「７ｔｈ」になって、７速段が確立される。   When the first switching clutch Ca, the second switching clutch Cb, and the lock-up clutch LC are engaged, the second planetary gear 6 is in a locked state where the relative rotation of each element is impossible. Both the rotational speeds on the line Y5 are “1”, the rotational speed on the vertical line Y4 is also “7th”, which is 1, and the seventh gear is established.

第１クラッチＣ１と第１切換クラッチＣａとロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「１」となり、縦線Ｙ４での回転速度が「８ｔｈ」となって、８速段が確立される。   When the first clutch C1, the first switching clutch Ca, and the lock-up clutch LC are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “1”, and the vertical line Y4 The rotational speed becomes “8th”, and the eighth gear is established.

第１クラッチＣ１と第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「１」となり、縦線Ｙ４での回転速度が「９ｔｈ」となって、９速段が確立される。   When the first clutch C1, the second switching clutch Cb, and the lock-up clutch LC are engaged, the rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is "1", and the vertical line Y4 The rotation speed becomes “9th” and the ninth gear is established.

第２切換クラッチＣｂと第２ブレーキＢ２とロックアップクラッチＬＣとを係合させると、縦線Ｙ１での回転速度が「０」、縦線Ｙ２での回転速度が「１」となり、縦線Ｙ４での回転速度が「１０ｔｈ」となって、１０速段が確立される。   When the second switching clutch Cb, the second brake B2, and the lockup clutch LC are engaged, the rotational speed at the vertical line Y1 is "0", the rotational speed at the vertical line Y2 is "1", and the vertical line Y4 The rotation speed at "10th" becomes 10th speed.

第１クラッチＣ１と第１切換クラッチＣａと第１ブレーキＢ１とを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ１」となって、後進１速段が確立される。   When the first clutch C1, the first switching clutch Ca, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, and the vertical line Y4 The rotation speed becomes negative “Rev1”, and the first reverse speed is established.

第１クラッチＣ１と第２切換クラッチＣｂと第１ブレーキＢ１とを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ２」となって、後進２速段が確立される。   When the first clutch C1, the second switching clutch Cb, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is "0", and the vertical line Y4 The rotation speed becomes negative “Rev2”, and the second reverse speed is established.

図４（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２，Ｃａ，Ｃｂ、ブレーキＢ１，Ｂ２、ロックアップクラッチＬＣ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。又、図４（ｂ）は、第１プラネタリギヤ５のギヤ比ｉを１．４、第２プラネタリギヤ６のギヤ比ｊを２．４、第３プラネタリギヤ７のギヤ比ｋを１．７とした場合における各変速段のギヤレシオ（第１入力軸４１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）およびレシオレンジ（１速段と１０速段のギヤレシオの比（図４（ｂ）の１速段のギヤレシオの右隣の欄に表示））が適切になる。   FIG. 4 (b) is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, Ca, Cb, the brakes B1, B2, and the lockup clutch LC. Represents engagement. 4B shows a case where the gear ratio i of the first planetary gear 5 is 1.4, the gear ratio j of the second planetary gear 6 is 2.4, and the gear ratio k of the third planetary gear 7 is 1.7. 6 also shows the gear ratio of each gear stage (the rotational speed of the first input shaft 41 / the rotational speed of the output gear 3). According to this, the common ratio (ratio of gear ratios between gears) and ratio orange (ratio of gear ratios of the first gear to the tenth gear (the gear ratio of the first gear in FIG. Display)) is appropriate.

第３実施形態のものによれば、クラッチＣ１，Ｃ２，Ｃａ，Ｃｂ、ブレーキＢ１，Ｂ２の６つの係合要素で前進１０段の変速を行うことができる。尚、第３実施形態においても、第２実施形態のように、第３プラネタリギヤ７を第２プラネタリギヤ６の径方向内側に配置して、第２プラネタリギヤ６のサンギヤＳｍと第３プラネタリギヤ７のリングギヤＲｒとを一体化すれば、変速機の軸長を更に短縮できる。   According to the third embodiment, a forward 10-speed shift can be performed with the six engagement elements of the clutches C1, C2, Ca, Cb and the brakes B1, B2. In the third embodiment as well, as in the second embodiment, the third planetary gear 7 is disposed radially inside the second planetary gear 6 so that the sun gear Sm of the second planetary gear 6 and the ring gear Rr of the third planetary gear 7 are arranged. And the shaft length of the transmission can be further shortened.

次に、図６、図７を参照して、本発明の第４実施形態の自動変速機を説明する。第４実施形態の自動変速機は、図６に示すように、第１実施形態の第１，第２クラッチＣ１，Ｃ２に代えて、第２プラネタリギヤ６のキャリアＣｍ（第４要素）に第１入力軸４１の回転を第１プラネタリギヤ５を介して減速して伝達する状態「Ｓ１」と、第２プラネタリギヤ６のサンギヤＳｍ（第６要素）に第１入力軸４１の回転を第１プラネタリギヤ５を介して減速して伝達する状態「Ｓ２」と、キャリアＣｍ（第４要素）及びサンギヤＳｍ（第６要素）に第１プラネタリギヤ５を介して減速した第１入力軸４１の回転の伝達を断つ状態「ＮＴ」とに切換自在な同期噛合機構ＳＭ（シンクロメッシュ）を設けている。そして、第１プラネタリギヤ５のサンギヤＳｆ（第１要素）を変速機ケース３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ブレーキＢ３を設けている。他の構成は、第１実施形態のものと同一である。第４実施形態においては、第１切換クラッチＣａが第１係合要素、第２切換クラッチＣｂが第２係合要素、第１ブレーキＢ１が第３係合要素、第３ブレーキＢ３が第４係合要素となる。   Next, an automatic transmission according to a fourth embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 6, the automatic transmission according to the fourth embodiment replaces the first and second clutches C <b> 1 and C <b> 2 of the first embodiment with the first carrier Cm (fourth element) of the second planetary gear 6. When the rotation of the input shaft 41 is decelerated and transmitted via the first planetary gear 5, the state "S1" and the rotation of the first input shaft 41 to the sun gear Sm (sixth element) of the second planetary gear 6 are transmitted to the first planetary gear 5. "S2" in which the speed is reduced and transmitted via the first input shaft 41, which is decelerated via the first planetary gear 5 to the carrier Cm (fourth element) and the sun gear Sm (sixth element). A synchronous meshing mechanism SM (Synchromesh) that can be switched to “NT” is provided. A third brake B3 is provided that can be switched between a state in which the sun gear Sf (first element) of the first planetary gear 5 is fixed to the transmission case 3 and a state in which the fixing is released. Other configurations are the same as those of the first embodiment. In the fourth embodiment, the first switching clutch Ca is the first engaging element, the second switching clutch Cb is the second engaging element, the first brake B1 is the third engaging element, and the third brake B3 is the fourth engaging element. It becomes a joint element.

図７を参照して、第４実施形態の自動変速機では、同期噛合機構ＳＭを前記「Ｓ２」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のサンギヤＳｍとを連結させ、第１切換クラッチＣａと第１ブレーキＢ１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のリングギヤＲｍ（縦線Ｙ３）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「１ｓｔ」になって、１速段が確立される。   Referring to FIG. 7, in the automatic transmission of the fourth embodiment, the synchronous meshing mechanism SM is switched to the “S2” state to connect the carrier Cf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6. When the first switching clutch Ca, the first brake B1 and the third brake B3 are engaged, the rotation speed of the ring gear Rm (vertical line Y3) of the second planetary gear 6 is “0”, and the rotation is performed on the vertical line Y5. The speed becomes the output speed N1 of the first planetary gear 5, and the rotational speed at the vertical line Y4 where the carrier Cr of the third planetary gear 7 connected to the output gear 8a is “1st”, and the first gear is established. Is done.

同期噛合機構ＳＭを前記「Ｓ２」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のサンギヤＳｍとを連結させ、第２切換クラッチＣｂと第１ブレーキＢ１と第３ブレーキＢ３とを係合させると、第３プラネタリギヤ７のサンギヤＳｒ（縦線Ｙ２）の回転速度が「０」、縦線Ｙ５での回転速度が第１プラネタリギヤ５の出力速度Ｎ１になり、出力ギヤ８ａ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Ｙ４での回転速度は「２ｎｄ」になって、２速段が確立される。   The synchronous meshing mechanism SM is switched to the “S2” state to connect the carrier Cf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6, and the second switching clutch Cb, the first brake B1, and the third brake B3. , The rotational speed of the sun gear Sr (vertical line Y2) of the third planetary gear 7 becomes “0”, the rotational speed at the vertical line Y5 becomes the output speed N1 of the first planetary gear 5, and the output gear 8a The rotational speed at the vertical line Y4 where the carrier Cr of the third planetary gear 7 to be connected is located is “2nd”, and the second speed stage is established.

同期噛合機構ＳＭを前記「Ｓ２」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のサンギヤＳｍとを連結させ、第１切換クラッチＣａと第２切換クラッチＣｂ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のリングギヤＲｍとキャリアＣｍとが連結されて、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に第１プラネタリギヤ５の出力速度Ｎ１になり、縦線Ｙ４での回転速度もＮ１である「３ｒｄ」になって、３速段が確立される。   The synchronous meshing mechanism SM is switched to the “S2” state, the carrier Cf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6 are connected, and the first switching clutch Ca, the second switching clutch Cb, and the third brake are connected. When B3 is engaged, the ring gear Rm of the second planetary gear 6 and the carrier Cm are connected, and the second planetary gear 6 enters a locked state in which the respective elements cannot be rotated relative to each other. Both the rotational speed at the vertical line Y5 become the output speed N1 of the first planetary gear 5, and the rotational speed at the vertical line Y4 is also "3rd", which is N1, so that the third speed stage is established.

同期噛合機構ＳＭを前記「Ｓ２」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のサンギヤＳｍとを連結させ、第２切換クラッチＣｂと第３ブレーキＢ３とロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「４ｔｈ」になって、４速段が確立される。第４実施形態では、４速段以上の変速段においてはロックアップクラッチＬＣを係合させてトルクコンバータにおけるスリップを防止することで燃費の向上を図るように構成されている。   The synchronous meshing mechanism SM is switched to the “S2” state to connect the carrier Cf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6, and the second switching clutch Cb, the third brake B3, and the lockup clutch LC. , The rotational speed at the vertical line Y2 is “1”, the rotational speed at the vertical line Y5 is N1, the rotational speed at the vertical line Y4 is “4th”, and the fourth gear is Established. The fourth embodiment is configured to improve fuel efficiency by engaging the lock-up clutch LC and preventing slippage in the torque converter at the fourth speed or higher.

同期噛合機構ＳＭを前記「Ｓ２」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のサンギヤＳｍとを連結させ、第１切換クラッチＣａと第３ブレーキＢ３とロックアップクラッチＬＣとを係合させると、縦線Ｙ３での回転速度が「１」、縦線Ｙ５での回転速度がＮ１になり、縦線Ｙ４での回転速度が「５ｔｈ」になって、５速段が確立される。   The synchronous meshing mechanism SM is switched to the “S2” state to connect the carrier Cf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6, and the first switching clutch Ca, the third brake B3, and the lockup clutch LC. , The rotational speed at the vertical line Y3 is “1”, the rotational speed at the vertical line Y5 is N1, the rotational speed at the vertical line Y4 is “5th”, and the fifth gear is Established.

第３ブレーキＢ３の係合を開放して、第１プラネタリギヤ５のキャリアＣｆへの第１入力軸４１の回転の伝達を断ち、同期噛合機構ＳＭを前記「ＮＴ」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆを、第２プラネタリギヤ６のサンギヤＳｍ及びキャリアＣｍの何れにも連結させない状態とし、第１切換クラッチＣａと第２切換クラッチＣｂとロックアップクラッチＬＣとを係合させると、第２プラネタリギヤ６が各要素の相対回転不能なロック状態になるため、縦線Ｙ２での回転速度と縦線Ｙ５での回転速度とが共に「１」になり、縦線Ｙ４での回転速度も１である「６ｔｈ」になって、６速段が確立される。尚、この６速段においては、同期噛合機構ＳＭは、キャリアＣｍ（第４要素）及びサンギヤＳｍ（第６要素）に第１プラネタリギヤ５を介して減速した第１入力軸４１の回転の伝達を断つ状態「ＮＴ」となっているが、次に切り換えられる変速段を推測して第２プラネタリギヤ６のサンギヤＳｍ側又はキャリアＣｍ側で待機するプリシフト状態としてもよい。これにより、スムーズに変速段を切り換えることができる。   The engagement of the third brake B3 is released, the transmission of the rotation of the first input shaft 41 to the carrier Cf of the first planetary gear 5 is cut off, the synchronous meshing mechanism SM is switched to the “NT” state, and the first When the carrier Cf of the planetary gear 5 is not connected to any of the sun gear Sm and the carrier Cm of the second planetary gear 6 and the first switching clutch Ca, the second switching clutch Cb, and the lockup clutch LC are engaged, 2 Since the planetary gear 6 is in a locked state where the relative rotation of each element is impossible, the rotational speed at the vertical line Y2 and the rotational speed at the vertical line Y5 are both "1", and the rotational speed at the vertical line Y4 is also 1 "6th" is established, and the sixth gear is established. In this sixth speed, the synchronous mesh mechanism SM transmits the rotation of the first input shaft 41 decelerated via the first planetary gear 5 to the carrier Cm (fourth element) and the sun gear Sm (sixth element). Although the cut state is “NT”, a pre-shift state in which the next gear to be switched can be estimated to stand by on the sun gear Sm side or the carrier Cm side of the second planetary gear 6 may be used. As a result, the gear position can be switched smoothly.

同期噛合機構ＳＭを前記「Ｓ１」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のキャリアＣｍとを連結させ、第１切換クラッチＣａと第３ブレーキＢ３とロックアップクラッチＬＣとを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「１」となり、縦線Ｙ４での回転速度が「７ｔｈ」となって、７速段が確立される。   The synchronous meshing mechanism SM is switched to the “S1” state to connect the carrier Cf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6, and the first switching clutch Ca, the third brake B3, and the lockup clutch LC. , The rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is "1", the rotational speed at the vertical line Y4 is "7th", and the seventh speed stage is established. Is done.

同期噛合機構ＳＭを前記「Ｓ１」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のキャリアＣｍとを連結させ、第２切換クラッチＣｂと第３ブレーキＢ３とロックアップクラッチＬＣとを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「１」となり、縦線Ｙ４での回転速度が「８ｔｈ」となって、８速段が確立される。   The synchronous meshing mechanism SM is switched to the “S1” state, the carrier Cf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 are connected, and the second switching clutch Cb, the third brake B3, and the lockup clutch LC are connected. , The rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is "1", the rotational speed at the vertical line Y4 is "8th", and the eighth speed stage is established Is done.

同期噛合機構ＳＭを前記「Ｓ１」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のキャリアＣｍとを連結させ、第１切換クラッチＣａと第１ブレーキＢ１と第３ブレーキＢ３とを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ３での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ１」となって、後進１速段が確立される。   The synchronous meshing mechanism SM is switched to the “S1” state, the carrier Cf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 are connected, and the first switching clutch Ca, the first brake B1, and the third brake B3. , The rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, the rotational speed at the vertical line Y4 is “Rev1”, and the reverse speed is 1st. A stage is established.

同期噛合機構ＳＭを前記「Ｓ１」の状態に切り替えて、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のキャリアＣｍとを連結させ、第２切換クラッチＣｂと第１ブレーキＢ１と第３ブレーキＢ３とを係合させると、縦線Ｙ１での回転速度がＮ１、縦線Ｙ２での回転速度が「０」となり、縦線Ｙ４での回転速度がマイナスの「Ｒｅｖ２」となって、後進２速段が確立される。   The synchronous meshing mechanism SM is switched to the “S1” state, the carrier Cf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 are connected, and the second switching clutch Cb, the first brake B1, and the third brake B3. , The rotational speed at the vertical line Y1 is N1, the rotational speed at the vertical line Y2 is “0”, the rotational speed at the vertical line Y4 is “Rev2”, and the reverse second speed A stage is established.

図６（ｂ）は、上述した各変速段と同期噛合機構ＳＭの状態とクラッチＣａ，Ｃｂ、ブレーキＢ１、Ｂ３、ロックアップクラッチＬＣ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。又、図６（ｂ）は、第１プラネタリギヤ５のギヤ比ｉを１．４、第２プラネタリギヤ６のギヤ比ｊを２．４、第３プラネタリギヤ７のギヤ比ｋを１．７とした場合における各変速段のギヤレシオ（第１入力軸４１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）およびレシオレンジ（１速段と８速段のギヤレシオの比（図６（ｂ）の１速段のギヤレシオの右隣の欄に表示））が適切になる。   FIG. 6B is a diagram summarizing and displaying the relationship between the above-described shift speeds and the state of the synchronous mesh mechanism SM and the engagement states of the clutches Ca, Cb, the brakes B1 and B3, and the lockup clutch LC. “◯” represents engagement. FIG. 6B shows the case where the gear ratio i of the first planetary gear 5 is 1.4, the gear ratio j of the second planetary gear 6 is 2.4, and the gear ratio k of the third planetary gear 7 is 1.7. 6 also shows the gear ratio of each gear stage (the rotational speed of the first input shaft 41 / the rotational speed of the output gear 3). According to this, the common ratio (ratio of the gear ratio between each gear) and the ratio orange (ratio of the gear ratio of the first gear to the eighth gear (the gear ratio of the first gear in FIG. 6B) Display)) is appropriate.

第４実施形態の自動変速機によれば、第１実施形態のものと比較して、２つのクラッチＣ１，Ｃ２を同期噛合機構ＳＭと第３ブレーキＢ３とに置き換えられることとなるため、換言すれば、１つの係合要素がフリクションロスの少ない同期噛合機構ＳＭに置き換えられることとなることにより、フリクションロスをより低減させることができる。尚、第４実施形態のものにおいても、第３実施形態のように、第２プラネタリギヤ６の第４要素たるキャリアＣｍを変速機ケース３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係合要素たるブレーキを追加すれば、前進１０段の変速を行うことができる。   According to the automatic transmission of the fourth embodiment, the two clutches C1 and C2 can be replaced with the synchronous meshing mechanism SM and the third brake B3 as compared with the first embodiment. For example, the friction loss can be further reduced by replacing one engagement element with the synchronous meshing mechanism SM with little friction loss. In the fourth embodiment, as in the third embodiment, the carrier Cm as the fourth element of the second planetary gear 6 can be switched between a state in which the carrier Cm is fixed to the transmission case 3 and a state in which the fixing is released. If a brake, which is a simple engagement element, is added, it is possible to perform a forward shift of 10 stages.

次に、図８、図９を参照して、本発明の第５実施形態の自動変速機を説明する。第５実施形態の自動変速機は、第１実施形態と同一の流体トルクコンバータ１と第１，第２入力部材たる第１，第２入力軸４１，４２とを備えている。又、第５実施形態の自動変速機は、第１，第２入力軸４１，４２と平行に配置した出力部材たる出力軸８とを備えている。出力軸８の回転は、出力軸８に固定の出力ギヤ８ａに噛合するファイナルドリブンギヤ８ｂを固定したデファレンシャルギヤＤｆを介して車両の左右の駆動輪に伝達される。   Next, an automatic transmission according to a fifth embodiment of the present invention will be described with reference to FIGS. The automatic transmission according to the fifth embodiment includes the same fluid torque converter 1 as that of the first embodiment and first and second input shafts 41 and 42 as first and second input members. The automatic transmission according to the fifth embodiment includes an output shaft 8 as an output member arranged in parallel with the first and second input shafts 41 and 42. The rotation of the output shaft 8 is transmitted to the left and right drive wheels of the vehicle via a differential gear Df in which a final driven gear 8b meshed with an output gear 8a fixed to the output shaft 8 is fixed.

又、変速機ケース３内には、第１プラネタリギヤ５と第２プラネタリギヤ６とが入力軸４１，４２と同心に配置されている。第１プラネタリギヤ５は、サンギヤＳｆと、リングギヤＲｆと、サンギヤＳｆとリングギヤＲｆとに噛合するピニオン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。   In the transmission case 3, the first planetary gear 5 and the second planetary gear 6 are disposed concentrically with the input shafts 41 and 42. The first planetary gear 5 is formed of a single pinion type planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the sun gear Sf and the ring gear Rf so as to freely rotate and revolve.

図９の下段に示す第１プラネタリギヤ５の速度線図（サンギヤ、キャリア、リングギヤの３個の要素の回転速度を直線で表すことができる図）を参照して、第１プラネタリギヤ５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要素はキャリアＣｆ、第３要素はリングギヤＲｆになる。ここで、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５のギヤ比（リングギヤの歯数／サンギヤの歯数）をｉとして、ｉ：１に設定される。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 a speed diagram of the first planetary gear 5 shown in the lower part of FIG. 9 (a diagram in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), the sun gear Sf of the first planetary gear 5 Assuming that the three elements comprising the carrier Cf and the ring gear Rf are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, the first element is the sun gear Sf. The second element is the carrier Cf, and the third element is the ring gear Rf. Here, 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 i: 1 where the gear ratio of the first planetary gear 5 (number of teeth of the ring gear / number of teeth of the sun gear) is i. Set to 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プラネタリギヤ６は、第１プラネタリギヤ５と同様に、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ている。   Similar to the first planetary gear 5, the second planetary gear 6 is a single pinion type comprising a sun gear Sm, a ring gear Rm, and a carrier Cm that supports the sun gear Sm and the ring gear Rm so as to rotate and revolve. It is composed of planetary gears.

図９の上段に示す第２プラネタリギヤ６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 second planetary gear 6 shown in the upper part of FIG. 9, three elements including the sun gear Sm, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are separated by a distance corresponding to the gear ratio in the speed diagram. If the fourth element, the fifth element, and the sixth element are respectively arranged from the left side in the order of arrangement, 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.

第１プラネタリギヤ５のリングギヤＲf（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）とは互いに連結されて、連結体Ｒｆ，Ｓｍを構成している。又、第１プラネタリギヤ５のキャリアＣｆ（第２要素）は、キャリアＣｆに固定の駆動ギヤＧ１ａと、駆動ギヤＧ１ａに噛合する出力軸８に固定の従動ギヤＧ１ｂとから成る第１ギヤ列Ｇ１を介して出力軸８に連結され、第２プラネタリギヤ６のキャリアＣｍ（第５要素）は、キャリアＣｍに固定の駆動ギヤＧ２ａと、駆動ギヤＧ２ａに噛合する出力軸８に固定の従動ギヤＧ２ｂとから成る第２ギヤ列Ｇ２を介して出力軸８に連結されている。第２プラネタリギヤのリングギヤＲｍ（第６要素）は、第２入力軸４２と連結されている。   The ring gear Rf (third element) of the first planetary gear 5 and the sun gear Sm (fourth element) of the second planetary gear 6 are connected to each other to form a connected body Rf, Sm. The carrier Cf (second element) of the first planetary gear 5 has a first gear train G1 including a drive gear G1a fixed to the carrier Cf and a driven gear G1b fixed to the output shaft 8 meshing with the drive gear G1a. The carrier Cm (fifth element) of the second planetary gear 6 is connected to the output shaft 8 through a drive gear G2a fixed to the carrier Cm and a driven gear G2b fixed to the output shaft 8 meshing with the drive gear G2a. It is connected to the output shaft 8 through a second gear train G2. A ring gear Rm (sixth element) of the second planetary gear is connected to the second input shaft 42.

ここで、第１ギヤ列Ｇ１のギヤ比（従動ギヤの歯数／駆動ギヤの歯数）をｐ、第２ギヤ列Ｇ２のギヤ比をｑとして、ｐ＞ｑになっている。また、第１プラネタリギヤ５のキャリアＣｆと第２プラネタリギヤ６のキャリアＣｍは、両ギヤ列Ｇ１，Ｇ２を介して出力軸８で連結されることになる。そして、第２プラネタリギヤ６のキャリアＣｍは、第１プラネタリギヤ５のキャリアＣｆの回転速度のｑ／ｐの速度で回転する。   Here, p> q, where p is the gear ratio of the first gear train G1 (number of teeth of the driven gear / number of teeth of the drive gear) and q is the gear ratio of the second gear train G2. Further, the carrier Cf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 are connected by the output shaft 8 via both gear trains G1 and G2. The carrier Cm of the second planetary gear 6 rotates at a speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5.

又、第５実施形態では、係合要素として、第１プラネタリギヤ５のサンギヤＳｆ（第１要素）と第１入力軸４１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、連結体Ｒｆ，Ｓｍ（第３要素、第４要素）と第１入力軸４１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、第１プラネタリギヤ５のサンギヤＳｆ（第１要素）を変速機ケース３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２プラネタリギヤ６のリングギヤＲｍ（第６要素）を変速機ケース３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とを備えている。   Further, in the fifth embodiment, as the engagement element, the first engagement switchable between a state in which the sun gear Sf (first element) of the first planetary gear 5 and the first input shaft 41 are connected and a state in which the connection is cut off. A second engagement element that can be switched between a state in which the first clutch C1, which is a combination element, the connecting bodies Rf and Sm (third element and fourth element), and the first input shaft 41 are connected and a state in which the connection is cut off. The first brake B1 as a third engagement element that can be switched between a state in which the second clutch C2 and the sun gear Sf (first element) of the first planetary gear 5 are fixed to the transmission case 3 and a state in which the fixing is released. And a second brake B2 that is a fourth engagement element that can be switched between a state in which the ring gear Rm (sixth element) of the second planetary gear 6 is fixed to the transmission case 3 and a state in which the fixation is released. .

第５実施形態においては、第２クラッチＣ２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の回転速度が「１」、第２プラネタリギヤ６のリングギヤＲｍの回転速度が「０」になり、第２プラネタリギヤ６の速度線が図９に「１ｓｔ」で示す線になる。そして、第２プラネタリギヤ６のキャリアＣｍの回転速度はｊ／（ｊ＋１）になり、出力軸８が第２ギヤ列Ｇ２を介してｊ／｛（ｊ＋１）ｑ｝の速度で回転して、１速段が確立される。   In the fifth embodiment, when the second clutch C2 and the second brake B2 are engaged, the rotational speed of the sun gear Sm of the second planetary gear 6 is “1”, and the rotational speed of the ring gear Rm of the second planetary gear 6 is “ 0 ", and the speed line of the second planetary gear 6 becomes a line indicated by" 1st "in FIG. The rotation speed of the carrier Cm of the second planetary gear 6 is j / (j + 1), and the output shaft 8 rotates at a speed of j / {(j + 1) q} via the second gear train G2. A stage 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の回転速度と第１プラネタリギヤ５のリングギヤＲｆの回転速度とが共に「１」になると共に、第１プラネタリギヤ５のサンギヤＳｆの回転速度が「０」になり、第１プラネタリギヤ５の速度線は図９に「２ｎｄ」で示す線になる。そして、第１プラネタリギヤ５のキャリアＣｆの回転速度はｉ／（ｉ＋１）、出力軸８がｉ／｛（ｉ＋１）ｐ}の速度で回転して、２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 sun gear Sm of the second planetary gear 6 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear. The rotational speed of the sun gear Sf of No. 5 becomes “0”, and the speed line of the first planetary gear 5 becomes a line indicated by “2nd” in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 is i / (i + 1), the output shaft 8 rotates at a speed of i / {(i + 1) p}, and the second 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１プラネタリギヤ５のサンギヤＳｆの回転速度と第１プラネタリギヤ５のリングギヤＲｆの回転速度とが共に「１」になって、第１プラネタリギヤ５がロック状態になり、第１プラネタリギヤ５の速度線は図９に「３ｒｄ」で示す線になる。そして、第１プラネタリギヤ５のキャリアＣｆの回転速度は「１」になり、出力軸８が１／ｐの速度で回転して、３速段が確立される。   When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear. 5 is locked, and the speed line of the first planetary gear 5 is a line indicated by “3rd” in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 becomes “1”, the output shaft 8 rotates at a speed of 1 / p, and the third speed stage is established.

第２クラッチＣ２とロックアップクラッチＬＣとを係合させると、第２プラネタリギヤ６のサンギヤＳｍの回転速度と第２プラネタリギヤ６のリングギヤＲｍの回転速度とが共に「１」になって、第２プラネタリギヤ６がロック状態になり、第２プラネタリギヤ６の速度線は図９に「４ｔｈ」で示す線になる。そして、第２プラネタリギヤ６のキャリアＣｍのの回転速度は「１」になり、出力軸８が１／ｑの速度で回転して、４速段が確立される。第５実施形態では、４速段以上の変速段においてはロックアップクラッチＬＣを係合させてトルクコンバータにおけるスリップを防止することで燃費の向上を図るように構成されている。   When the second clutch C2 and the lockup clutch LC are engaged, both the rotational speed of the sun gear Sm of the second planetary gear 6 and the rotational speed of the ring gear Rm of the second planetary gear 6 become “1”, and the second planetary gear 6 is in a locked state, and the speed line of the second planetary gear 6 is a line indicated by “4th” in FIG. Then, the rotation speed of the carrier Cm of the second planetary gear 6 becomes “1”, the output shaft 8 rotates at a speed of 1 / q, and the fourth speed stage is established. The fifth embodiment is configured to improve fuel efficiency by engaging the lock-up clutch LC and preventing slippage in the torque converter at the fourth speed or higher.

第１クラッチＣ１とロックアップクラッチＬＣとを係合させると、第１プラネタリギヤ５のサンギヤＳｆの回転速度と第２プラネタリギヤ６のリングギヤＲｍの回転速度とが共に「１」になると共に、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤ６のサンギヤＳｍとが等速度で回転し、第２プラネタリギヤ６のキャリアＣｍが第１プラネタリギヤ５のキャリアＣｆのｑ／ｐの速度で回転して、第１プラネタリギヤ５と第２プラネタリギヤ６の速度線は図９に「５ｔｈ」で示す線になる。そして、第１プラネタリギヤのキャリアＣｆの回転速度は（１−ｉｊ）ｐ／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝、第２プラネタリギヤ６のキャリアＣｍの回転速度は（１−ｉｊ）ｑ／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝になり、出力軸８が（１−ｉｊ）／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝の速度で回転して、５速段が確立される。   When the first clutch C1 and the lockup clutch LC are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rm of the second planetary gear 6 both become “1”, and the first planetary gear. The ring gear Rf of the second planetary gear 6 and the sun gear Sm of the second planetary gear 6 rotate at the same speed, the carrier Cm of the second planetary gear 6 rotates at the speed of q / p of the carrier Cf of the first planetary gear 5, and the first planetary gear 5 The speed line of the second planetary gear 6 is a line indicated by “5th” in FIG. The rotation speed of the carrier Cf of the first planetary gear is (1-ij) p / {(i + 1) p- (j + 1) iq}, and the rotation speed of the carrier Cm of the second planetary gear 6 is (1-ij) q / { (I + 1) p- (j + 1) iq}, and the output shaft 8 rotates at a speed of (1-ij) / {(i + 1) p- (j + 1) iq} to establish the fifth gear.

ロックアップクラッチＬＣと第１ブレーキＢ１とを係合させると、第１プラネタリギヤ５のサンギヤＳｆの回転速度が「０」、第２プラネタリギヤ６のリングギヤＲｍの回転速度が「１」になると共に、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤ６のサンギヤＳｍとが等速度で回転し、第２プラネタリギヤ６のキャリアＣｍが第１プラネタリギヤ５のキャリアＣｆのｑ／ｐの速度で回転して、第１プラネタリギヤ５と第２プラネタリギヤ６の速度線は図９に「６ｔｈ」で示す線になる。そして、第１プラネタリギヤのキャリアＣｆの回転速度はｉｊｐ／｛（ｊ＋１）ｉｑ−（ｉ＋１）ｐ｝、第２プラネタリギヤ６のキャリアＣｍの回転速度はｉｊｑ／｛（ｊ＋１）ｉｑ−（ｉ＋１）ｐ｝になり、出力軸８がｉｊ／｛（ｊ＋１）ｉｑ−（ｉ＋１）ｐ｝の速度で回転して、６速段が確立される。   When the lockup clutch LC and the first brake B1 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “0”, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes “1”, and The ring gear Rf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6 rotate at the same speed, the carrier Cm of the second planetary gear 6 rotates at the speed of q / p of the carrier Cf of the first planetary gear 5, and the first planetary gear 5 rotates. The speed lines of the planetary gear 5 and the second planetary gear 6 are indicated by “6th” in FIG. The rotation speed of the carrier Cf of the first planetary gear is ijp / {(j + 1) iq− (i + 1) p}, and the rotation speed of the carrier Cm of the second planetary gear 6 is ijq / {(j + 1) iq− (i + 1) p}. The output shaft 8 rotates at a speed of ij / {(j + 1) iq- (i + 1) p}, and the sixth 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１プラネタリギヤ５のサンギヤＳｆの回転速度が「１」、第２プラネタリギヤ６のリングギヤＲｍの回転速度が「０」になると共に、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤ６のサンギヤＳｍとが等速度で回転し、第２プラネタリギヤ６のキャリアＣｍが第１プラネタリギヤ５のキャリアＣｆのｑ／ｐの速度で回転して、第１プラネタリギヤ５と第２プラネタリギヤ６の速度線は図９に「Ｒｅｖ」で示す線になる。そして、第１プラネタリギヤのキャリアＣｆの回転速度はｐ／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝、第２プラネタリギヤ６のキャリアＣｒの回転速度はｑ／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝になり、出力軸８が１／｛（ｉ＋１）ｐ−（ｊ＋１）ｉｑ｝の速度で回転して、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 sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6 rotate at the same speed, the carrier Cm of the second planetary gear 6 rotates at the speed of q / p of the carrier Cf of the first planetary gear 5, and the first planetary gear 5 rotates. The speed lines of the planetary gear 5 and the second planetary gear 6 are indicated by “Rev” in FIG. The rotational speed of the carrier Cf of the first planetary gear is p / {(i + 1) p- (j + 1) iq}, and the rotational speed of the carrier Cr of the second planetary gear 6 is q / {(i + 1) p- (j + 1) iq}. The output shaft 8 rotates at a speed of 1 / {(i + 1) p- (j + 1) iq}, and the reverse gear is established.

尚、図９中の点線で示す速度線は、第１と第２の両プラネタリギヤ５，６のうち動力伝達する一方のプラネタリギヤに追従して他方のプラネタリギヤの各要素が回転することを表している。   A speed line indicated by a dotted line in FIG. 9 represents that each element of the other planetary gear rotates following the one of the first and second planetary gears 5 and 6 that transmits power. .

図８（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２、ブレーキＢ１，Ｂ２、ロックアップクラッチＬＣ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８（ｂ）は、第１プラネタリギヤ５のギヤ比ｉを２．５５、第２プラネタリギヤ６のギヤ比ｊを２．５５、第１ギヤ列Ｇ１のギヤ比ｐを１．４２、第２ギヤ列Ｇ２のギヤ比ｑを１．００とした場合における各変速段のギヤレシオ（第１入力軸４１の回転速度／出力軸８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（１速レシオ／６速レシオ）も適切になる。   FIG. 8 (b) is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, the brakes B1, B2, and the lock-up clutch LC. Represents. FIG. 8B shows that the gear ratio i of the first planetary gear 5 is 2.55, the gear ratio j of the second planetary gear 6 is 2.55, the gear ratio p of the first gear train G1 is 1.42, Also shown is the gear ratio (rotational speed of the first input shaft 41 / rotational speed of the output shaft 8) of each gear when the gear ratio q of the two gear train G2 is 1.00. According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (1st speed ratio / 6th speed ratio) becomes appropriate.

第５実施形態の自動変速機によれば、ロックアップクラッチＬＣを除くクラッチＣ１，Ｃ２、ブレーキＢ１，Ｂ２の４つの係合要素で、前進６段の変速を行うことができる。又、プラネタリギヤとして第１と第２の２つのプラネタリギヤ５，６を用いるだけであるため、３つのプラネタリギヤを用いるものに比し、変速機の軸長を短縮できる。更に、５速段と６速段と後進段以外の変速段では第１と第２の両プラネタリギヤ５，６の片方のプラネタリギヤ単独での動力伝達が行われると共に、３速段と４速段とにおいて夫々第１プラネタリギヤ５と第２プラネタリギヤ６とがロック状態になるため、噛合伝達効率は１００％になり、全ての変速段のトータルの伝達効率が向上する。   According to the automatic transmission of the fifth embodiment, it is possible to perform a forward six-speed shift with the four engagement elements of the clutches C1 and C2 and the brakes B1 and B2 excluding the lockup clutch LC. Further, since only the first and second planetary gears 5 and 6 are used as planetary gears, the shaft length of the transmission can be shortened as compared with the one using three planetary gears. Further, at the speeds other than the fifth speed stage, the sixth speed stage, and the reverse speed stage, power is transmitted by only one of the first and second planetary gears 5 and 6, and the third speed stage and the fourth speed stage. Since each of the first planetary gear 5 and the second planetary gear 6 is in the locked state, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the gears is improved.

尚、第５実施形態では、第１と第２の各プラネタリギヤ５，６をシングルピニオン型のプラネタリギヤで構成したが、ダブルピニオン型のプラネタリギヤで第１プラネタリギヤ５や第２プラネタリギヤ６を構成することも可能である。第１プラネタリギヤ５をダブルピニオン型のプラネタリギヤで構成した場合、サンギヤとキャリアとの一方が第１要素、リングギヤが第２要素、サンギヤとキャリアとの他方が第３要素になる。また、第２プラネタリギヤ６をダブルピニオン型のプラネタリギヤで構成した場合、サンギヤとキャリアとの一方が第４要素、リングギヤが第５要素、サンギヤとキャリアとの他方が第６要素になる。   In the fifth embodiment, each of the first and second planetary gears 5 and 6 is constituted by a single pinion type planetary gear. However, the first planetary gear 5 and the second planetary gear 6 may be constituted by a double pinion type planetary gear. Is possible. When the first planetary gear 5 is formed of a double pinion type planetary gear, one of the sun gear and the carrier is the first element, the ring gear is the second element, and the other of the sun gear and the carrier is the third element. When the second planetary gear 6 is constituted by a double pinion type planetary gear, one of the sun gear and the carrier is the fourth element, the ring gear is the fifth element, and the other of the sun gear and the carrier is the sixth element.

又、第５実施形態では、入力軸４１，４２の周りに、一端側から順に、第１クラッチＣ１と、第１ブレーキＢ１と、第１ギヤ列Ｇ１と、第１プラネタリギヤ５と、第２ギヤ列Ｇ２と、第２プラネタリギヤ６及び第２ブレーキＢ２と、第２クラッチＣ２とを配置したが、これに限定されない。例えば、第１ブレーキＢ１と第２ブレーキＢ２との間に、第１プラネタリギヤ５と第１ギヤ列Ｇ１と第２ギヤ列Ｇ２とを順に配置してもよい。また、第１ブレーキＢ１と第２ブレーキＢ２との間に、第１ギヤ列Ｇ１と、第２ギヤ列Ｇ２と、第１プラネタリギヤ５とを配置してもよい。   In the fifth embodiment, the first clutch C1, the first brake B1, the first gear train G1, the first planetary gear 5, and the second gear are sequentially arranged around the input shafts 41 and 42 from one end side. Although the row G2, the second planetary gear 6, the second brake B2, and the second clutch C2 are arranged, the present invention is not limited to this. For example, the first planetary gear 5, the first gear train G1, and the second gear train G2 may be sequentially disposed between the first brake B1 and the second brake B2. Further, the first gear train G1, the second gear train G2, and the first planetary gear 5 may be disposed between the first brake B1 and the second brake B2.

又、第２プラネタリギヤ６を第１プラネタリギヤ５の径方向外側に配置し、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤ６のサンギヤＳｍとを一体にして連結体Ｒｆ，Ｓｍを構成するようにしてもよい。このように構成すれば、更に変速機の軸長を短くすることができる。この場合、第１クラッチＣ１を第２クラッチＣ２の径方向内側に配置させることもできる。   Further, the second planetary gear 6 is arranged on the radially outer side of the first planetary gear 5, and the ring gear Rf of the first planetary gear 5 and the sun gear Sm of the second planetary gear 6 are integrated to form a coupling body Rf, Sm. Also good. If comprised in this way, the axial length of a transmission can be shortened further. In this case, the first clutch C1 can be disposed radially inside the second clutch C2.

次に、図１０、図１１を参照して、第６実施形態の自動変速機を説明する。変速機ケース３内には、第１プラネタリギヤ５と第２プラネタリギヤ６とが入力軸と同心に配置されている。第１プラネタリギヤ５は、サンギヤＳｆと、リングギヤＲｆと、サンギヤＳｆとリングギヤＲｆとに噛合するピニオン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。   Next, an automatic transmission according to a sixth embodiment will be described with reference to FIGS. 10 and 11. In the transmission case 3, the first planetary gear 5 and the second planetary gear 6 are disposed concentrically with the input shaft. The first planetary gear 5 is formed of a single pinion type planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the sun gear Sf and the ring gear Rf so as to freely rotate and revolve.

図１１の下段に示す第１プラネタリギヤ５の速度線図（サンギヤ、キャリア、リングギヤの３個の要素の回転速度を直線で表すことができる図）を参照して、第１プラネタリギヤ５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要素はキャリアＣｆ、第３要素はリングギヤＲｆになる。ここで、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５のギヤ比（リングギヤの歯数／サンギヤの歯数）をｉとして、ｉ：１に設定される。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 a speed diagram of the first planetary gear 5 shown in the lower part of FIG. 11 (a diagram in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), the sun gear Sf of the first planetary gear 5 Assuming that the three elements comprising the carrier Cf and the ring gear Rf are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, the first element is the sun gear Sf. The second element is the carrier Cf, and the third element is the ring gear Rf. Here, 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 i: 1 where the gear ratio of the first planetary gear 5 (number of teeth of the ring gear / number of teeth of the sun gear) is i. Set to 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プラネタリギヤ６は、入力軸方向に並ぶ一対のサンギヤＳｍ，Ｓｍ’と、リングギヤＲｍと、一対のサンギヤＳｍ，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とから成るプラネタリギヤで構成されている。一対のサンギヤＳｍ，Ｓｍ’は同一歯数に設定されている。   The second planetary gear 6 is a carrier Cm that supports a pair of sun gears Sm, Sm ′ aligned in the input shaft direction, a ring gear Rm, and a pinion Pm that meshes with the pair of sun gears Sm, Sm ′ and the ring gear Rm so as to rotate and revolve. It consists of a planetary gear consisting of The pair of sun gears Sm, Sm 'is set to the same number of teeth.

図１１の上段に示す第２プラネタリギヤ６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，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，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，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 second planetary gear 6 shown in the upper part of FIG. 11, the three elements including the sun gears Sm, Sm ′, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are converted into the gear ratio in the speed diagram. If the fourth element, the fifth element, and the sixth element are respectively arranged from the left side in the order of arrangement at the corresponding intervals, the fourth element is the sun gear Sm, 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 gears Sm, 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.

第１プラネタリギヤ５のサンギヤＳｆ（第１要素）は第１入力軸４１と連結されている。第２プラネタリギヤ６のキャリアＣｍ（第５要素）は第２入力軸４２と連結されている。第１プラネタリギヤ５のキャリアＣｆ（第２要素）は、キャリアＣｆに固定の駆動ギヤＧ１ａと、駆動ギヤＧ１ａに噛合する出力軸８に固定の従動ギヤＧ１ｂとから成る第１ギヤ列Ｇ１を介して出力軸８に連結されている。第２プラネタリギヤ６のリングギヤＲｍ（第６要素）は、リングギヤＲｍに固定の駆動ギヤＧ２ａと、駆動ギヤＧ２ａに噛合する出力軸８に固定の従動ギヤＧ２ｂとから成る第２ギヤ列Ｇ２を介して出力軸８に連結されている。尚、図１０（ａ）で、第２入力軸４２が第２プラネタリギヤ６のピニオンＰｍを貫通してキャリアＣｍ（第５要素）と連結しているように見えるが、実際には、ピニオンＰｍと接触しないようにピニオンＰｍに対しキャリアＣｍの回転方向に間隔を存して第２入力軸４２がキャリアＣｍと連結している。   The sun gear Sf (first element) of the first planetary gear 5 is connected to the first input shaft 41. The carrier Cm (fifth element) of the second planetary gear 6 is connected to the second input shaft 42. The carrier Cf (second element) of the first planetary gear 5 is connected via a first gear train G1 including a drive gear G1a fixed to the carrier Cf and a driven gear G1b fixed to the output shaft 8 meshing with the drive gear G1a. It is connected to the output shaft 8. The ring gear Rm (sixth element) of the second planetary gear 6 is connected via a second gear train G2 including a drive gear G2a fixed to the ring gear Rm and a driven gear G2b fixed to the output shaft 8 meshing with the drive gear G2a. It is connected to the output shaft 8. In FIG. 10 (a), the second input shaft 42 seems to pass through the pinion Pm of the second planetary gear 6 and be connected to the carrier Cm (fifth element). The second input shaft 42 is connected to the carrier Cm with an interval in the rotation direction of the carrier Cm with respect to the pinion Pm so as not to contact.

又、第６実施形態の自動変速機では、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）と第１入力軸４１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５のリングギヤＲｆ（第３要素）と第２プラネタリギヤ６のキャリアＣｍ（第５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３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２プラネタリギヤ６のキャリアＣｍ（第５要素）を変速機ケース３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とを備えている。他の構成は第５実施形態と同一である。   In the automatic transmission according to the sixth embodiment, the engagement element can be switched between a state in which the sun gear Sm (fourth element) of the second planetary gear 6 and the first input shaft 41 are connected and a state in which the connection is disconnected. A state in which the first clutch C1, which is a first engaging element, the ring gear Rf (third element) of the first planetary gear 5 and the carrier Cm (fifth element) of the second planetary gear 6 are connected, and a state in which this connection is broken. The second clutch C2, which is a second engaging element that can be switched to the second gear, and the sun gear Sm ′ (fourth element) of the second planetary gear 6 can be switched between a state in which it is fixed to the transmission case 3 and a state in which this fixing is released. A fourth engagement element that can be switched between a state in which the first brake B1 as the third engagement element and the carrier Cm (fifth element) of the second planetary gear 6 are fixed to the transmission case 3 and a state in which the fixation is released. 2nd And a rake B2. Other configurations are the same as those of the fifth embodiment.

第６実施形態においては、第２クラッチＣ２と第２ブレーキＢ２とを係合させると、第１プラネタリギヤ５のサンギヤＳｆの回転速度が「１」、第１プラネタリギヤ５のリングギヤＲｆの回転速度が「０」になり、第１プラネタリギヤ５の速度線が図１１に「１ｓｔ」で示す線になり、１速段が確立される。   In the sixth embodiment, when the second clutch C2 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1” and the rotational speed of the ring gear Rf of the first planetary gear 5 is “ 0 ", the speed line of the first planetary gear 5 becomes a line indicated by" 1st "in FIG. 11, and the first 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１プラネタリギヤ５のサンギヤＳｆの回転速度が「１」、第２プラネタリギヤ６のサンギヤＳｍの回転速度が「０」になり、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤのキャリアＣｍとが等速度で回転し、第１，第２プラネタリギヤ５，６の速度線は図１１に「２ｎｄ」で示す線になって、２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 sun gear Sf of the first planetary gear 5 is "1", the rotational speed of the sun gear Sm of the second planetary gear 6 is "0", and the first The ring gear Rf of the planetary gear 5 and the carrier Cm of the second planetary gear rotate at the same speed, and the speed lines of the first and second planetary gears 5 and 6 become a line indicated by “2nd” in FIG. 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１プラネタリギヤ５のサンギヤＳｆの回転速度と第２プラネタリギヤ６のサンギヤＳｍの回転速度とが共に「１」になって、第１プラネタリギヤ５のリングギヤＲｆと第２プラネタリギヤのキャリアＣｍとが等速度で回転し、第１，第２プラネタリギヤ５，６の速度線は図１１に「３ｒｄ」で示す線になり、３速段が確立される。   When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sm of the second planetary gear 6 both become “1”, and the first planetary gear The ring gear Rf of No. 5 and the carrier Cm of the second planetary gear rotate at the same speed, and the speed lines of the first and second planetary gears 5 and 6 become a line indicated by “3rd” in FIG. The

第２クラッチＣ２とロックアップクラッチＬＣとを係合させると、第１プラネタリギヤ５のサンギヤＳｆの回転速度と第１プラネタリギヤ５のリングギヤＲｆの回転速度とが共に「１」になり、第１プラネタリギヤ５がロック状態になって、第１プラネタリギヤ５の速度線は図１１に「４ｔｈ」で示す線になり、４速段が確立される。第６実施形態では、４速段以上の変速段においてはロックアップクラッチＬＣを係合させてトルクコンバータにおけるスリップを防止することで燃費の向上を図るように構成されている。   When the second clutch C2 and the lockup clutch LC are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear 5 Is in a locked state, the speed line of the first planetary gear 5 becomes a line indicated by “4th” in FIG. 11, and the fourth speed stage is established. The sixth embodiment is configured to improve fuel efficiency by engaging the lock-up clutch LC and preventing slippage in the torque converter at the fourth speed or higher.

第１クラッチＣ１とロックアップクラッチＬＣとを係合させると、第２プラネタリギヤ６のサンギヤＳｍの回転速度と第２プラネタリギヤ６のキャリアＣｍの回転速度とが共に「１」になって、第２プラネタリギヤ６がロック状態になり、第２プラネタリギヤ６の速度線は図１１に「５ｔｈ」で示す線になって、５速段が確立される。   When the first clutch C1 and the lockup clutch LC are engaged, the rotational speed of the sun gear Sm of the second planetary gear 6 and the rotational speed of the carrier Cm of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is locked, and the speed line of the second planetary gear 6 becomes a line indicated by “5th” in FIG.

ロックアップクラッチＬＣ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’の回転速度が「０」、第２プラネタリギヤ６のキャリアＣｍの回転速度が「１」になって、第２プラネタリギヤ６の速度線は図１１に「６ｔｈ」で示す線になり、６速段が確立される。   When the lockup clutch LC and the first brake B1 are engaged, the rotational speed of the sun gear Sm ′ of the second planetary gear 6 becomes “0”, and the rotational speed of the carrier Cm of the second planetary gear 6 becomes “1”. The speed line of the second planetary gear 6 is a line indicated by “6th” in FIG. 11, and the sixth speed stage 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の回転速度が「１」、第２プラネタリギヤ６のキャリアＣｍの回転速度が「０」になり、第２プラネタリギヤ６の速度線は図１１に「Ｒｅｖ」で示す線になって、後進段が確立される。   When the first clutch C1 and the second brake B2 are engaged, the rotation speed of the sun gear Sm of the second planetary gear 6 becomes “1”, the rotation speed of the carrier Cm of the second planetary gear 6 becomes “0”, and the second The speed line of the planetary gear 6 becomes a line indicated by “Rev” in FIG. 11, and the reverse speed is established.

尚、図１１中の点線で示す速度線は、第１と第２の両プラネタリギヤ５，６のうち動力伝達する一方のプラネタリギヤに追従して他方のプラネタリギヤの各要素が回転することを表している。   A speed line indicated by a dotted line in FIG. 11 represents that each element of the other planetary gear rotates following the one of the first and second planetary gears 5 and 6 that transmits power. .

図１０（ｂ）は、上述した各変速段とクラッチＣ１，Ｃ２、ブレーキＢ１，Ｂ２、ロックアップクラッチＬＣ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１０（ｂ）は、第１プラネタリギヤ５のギヤ比ｉを２．５５、第２プラネタリギヤ６のギヤ比ｊを２．５５、第１ギヤ列Ｇ１のギヤ比ｐを１．４２、第２ギヤ列Ｇ２のギヤ比ｑを１．００とした場合における各変速段のギヤレシオ（第１入力軸４１の回転速度／出力軸８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（１速レシオ／６速レシオ）も適切になる。   FIG. 10 (b) is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, the brakes B1, B2, and the lock-up clutch LC. Represents. FIG. 10B shows a gear ratio i of the first planetary gear 5 of 2.55, a gear ratio j of the second planetary gear 6 of 2.55, a gear ratio p of the first gear train G1 of 1.42, Also shown is the gear ratio (rotational speed of the first input shaft 41 / rotational speed of the output shaft 8) of each gear when the gear ratio q of the two gear train G2 is 1.00. According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (1st speed ratio / 6th speed ratio) becomes appropriate.

第６実施形態の自動変速機によれば、第５実施形態のものと同様に、ロックアップクラッチＬＣを除くクラッチＣ１，Ｃ２、ブレーキＢ１，Ｂ２の４つの係合要素で、前進６段の変速を行うことができる。又、２速段と３速段以外の変速段では第１と第２の両プラネタリギヤ５，６の片方のプラネタリギヤ単独での動力伝達が行われると共に、４速段と５速段とにおいて夫々第１プラネタリギヤ５と第２プラネタリギヤ６とがロック状態になるため、噛合伝達効率は１００％になり、全ての変速段のトータルの伝達効率が向上する。   According to the automatic transmission of the sixth embodiment, as in the fifth embodiment, the four engagement elements of the clutches C1 and C2 and the brakes B1 and B2 excluding the lockup clutch LC are used to change the forward six-speed shift. It can be performed. Further, at the speeds other than the second speed stage and the third speed stage, power is transmitted by only one of the first and second planetary gears 5 and 6, and at the fourth speed stage and the fifth speed stage, respectively. Since the first planetary gear 5 and the second planetary gear 6 are in a locked state, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the gears is improved.

尚、何れの実施形態の自動変速機もＦＦ車用のもの又はＦＲ車用のものとすることができる。例えば、第５，第６実施形態の自動変速機においては、出力軸８にプロペラシャフトを連結すればＦＲ車用となる。   Note that the automatic transmission according to any of the embodiments can be used for an FF vehicle or an FR vehicle. For example, in the automatic transmissions of the fifth and sixth embodiments, if a propeller shaft is connected to the output shaft 8, it will be for an FR vehicle.

（ａ）本発明の自動変速機の第１実施形態のスケルトン図、（ｂ）第１実施形態の各変速段での各係合要素の係合状態を纏めて示した図。(A) Skeleton diagram of the first embodiment of the automatic transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear position of the first embodiment. 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. 本発明の自動変速機の第２実施形態のスケルトン図。The skeleton figure of 2nd Embodiment of the automatic transmission of this invention. （ａ）本発明の自動変速機の第３実施形態のスケルトン図、（ｂ）第３実施形態の各変速段での各係合要素の係合状態を纏めて示した図。(A) Skeleton diagram of the third embodiment of the automatic transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear position of the third embodiment. 第３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 3rd Embodiment. （ａ）本発明の自動変速機の第４実施形態のスケルトン図、（ｂ）第４実施形態の各変速段での各係合要素の係合状態を纏めて示した図。(A) Skeleton diagram of the fourth embodiment of the automatic transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear position of the fourth embodiment. 第４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 4th Embodiment. （ａ）本発明の自動変速機の第５実施形態のスケルトン図、（ｂ）第５実施形態の各変速段での各係合要素の係合状態を纏めて示した図。(A) Skeleton diagram of the fifth embodiment of the automatic transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear position of the fifth embodiment. 第５実施形態の第１，第２プラネタリギヤの速度線図。The speed diagram of the 1st, 2nd planetary gear of 5th Embodiment. （ａ）本発明の自動変速機の第６実施形態のスケルトン図、（ｂ）第６実施形態の各変速段での各係合要素の係合状態を纏めて示した図。(A) Skeleton diagram of the sixth embodiment of the automatic transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear position of the sixth embodiment. 第６実施形態の第１，第２プラネタリギヤの速度線図。The speed diagram of the 1st, 2nd planetary gear of 6th Embodiment.

符号の説明Explanation of symbols

１…流体トルクコンバータ、２ａ…フライホイール、２ｂ…ダンパ、３…変速機ケース、４１…第１入力軸（第１入力部材）、４２…第２入力軸（第２入力部材）、４２ａ…第２入力軸用ディスク、５…第１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、８…出力軸（第５，６実施形態）、８ａ…出力ギヤ、８ｂ…ファイナルドリブンギヤ、Ｐｏ…ポンプ、Ｔａ…タービン、Ｓｔ…ステータ、ＬＣ…ロックアップクラッチ、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３要素）、Ｃｆ…第１プラネタリギヤのキャリア（第２要素）、Ｓｍ…第２プラネタリギヤのサンギヤ（第１〜第４実施形態の第６要素、第５，第６実施形態の第４要素）、Ｒｍ…第２プラネタリギヤのリングギヤ（第１〜第４実施形態の第５要素、第５，第６実施形態の第６要素）、Ｒｍ’…第２プラネタリギヤのリングギヤ（第３実施形態）、Ｃｍ…第２プラネタリギヤのキャリア（第１〜第４実施形態の第４要素、第５，第６実施形態の第５要素）、Ｓｒ…第３プラネタリギヤ７のサンギヤ（第７要素）、Ｒｒ…第３プラネタリギヤ７のリングギヤ（第９要素）、Ｃｒ…第３プラネタリギヤのキャリア（第８要素）、Ｐｆ，Ｐｍ，Ｐｍ’，Ｐｒ…ピニオン、Ｃ１…第１クラッチ（第１〜第３実施形態の第１係合要素又は第２係合要素、第５，６実施形態の第１係合要素）、Ｃ２…第２クラッチ（第１〜第３実施形態の第２係合要素又は第１係合要素、第５，６実施形態の第２係合要素）、Ｃａ…第１切換クラッチ（第１〜第３実施形態の第３係合要素、第４実施形態の第１係合要素）、Ｃｂ…第２切換クラッチ（第１〜第３実施形態の第４係合要素、第４実施形態の第２係合要素）、Ｂ１…第１ブレーキ（第１〜第３実施形態の第５係合要素、第４，第５，６実施形態の第３係合要素）、Ｂ２…第２ブレーキ（第１〜第３実施形態の第６係合要素、第５，６実施形態の第４係合要素）、Ｂ３…第３ブレーキ（第４実施形態の第４係合要素）、ＳＭ…同期噛合機構。 DESCRIPTION OF SYMBOLS 1 ... Fluid torque converter, 2a ... Flywheel, 2b ... Damper, 3 ... Transmission case, 41 ... 1st input shaft (1st input member), 42 ... 2nd input shaft (2nd input member), 42a ... 1st 2 Disc for input shaft, 5 ... 1st planetary gear, 6 ... 2nd planetary gear, 7 ... 3rd planetary gear, 8 ... Output shaft (5th, 6th embodiment), 8a ... Output gear, 8b ... Final driven gear, Po ... Pump , Ta ... turbine, St ... stator, LC ... lock-up clutch, Sf ... first planetary gear sun gear (first element), Rf ... first planetary gear ring gear (third element), Cf ... first planetary gear carrier (first 2 elements), Sm ... Sun gear of the second planetary gear (sixth element of the first to fourth embodiments, fourth element of the fifth and sixth embodiments), Rm ... second planetary Ring gear (the fifth element of the first to fourth embodiments, the sixth element of the fifth and sixth embodiments), Rm ′, the ring gear of the second planetary gear (third embodiment), and Cm, the second planetary gear. Carrier (fourth element of first to fourth embodiments, fifth element of fifth and sixth embodiments), Sr... Sun gear (seventh element) of third planetary gear 7, Rr... Ring gear (third planetary gear 7) Ninth element), Cr ... third planetary gear carrier (eighth element), Pf, Pm, Pm ', Pr ... pinion, C1 ... first clutch (first engaging element or first of the first to third embodiments) 2 engaging elements, first engaging elements of the fifth and sixth embodiments), C2... Second clutch (second engaging elements or first engaging elements of the first to third embodiments, fifth and sixth embodiments) Second engaging element), Ca ... first switching clutch (first to third embodiments) Third engagement element in the state, first engagement element in the fourth embodiment), Cb... Second switching clutch (fourth engagement element in the first to third embodiments, second engagement in the fourth embodiment) Element), B1... First brake (the fifth engagement element of the first to third embodiments, the third engagement element of the fourth, fifth and sixth embodiments), B2. 6th engagement element of 3rd embodiment, 4th engagement element of 5th, 6th embodiment), B3 ... 3rd brake (4th engagement element of 4th Embodiment), SM ... Synchronous meshing mechanism.

Claims (8)

ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、サンギヤ、キャリア及びリングギヤから成る３個の要素を有する複数のプラネタリギヤとを備え、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転をプラネタリギヤで複数段に変速して出力部材に出力する自動変速機であって、
入力部材は第１と第２の２つの入力部材で構成され、
第１入力部材はタービンに連結され、
第２入力部材は、ロックアップクラッチに介設された第２入力部材用ディスクと、プラネタリギヤの何れか１の要素とに連結され、ロックアップクラッチの係合で動力源の回転が伝達される状態となり、ロックアップクラッチの開放で動力源の回転の伝達を断たれる状態となり、
各プラネタリギヤは変速機ケース内に配置され、
第２入力部材に連結されるプラネタリギヤの要素は、前進１速段を確立する際に変速機ケースに固定される要素であり、
前記複数のプラネタリギヤは、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第２と第３の２つのプラネタリギヤとで構成され、
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５要素が第２入力部材に連結され、第６要素と第９要素とが連結されると共に、第８要素が出力部材に連結され、
第４要素と第６要素の何れか一方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態とこの状態を断つ状態とに切換自在な第１係合要素と、
第４要素と第６要素の何れか他方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態とこの状態を断つ状態とに切換自在な第２係合要素と、
第４要素と第７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３係合要素と、
第５要素と第７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４係合要素と、
第５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５係合要素とを備えることを特徴とする自動変速機。 A fluid torque converter comprising: a fluid torque converter having a lockup clutch for mechanically connecting a pump and a turbine and connected to a power source; and a plurality of planetary gears having three elements including a sun gear, a carrier, and a ring gear. An automatic transmission that shifts the rotation of an input member to which rotation of a power source is input via a planetary gear to a plurality of stages and outputs it to an output member,
The input member is composed of first and second input members,
The first input member is coupled to the turbine;
The second input member is connected to the second input member disk interposed in the lockup clutch and any one of the planetary gears, and the rotation of the power source is transmitted by the engagement of the lockup clutch. next, Ri Do a state cut off the transmission of rotation power source at the opening of the lock-up clutch,
Each planetary gear is placed in the transmission case,
The planetary gear element connected to the second input member is an element fixed to the transmission case when establishing the first forward speed,
The plurality of planetary gears includes a first planetary gear for input disposed in a transmission case, and second and third planetary gears for transmission,
The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are respectively arranged in the order corresponding to the gear ratio in the velocity diagram in the order of arrangement, and 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 five elements are connected to the second input member as the seventh element, the eighth element, and the ninth element, respectively, in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram, and the sixth element And the ninth element are coupled, and the eighth element is coupled to the output member,
A first engagement element switchable between a state in which the rotation of the first input member is transmitted to one of the fourth element and the sixth element via the first planetary gear and a state in which this state is cut off;
A second engagement element switchable between a state in which the rotation of the first input member is transmitted to the other of the fourth element and the sixth element via the first planetary gear and a state in which this state is cut off;
A third engagement element switchable between a state in which the fourth element and the seventh element are connected and a state in which the connection is broken;
A fourth engagement element switchable between a state in which the fifth element and the seventh element are connected and a state in which the connection is broken;
An automatic transmission comprising: a fifth engagement element that is switchable between a state in which the fifth element is fixed to the transmission case and a state in which the fixation is released. 請求項１記載の自動変速機であって、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係合要素を備えることを特徴とする自動変速機。  2. The automatic transmission according to claim 1, further comprising a sixth 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. . 請求項１又は請求項２記載の自動変速機であって、  The automatic transmission according to claim 1 or claim 2,
第６要素は前記第２プラネタリギヤのサンギヤであり、第９要素は前記第３プラネタリギヤのリングギヤであり、第３プラネタリギヤが第２プラネタリギヤの径方向内側に配置され、第２プラネタリギヤのサンギヤと第３プラネタリギヤのリングギヤとを一体化することを特徴とする自動変速機。  The sixth element is a sun gear of the second planetary gear, the ninth element is a ring gear of the third planetary gear, the third planetary gear is disposed radially inward of the second planetary gear, the sun gear of the second planetary gear and the third planetary gear An automatic transmission which is integrated with a ring gear. ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、サンギヤ、キャリア及びリングギヤから成る３個の要素を有する複数のプラネタリギヤとを備え、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転をプラネタリギヤで複数段に変速して出力部材に出力する自動変速機であって、A fluid torque converter comprising: a fluid torque converter having a lockup clutch for mechanically connecting a pump and a turbine and connected to a power source; and a plurality of planetary gears having three elements including a sun gear, a carrier, and a ring gear. An automatic transmission that shifts the rotation of an input member to which rotation of a power source is input via a planetary gear to a plurality of stages and outputs it to an output member,
入力部材は第１と第２の２つの入力部材で構成され、  The input member is composed of first and second input members,
第１入力部材はタービンに連結され、  The first input member is coupled to the turbine;
第２入力部材は、ロックアップクラッチに介設された第２入力部材用ディスクと、プラネタリギヤの何れか１の要素とに連結され、ロックアップクラッチの係合で動力源の回転が伝達される状態となり、ロックアップクラッチの開放で動力源の回転の伝達を断たれる状態となり、  The second input member is connected to the second input member disk interposed in the lockup clutch and any one of the planetary gears, and the rotation of the power source is transmitted by the engagement of the lockup clutch. And the transmission of the rotation of the power source is cut off by releasing the lock-up clutch,
各プラネタリギヤは変速機ケース内に配置され、  Each planetary gear is placed in the transmission case,
第２入力部材に連結されるプラネタリギヤの要素は、前進１速段を確立する際に変速機ケースに固定される要素であり、  The planetary gear element connected to the second input member is an element fixed to the transmission case when establishing the first forward speed,
前記複数のプラネタリギヤは、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第２と第３の２つのプラネタリギヤとで構成され、  The plurality of planetary gears includes a first planetary gear for input disposed in a transmission case, and second and third planetary gears for transmission,
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５要素が第２入力部材に連結され、第６要素と第９要素とが連結されると共に、第８要素が出力部材に連結され、  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 the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The five elements are connected to the second input member as the seventh element, the eighth element, and the ninth element, respectively, in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram, and the sixth element And the ninth element are coupled, and the eighth element is coupled to the output member,
第４要素又は第６要素の一方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態と、第４要素又は第６要素の他方に第１入力部材の回転を第１プラネタリギヤを介して伝達する状態と、第４要素及び第６要素に第１プラネタリギヤを介した第１入力部材の回転の伝達を断つ状態とに切換自在な同期噛合機構と、  A state in which the rotation of the first input member is transmitted to one of the fourth element or the sixth element via the first planetary gear, and the rotation of the first input member to the other of the fourth element or the sixth element via the first planetary gear. A synchronous meshing mechanism that is switchable between a state in which the transmission of rotation of the first input member through the first planetary gear is cut off to the fourth element and the sixth element,
第４要素と第７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、  A first engagement element that is switchable between a state in which the fourth element and the seventh element are connected and a state in which the connection is broken;
第５要素と第７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２係合要素と、  A second engagement element switchable between a state in which the fifth element and the seventh element are connected and a state in which the connection is broken;
第５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３係合要素と、  A third engagement element switchable between a state in which the fifth element is fixed to the transmission case and a state in which the fixation is released;
第１要素又は第３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４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 comprising a fourth engagement element that is switchable between a state in which the first element or the third element is fixed to the transmission case and a state in which the fixation is released. 請求項１から請求項４の何れか１項に記載の自動変速機において、第１プラネタリギヤは、第１要素と第３要素の一方が第１入力部材に連結される入力要素、他方が変速機ケースに固定される固定要素、第２要素が出力要素である減速用のプラネタリギヤ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 4, wherein the first planetary gear includes an input element in which one of the first element and the third element is connected to the first input member, and the other is the transmission. An automatic transmission characterized in that a fixed element fixed to the case and a second planetary gear for reduction are output elements. ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、サンギヤ、キャリア及びリングギヤから成る３個の要素を有する複数のプラネタリギヤとを備え、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転をプラネタリギヤで複数段に変速して出力部材に出力する自動変速機であって、  A fluid torque converter comprising: a fluid torque converter having a lockup clutch for mechanically connecting a pump and a turbine and connected to a power source; and a plurality of planetary gears having three elements including a sun gear, a carrier, and a ring gear. An automatic transmission that shifts the rotation of an input member to which rotation of a power source is input via a planetary gear to a plurality of stages and outputs it to an output member,
入力部材は第１と第２の２つの入力部材で構成され、  The input member is composed of first and second input members,
第１入力部材はタービンに連結され、  The first input member is coupled to the turbine;
第２入力部材は、ロックアップクラッチに介設された第２入力部材用ディスクと、プラネタリギヤの何れか１の要素とに連結され、ロックアップクラッチの係合で動力源の回転が伝達される状態となり、ロックアップクラッチの開放で動力源の回転の伝達を断たれる状態となり、  The second input member is connected to the second input member disk interposed in the lockup clutch and any one of the planetary gears, and the rotation of the power source is transmitted by the engagement of the lockup clutch. And the transmission of the rotation of the power source is cut off by releasing the lock-up clutch,
各プラネタリギヤは変速機ケース内に配置され、  Each planetary gear is placed in the transmission case,
第２入力部材に連結されるプラネタリギヤの要素は、前進１速段を確立する際に変速機ケースに固定される要素であり、  The planetary gear element connected to the second input member is an element fixed to the transmission case when establishing the first forward speed,
前記複数のプラネタリギヤは、第１プラネタリギヤと第２プラネタリギヤとで構成され、The plurality of planetary gears includes a first planetary gear and a second planetary gear,
第１プラネタリギヤのサンギヤ、キャリア、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要素として、  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, and the sun gear of the second planetary gear. , The three elements consisting of the carrier and the ring gear are respectively arranged as a fourth element, a fifth element and a sixth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram.
第６要素が第２入力部材に連結され、第３要素と第４要素とを連結して連結体が構成され、第１，第２入力部材に平行に配置した出力部材たる出力軸に、第２要素が第１ギヤ列を介して連結されると共に、第５要素が第１ギヤ列とは異なるギヤ比の第２ギヤ列を介して連結され、  The sixth element is connected to the second input member, the third element and the fourth element are connected to form a connection body, and the output shaft as an output member arranged in parallel with the first and second input members Two elements are connected via a first gear train, and a fifth element is connected via a second gear train having a gear ratio different from that of the first gear train,
第１要素と第１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、  A first engagement element that is switchable between a state of connecting the first element and the first input member and a state of disconnecting the connection;
連結体と第１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、  A second engagement element that is switchable between a state in which the connecting body and the first input member are connected and a state in which the connection is broken;
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３係合要素と、  A third engagement element switchable between a state in which the first element is fixed to the transmission case and a state in which the fixation is released;
第６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４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 comprising a fourth engagement element that is switchable between a state in which the sixth element is fixed to the transmission case and a state in which the fixation is released. 請求項６記載の自動変速機であって、第３要素は第１プラネタリギヤのリングギヤであり、第４要素は前記第２プラネタリギヤのサンギヤであり、第２プラネタリギヤが第１プラネタリギヤの径方向外側に配置され、第１プラネタリギヤのリングギヤと第２プラネタリギヤのサンギヤとを一体化して前記連結体が構成されることを特徴とする自動変速機。  7. The automatic transmission according to claim 6, wherein the third element is a ring gear of the first planetary gear, the fourth element is a sun gear of the second planetary gear, and the second planetary gear is disposed radially outside the first planetary gear. An automatic transmission characterized in that the coupling body is configured by integrating a ring gear of the first planetary gear and a sun gear of the second planetary gear. ポンプとタービンとを機械的に連結させるロックアップクラッチを有し動力源に連結される流体トルクコンバータと、サンギヤ、キャリア及びリングギヤから成る３個の要素を有する複数のプラネタリギヤとを備え、流体トルクコンバータを介して動力源の回転が入力される入力部材の回転をプラネタリギヤで複数段に変速して出力部材に出力する自動変速機であって、A fluid torque converter comprising: a fluid torque converter having a lockup clutch for mechanically connecting a pump and a turbine and connected to a power source; and a plurality of planetary gears having three elements including a sun gear, a carrier, and a ring gear. An automatic transmission that shifts the rotation of an input member to which rotation of a power source is input via a planetary gear to a plurality of stages and outputs it to an output member,
入力部材は第１と第２の２つの入力部材で構成され、  The input member is composed of first and second input members,
第１入力部材はタービンに連結され、  The first input member is coupled to the turbine;
第２入力部材は、ロックアップクラッチに介設された第２入力部材用ディスクと、プラネタリギヤの何れか１の要素とに連結され、ロックアップクラッチの係合で動力源の回転が伝達される状態となり、ロックアップクラッチの開放で動力源の回転の伝達を断たれる状態となり、  The second input member is connected to the second input member disk interposed in the lockup clutch and any one of the planetary gears, and the rotation of the power source is transmitted by the engagement of the lockup clutch. And the transmission of the rotation of the power source is cut off by releasing the lock-up clutch,
各プラネタリギヤは変速機ケース内に配置され、  Each planetary gear is placed in the transmission case,
第２入力部材に連結されるプラネタリギヤの要素は、前進１速段を確立する際に変速機ケースに固定される要素であり、  The planetary gear element connected to the second input member is an element fixed to the transmission case when establishing the first forward speed,
前記複数のプラネタリギヤは、第１プラネタリギヤと第２プラネタリギヤとで構成され、  The plurality of planetary gears includes a first planetary gear and a second planetary gear,
第１プラネタリギヤのサンギヤ、キャリア、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要素として、  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, and the sun gear of the second planetary gear. , The three elements consisting of the carrier and the ring gear are respectively arranged as a fourth element, a fifth element and a sixth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram.
第１要素と第１入力部材とが連結され、第５要素と第２入力部材とが連結され、第１入力部材及び第２入力部材たる入力軸に平行に配置した出力部材たる出力軸に、第２要素が第１ギヤ列を介して連結されると共に、第６要素が第１ギヤ列とは異なるギヤ比の第２ギヤ列を介して連結され、  The first element and the first input member are connected, the fifth element and the second input member are connected, and the output shaft as an output member arranged in parallel with the input shaft as the first input member and the second input member, The second element is connected via a first gear train, and the sixth element is connected via a second gear train having a gear ratio different from that of the first gear train,
第１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、  A first engagement element switchable between a state in which the first element and the fourth element are connected and a state in which the connection is broken;
第３要素と第５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２係合要素と、  A second engagement element switchable between a state in which the third element and the fifth element are connected and a state in which the connection is broken;
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３係合要素と、  A third 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;
第５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４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 comprising a fourth engagement element that is switchable between a state in which the fifth element is fixed to the transmission case and a state in which the fixation is released.
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